CN101216093B - Automatic transmission - Google Patents

Automatic transmission Download PDF

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Publication number
CN101216093B
CN101216093B CN 200710161113 CN200710161113A CN101216093B CN 101216093 B CN101216093 B CN 101216093B CN 200710161113 CN200710161113 CN 200710161113 CN 200710161113 A CN200710161113 A CN 200710161113A CN 101216093 B CN101216093 B CN 101216093B
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CN
China
Prior art keywords
clutch
rotation
gear
automatic transmission
key element
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Expired - Fee Related
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CN 200710161113
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Chinese (zh)
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CN101216093A (en
Inventor
杉浦伸忠
荒井武夫
尾崎和久
塚本一雄
香山和道
稻垣知亲
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Aisin AW Co Ltd
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Aisin AW Co Ltd
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Publication of CN101216093A publication Critical patent/CN101216093A/en
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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
    • F16H3/663—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another with conveying rotary motion between axially spaced orbital gears, e.g. RAVIGNEAUX
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • 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
    • F16H2200/0008—Transmissions for multiple ratios specially adapted for front-wheel-driven vehicles
    • 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
    • F16H2200/2007—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with two 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
    • F16H2200/2002—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
    • F16H2200/202—Transmissions using gears with orbital motion characterised by the type of Ravigneaux set
    • F16H2200/2023—Transmissions using gears with orbital motion characterised by the type of Ravigneaux set using a Ravigneaux set with 4 connections
    • 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
    • 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
    • F16H2200/2066—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes using one freewheel mechanism
    • 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
    • F16H2200/2069—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes using two freewheel mechanism

Abstract

The present invention relates to an automatic speed changer, wherein, a rotation speed-reducing mechanism which outputs the speed-reduced rotation of the input axis with speed-reduced rotation is arranged at one axial side of the planetary gear unit, the second rotating element arranged on the planetary gear unit, the first clutch between the third rotating element and the input axis and the second clutch is arranged at the other axial side of the planetary gear unit, besides, the output component is arranged between the first clutch and the second clutch and the planetary gear unit. The speed-reducing rotation output mechanism is composed of an input rotating element which always inputs the rotation of the input axis, a fixed element for fixing the rotation, a speed reducing planetary gear of the output rotating element which is always connected to the first rotating element, and a third clutch which is arranged between the input axis and the input rotating element, the speed-reducing rotation can be outputted by the combination of the third clutch, and the friction plate of the third clutch is arranged at the opposite side to the planetary gear unit relative to the external circumference side of the planetary gear or the speed-reducing planetary gear.

Description

Automatic transmission
The application is that application number is 03800931.5, the applying date is dividing an application of March 31, denomination of invention in 2003 application for a patent for invention that is automatic transmission.
Technical field
The present invention relates to be contained in the automatic transmission on the vehicle etc., in detail, thereby relate to the arrangement that freely is input to the automatic transmission that a rotation key element of planetary gear unit can multi-change speed by the rotation of will slowing down.
Background technique
In general, be contained in the automatic transmission on vehicle etc., having of having connect the 2 planetary planetary gear units of row and planetary pinion that the rotation of the deceleration after the rotational delay of input shaft is freely exported (for example, open flat 4-125345 communique with reference to the spy, and the spy opens the 2000-274498 communique).In these automatic transmission, will freely be input on the rotation key element with planetary gear unit of 4 rotation key elements for example from the deceleration of above line star gear rotation, thereby 6 retainings of realizing for example advancing, 1 retaining falls back by clutch.
But, though in above-mentioned automatic transmission, have a plurality of clutches that are used for to the rotation of the rotation key element of above-mentioned planetary gear unit or above-mentioned planetary rotation key element input input shaft, but because the configuration of these a plurality of clutches is used for this planetary deceleration rotation is just become very long in the axial direction to the parts of the rotation key element transmission of planetary gear unit.In addition, particularly in the automatic transmission of the vehicle that is used for FF (front-mounted engine, front-wheel drive), what have also has a gear that the output of this automatic transmission rotation is outputed to parallel other on driving wheel, it is so-called counter shaft gear, this counter shaft gear is configured between for example above-mentioned planetary gear unit and the above-mentioned planetary pinion too, because the configuration of this counter shaft gear, the parts that transmit above-mentioned deceleration rotation just become very long in the axial direction.
The parts that transmit the rotation of slowing down are elongated, and the parts that just transmit big torque are elongated.The very long parts that can bear this big torque are set, the very long bigger parts of wall ratio just are set, can hinder the miniaturization of automatic transmission like this.And this component weight is also very big, not only hinders the light of automatic transmission, and because the inertial force increase, thereby reduce the controlled of automatic transmission, be easy to generate speed change and impact.
Summary of the invention
The objective of the invention is to, an a kind of axial side that is configured in planetary gear unit by the rotation output mechanism that will slow down is provided, the the 1st and the 2nd clutch is configured in the axial opposite side of planetary gear unit, output block is configured between the 1st and the 2nd clutch and the planetary gear unit, thus the automatic transmission that addresses the above problem.
The present invention's 1 automatic transmission is being provided with the input shaft that rotates according to the output of driving source, have the 1st, the 2nd, the planetary gear unit of the 3rd and the 4th rotation key element, deceleration after the rotational delay of above-mentioned input shaft rotation is freely outputed to the deceleration rotation output mechanism of above-mentioned the 1st rotation key element, be in the 1st clutch between above-mentioned input shaft and above-mentioned the 2nd rotation key element, be in the 2nd clutch between above-mentioned input shaft and above-mentioned the 3rd rotation key element, with the output block that the above-mentioned the 4th rotation of rotating key element is outputed to the driving wheel transfer mechanism, above-mentioned deceleration rotation output mechanism is configured in an axial side of above-mentioned planetary gear unit, the the above-mentioned the 1st and the 2nd clutch is configured in the axial opposite side of above-mentioned planetary gear unit, above-mentioned output block is configured between the above-mentioned the 1st and the 2nd clutch and the planetary gear unit, described deceleration rotation output mechanism is by the input rotation key element of the rotation with the described input shaft of input, the fixed factors of fixing rotation, and the epicyclic reduction gear of the output rotation key element that always is connected with described the 1st rotation key element, constitute with the 1st break of the rotation that can fix described fixed factors, combination by described the 1st break, can export described deceleration rotation, the cylinder of the Hydrauservo System of described the 1st break be formed on respect to described epicyclic reduction gear and with the housing of the opposite in the axial direction side of described planetary gear unit on.
Like this, can slow down rotation output mechanism and planetary gear unit, for example clutch and output block not separated configuration, and can make the parts (for example transferring elements or housing part etc.) that transmit the rotation of slowing down shorter near configuration.Therefore can realize miniaturization, the light of automatic transmission, and can reduce inertial force,, reduce speed change and impact so can improve the controlled of automatic transmission.
In the present invention's 2 the automatic transmission, above-mentioned the 1st clutch is connected with above-mentioned the 2nd rotation key element by interior all sides of above-mentioned output block, and above-mentioned the 2nd clutch is connected with above-mentioned the 3rd rotation key element by the outer circumferential side of above-mentioned the 1st clutch and interior all sides of above-mentioned output block.
Like this, can prevent that the parts when respectively rotating key element connects are staggered, can realize the miniaturization of automatic transmission.
In the present invention's 3 the automatic transmission, the friction plate that parts spline on above-mentioned the 1st clutch has interior all sides and is connected above-mentioned the 2nd rotation key element combines, comprise Hydrauservo System and combine with the outer circumferential side spline of this friction plate, and the 1st clutch drum that is connected with above-mentioned input shaft, press the 1st piston of this friction plate, and between the interior all sides and above-mentioned input shaft by the close shape of liquid ground sealing the 1st piston, and between outer circumferential side and the 1st clutch drum and the 1st Hydrauservo System hydraulic chamber that forms, the friction plate that all sides combined with above-mentioned the 1st clutch drum spline in above-mentioned the 2nd clutch had, comprise Hydrauservo System and combine with the outer circumferential side spline of this friction plate, and the 2nd clutch drum that is connected with above-mentioned the 3rd rotation key element, press the 2nd piston of this friction plate, and the 2nd Hydrauservo System hydraulic chamber that forms between the interior all sides by the close shape of liquid ground sealing the 2nd piston and outer circumferential side and the 2nd clutch drum.
Like this, though the 1st clutch is for disposing the structure of the 2nd clutch at its outer circumferential side, can not be to the outer circumferential side enlarged, but by Hydrauservo System is arranged on the input shaft, (for example than being arranged on the hub portion), can guarantee this bigger Hydrauservo System, especially the 1st Hydrauservo System compression area in interior all sides, can increase the capacity of the 1st clutch with hydraulic chamber.
In the present invention's 4 the automatic transmission, the friction plate that parts spline on above-mentioned the 1st clutch has interior all sides and is connected above-mentioned the 2nd rotation key element combines, comprise Hydrauservo System and combine with the outer circumferential side spline of this friction plate, and the 1st clutch drum that is connected with above-mentioned input shaft, press the 1st piston of this friction plate, and between the interior all sides and above-mentioned input shaft by the close shape of liquid ground sealing the 1st piston, and between outer circumferential side and the 1st clutch drum and the 1st Hydrauservo System hydraulic chamber that forms, in above-mentioned the 2nd clutch has all sides be connected the above-mentioned the 3rd and rotate the friction plate that the parts spline on the key element combines, comprise Hydrauservo System and combine with the outer circumferential side spline of this friction plate, and be configured in the outer circumferential side of above-mentioned the 1st clutch drum and the 2nd clutch drum that is connected with above-mentioned input shaft, press the 2nd piston of this friction plate, and the 2nd Hydrauservo System hydraulic chamber that forms between the interior all sides by the close shape of liquid ground sealing the 2nd piston and outer circumferential side and the 2nd clutch drum.
Like this, though the 1st clutch is for disposing the structure of the 2nd clutch at its outer circumferential side, can not be to the outer circumferential side enlarged, but by Hydrauservo System is arranged on the input shaft, (for example than being arranged on the hub portion), can guarantee this bigger Hydrauservo System, especially the 1st Hydrauservo System compression area in interior all sides, can increase the capacity of the 1st clutch with hydraulic chamber.
In the present invention's 5 the automatic transmission, above-mentioned deceleration rotation output mechanism has epicyclic reduction gear, and above-mentioned planetary pinion, above-mentioned planetary gear unit and above-mentioned output block are set to the structure coaxial with above-mentioned input shaft.
Like this, particularly when automatic transmission being contained on the FF vehicle, (for example comparing) with the situation that epicyclic reduction gear etc. is arranged on other, can realize the miniaturization of driving wheel transfer mechanism (for example in the middle of axial region 4 etc.), can prevent the interference with for example body part, improve the vehicle boarded performance of automatic transmission.
In the present invention's 6 the automatic transmission, above-mentioned deceleration rotation output mechanism by the fixed factors of the input rotation key element of rotation, fixing rotation and the output that always is connected with above-mentioned the 1st rotation key element with the above-mentioned input shaft of input rotate the above-mentioned epicyclic reduction gear of key element and fixedly the 1st break of said fixing key element constitute, by the combination of above-mentioned the 1st break, can export above-mentioned deceleration rotation.
Like this, because fixedly the output of the rotation of slowing down is connected, disconnected to the 1st break of the rotation of fixed factors, so compare with the clutch of for example connecting, disconnect the deceleration rotation, the miniaturization of the 1st break can be realized, and slow down rotation output mechanism and the close configuration of planetary gear unit can be made.Can realize miniaturization, the light of automatic transmission like this.
In the present invention's 7 the automatic transmission, above-mentioned deceleration rotation output mechanism is by the epicyclic reduction gear of the fixed factors of the input rotation key element of the rotation with the above-mentioned input shaft of input, fixing rotation and the output rotation key element that is connected with above-mentioned the 1st rotation key element always and can be fixed in above-mentioned input shaft and the 1st break that the rotation of the 3rd clutch between the key element and said fixing key element is rotated in above-mentioned input constitutes, by the combination of above-mentioned the 3rd clutch, above-mentioned the 1st break, can export above-mentioned deceleration rotation.
Like this, because the output of the rotation of slowing down is connected, disconnected to the 3rd clutch between input shaft and input rotation key element and the 1st break of the fixedly rotation of fixed factors, so compare with the clutch of for example connecting, disconnect the deceleration rotation, the miniaturization of the 3rd break and the 1st break can be realized, and slow down rotation output mechanism and the close configuration of planetary gear unit can be made.Can realize the miniaturization and the light of automatic transmission like this.
In the present invention's 8 the automatic transmission, above-mentioned deceleration rotation output mechanism constitutes by the epicyclic reduction gear of the fixed factors of the input rotation key element with rotation of always importing above-mentioned input shaft, fixing rotation always and the output rotation key element that is connected with above-mentioned the 1st rotation key element always with at the 3rd clutch that above-mentioned input shaft and above-mentioned input are rotated between the key element, by the combination of above-mentioned the 3rd clutch, can export above-mentioned deceleration rotation.
Like this, because the output of the rotation of slowing down is connected, disconnected to the 3rd clutch between input shaft and input rotation key element, so compare with the clutch of for example connecting, disconnect the deceleration rotation, the miniaturization of the 3rd clutch can be realized, and slow down rotation output mechanism and the close configuration of planetary gear unit can be made.Can realize the miniaturization and the light of automatic transmission like this.
In the present invention's 9 the automatic transmission, above-mentioned deceleration rotation output mechanism constitutes by the epicyclic reduction gear of the fixed factors of the input rotation key element with rotation of always importing above-mentioned input shaft, fixing rotation always and the output rotation key element that is connected with above-mentioned the 1st rotation key element with at the 3rd clutch that above-mentioned the 1st rotation key element and above-mentioned output are rotated between the key element, by the combination of above-mentioned the 3rd clutch, can export above-mentioned deceleration rotation.
Like this, because the output of the rotation of slowing down is connected, disconnected to the 3rd clutch between the 1st rotation key element and output rotation key element, so the rotation of slowing down freely can be outputed to the 1st rotation key element, utilize planetary pinion idle running by the rotation that for example discharges the 3rd clutch simultaneously, can make the input shaft that is input to input rotation key element.Like this, can break be set and the key element that will for example fix rotation directly is fixed on the housing etc., thereby can realize the miniaturization and the light of automatic transmission.
In the present invention's 10 the automatic transmission, above-mentioned the 1st clutch, above-mentioned the 2nd clutch, above-mentioned the 3rd clutch has Hydrauservo System respectively, the Hydrauservo System of above-mentioned the 2nd clutch is configured in from an end of above-mentioned housing extends on the 1st hub portion that is provided with, and be communicated with the oil circuit that is arranged on the 1st hub portion, the Hydrauservo System of above-mentioned the 1st clutch is configured in an end of above-mentioned input shaft, and be communicated with the oil circuit of an end of above-mentioned the 1st hub portion or above-mentioned housing by the oil circuit that is arranged in the above-mentioned input shaft, the Hydrauservo System of above-mentioned the 3rd clutch is configured in from the other end of above-mentioned housing extends on the other end of the 2nd hub portion that is provided with or above-mentioned input shaft, is communicated with oil circuit that is arranged on above-mentioned the 2nd hub portion or the oil circuit that is arranged in the above-mentioned input shaft.
Like this, because the Hydrauservo System of the 1st clutch is arranged on the end of input shaft, so by utilizing a pair of seal ring to stop to leak and from the oil circuit fuel feeding of housing in being arranged on input shaft, can between for example input shaft and this Hydrauservo System, seal ring be set, just can be to this Hydrauservo System fuel feeding.In addition, the Hydrauservo System of the 2nd and the 3rd clutch can not passed through for example other parts, and respectively from extending the hub portion DFF Direct Fuel Feed that is provided with from housing, promptly can carry out fuel feeding by a pair of seal ring is set respectively.Therefore, by only in 3 Hydrauservo Systems, a pair of seal ring being set respectively, just can fuel feeding, thus minimum is reduced in the sliding friction that seal ring can be caused, improves the efficient of automatic transmission.
In the present invention's 11 the automatic transmission, above-mentioned the 1st clutch, above-mentioned the 2nd clutch, above-mentioned the 3rd clutch has Hydrauservo System respectively, the Hydrauservo System of above-mentioned the 2nd clutch is configured in from an end of above-mentioned housing extends on the 1st hub portion that is provided with, and be communicated with the oil circuit that is arranged on the 1st hub portion, the Hydrauservo System of above-mentioned the 1st clutch is configured in an end of above-mentioned input shaft, and be communicated with the oil circuit of an end of above-mentioned the 1st hub portion or above-mentioned housing by the oil circuit that is arranged in the above-mentioned input shaft, the Hydrauservo System of above-mentioned the 3rd clutch is configured on the other end of above-mentioned input shaft, is communicated with oil circuit in being arranged on above-mentioned input shaft.
Like this, because the Hydrauservo System of the 1st clutch is arranged on the end of input shaft, so by utilizing a pair of seal ring to stop to leak and from the oil circuit fuel feeding of housing in being arranged on input shaft, can between for example input shaft and this Hydrauservo System, seal ring be set, just can be to this Hydrauservo System fuel feeding.The Hydrauservo System of the 2nd clutch can not passed through for example other parts, and from extend the hub portion fuel feeding that is provided with from housing.In addition, the Hydrauservo System of the 3rd clutch is configured on the above-mentioned input shaft, by utilizing a pair of seal ring to stop to leak and from the oil circuit fuel feeding of housing in being arranged on input shaft, can between for example input shaft and this Hydrauservo System, seal ring be set, just can be to this Hydrauservo System fuel feeding.Promptly, a pair of seal ring just can carry out fuel feeding by being set respectively.Therefore, by only in 3 Hydrauservo Systems, a pair of seal ring being set respectively, just can fuel feeding, thus minimum is reduced in the sliding friction that seal ring causes, improve the efficient of automatic transmission.In addition, though on input shaft, disposing the Hydrauservo System of the 1st and the 3rd clutch, but because respectively in distolateral and another distolateral separate configuration of input shaft, do not need to be provided with again the Hydrauservo System in the input shaft, so can subtract thin input shaft, realize the miniaturization of automatic transmission.
In the present invention's 12 the automatic transmission, all sides were rotated the friction plate that the parts spline on the key element combines with the above-mentioned input rotation key element or the above-mentioned output that are connected above-mentioned epicyclic reduction gear in above-mentioned the 3rd clutch had, comprise Hydrauservo System and the 3rd clutch drum that combines with the outer circumferential side spline of this friction plate, press the 3rd piston of this friction plate, the 1st Hydrauservo System hydraulic chamber that forms between interior all sides by the close shape of liquid ground sealing the 3rd piston and outer circumferential side and the 3rd clutch drum, above-mentioned friction plate is configured at least the position that partly overlaps with the outer radial periphery side of above-mentioned epicyclic reduction gear, above-mentioned the 3rd clutch drum is with to the configuration of the form of above-mentioned epicyclic reduction gear direction opening, between the Hydrauservo System that above-mentioned epicyclic reduction gear is configured in above-mentioned the 3rd clutch and above-mentioned planetary gear unit axial.
Like this, because friction plate is configured in planetary outer radial periphery side, can make automatic transmission miniaturization in the axial direction.In addition, because between the Hydrauservo System by epicyclic reduction gear being configured in the 3rd clutch and planetary gear unit axial, can be with epicyclic reduction gear and planetary gear unit disposed adjacent (Hydrauservo System of the 3rd clutch is not between epicyclic reduction gear and the planetary gear unit), the parts (for example transferring elements or housing part etc.) of rotation can be shorter so transmission is slowed down.Like this, can realize the miniaturization and the light of automatic transmission, and,, reduce speed change and impact so can improve the controlled of automatic transmission owing to can reduce inertial force.
In the present invention's 13 the automatic transmission, above-mentioned epicyclic reduction gear is the double pinion planetary pinion.
Like this, because the rotation that can make input shaft is as the rotation output of slowing down, even and set the gear ratio of automatic transmission preferably, what also need not increase planetary gear unit, epicyclic reduction gear respectively rotates key element, high speed rotating can be suppressed, thereby the miniaturization of automatic transmission can be realized.
In the present invention's 14 the automatic transmission, above-mentioned epicyclic reduction gear is included as the 1st planetary carrier of above-mentioned input rotation key element, rotates the 1st ring gear of key element for the 1st sun gear of said fixing key element, for above-mentioned output.
Like this, the rotation of input shaft can be exported as the rotation of slowing down.
In the present invention's 15 the automatic transmission, above-mentioned epicyclic reduction gear is included as the 1st sun gear of above-mentioned input rotation key element, rotates the 1st ring gear of key element for the 1st planetary carrier of said fixing key element, for above-mentioned output.
Like this, the rotation of input shaft can be exported as the rotation of slowing down.
In the present invention's 16 the automatic transmission, above-mentioned planetary gear unit is by the 2nd sun gear, the 3rd sun gear, the 2nd planetary carrier, and drawing of the 2nd ring gear composition tieed up Nao formula planetary pinion, above-mentioned the 1st rotation key element is the output rotation of the above-mentioned deceleration rotation of input output mechanism, and above-mentioned the 2nd sun gear is freely fixed in the locking of passing through the 2nd break, above-mentioned the 2nd rotation key element is above-mentioned the 3rd sun gear of the rotation of importing above-mentioned input shaft by the combination of above-mentioned the 1st clutch, above-mentioned the 3rd rotation key element is to have and the long small gear of above-mentioned the 2nd sun gear engagement and the short and small gear that meshes with above-mentioned the 3rd sun gear, fix freely by the locking of the 3rd break, and by above-mentioned the 2nd planetary carrier of rotation in conjunction with the above-mentioned input shaft of input of above-mentioned the 2nd clutch, above-mentioned the 4th rotation key element is above-mentioned the 2nd ring gear with above-mentioned long pinion.
Like this, 6 retainings of can realizing for example advancing, 1 retaining that falls back, and can make slow down rotation output mechanism and planetary gear unit near configuration can shorten and be used to transmit the transferring elements that slows down and rotate.
In the present invention's 17 the automatic transmission, have and dispose side by side with above-mentioned the 3rd break and at the 1st overrunning clutch of the rotation of a direction restriction above line gear rack.
Like this, owing to can utilize 1 retaining that advances when realizing for example just driving of the 1st clutch and the 1st overrunning clutch, so can realize switching to 1 retaining that advances when travelling reposefully from for example non-position of travelling.
In the present invention's 18 the automatic transmission, above-mentioned the 3rd break is configured in the outer circumferential side of above-mentioned planetary gear unit, above-mentioned the 1st overrunning clutch and above-mentioned the 2nd clutch disposed adjacent.
Like this, when realizing advancing 1 retaining, the 1st overrunning clutch combines with the 1st clutch of the rotation of input input shaft, corresponding therewith, by the 3rd break and connection, the 3rd clutch that disconnects the rotation of slowing down combine to realize falling back and 1 keeps off, so act on anti-torque on the 3rd break greater than the anti-torque that acts on the 1st overrunning clutch.Therefore, by make the 3rd break near with the outer circumferential side setting of planetary gear unit, can make the parts of transmission of torque to the 3 breaks of the rotation of slowing down shorter relatively.In addition, even the 1st overrunning clutch is arranged near the 2nd clutch that leaves planetary gear unit, do not need to strengthen the parts that connect the 2nd clutch and the 2nd planetary carrier yet.In addition, dispose the 1st overrunning clutch, can increase the design freedom of break by periphery not at planetary gear unit.Like this, can realize the miniaturization and the light of automatic transmission.
In the present invention's 19 the automatic transmission, above-mentioned the 3rd break and above-mentioned the 1st overrunning clutch are configured in the outer circumferential side of above-mentioned planetary gear unit.
Like this, (because with for example the 1st overrunning clutch is compared with the situation of the 1st clutch disposed adjacent, the part that disposes the 1st and the 2nd clutch can realize miniaturization in the axial direction) can make output block for example near the fluid torque converter side.Like this, thus can make driving wheel transfer mechanism portion (particularly in the middle of axial region) realize miniaturization in the axial direction.
In the present invention's 20 the automatic transmission, have with above-mentioned the 2nd break dispose side by side, the 2nd overrunning clutch that a direction limits the rotation of above-mentioned the 2nd sun gear that is locked in by the 4th break.
Like this, can switch to 3 retainings that advance from 2 retainings that for example advance reposefully.
In the present invention's 21 the automatic transmission, have between above-mentioned deceleration rotation output mechanism and above-mentioned the 2nd sun gear and be connected the output rotation of above-mentioned deceleration rotation output mechanism and the housing part of the rotation of above-mentioned the 2nd sun gear, the inner ring of above-mentioned the 2nd overrunning clutch and above-mentioned housing part are integrally formed.
Like this, can realize reposefully switching to 3 retainings that advance, can realize the miniaturization of automatic transmission simultaneously from 2 retainings that for example advance.
In the present invention's 22 the automatic transmission, represent in rotating speed separately, transverse axis the speed line chart of above-mentioned the 1st, the 2nd, the 3rd and the 4th rotation key element at the longitudinal axis corresponding to the gear ratio of above-mentioned the 1st, the 2nd, the 3rd and the 4th rotation key element, import the longitudinal axis of above-mentioned the 1st rotation key element of above-mentioned deceleration rotation, corresponding successively above-mentioned the 3rd rotation key element of other longitudinal axis, above-mentioned the 4th rotation key element that is connected with above-mentioned output block, above-mentioned the 2nd rotation key element corresponding to laterally end.
Like this, shown in the speed line chart, when 6 retainings, 1 retaining that falls back are advanced in realization, can make slow down rotation output mechanism and the close configuration of planetary gear unit, thereby can shorten the length of the parts that transmit the rotation of slowing down.Like this, can realize the miniaturization and the light of automatic transmission, so and since can reduce inertial force can improve automatic transmission controlled, reduce the generation that speed change is impacted.
In the present invention's 23 the automatic transmission, respectively by above-mentioned the 1st clutch and above-mentioned the 3rd break in conjunction with realizing 1 retaining that advances, by above-mentioned the 1st clutch and above-mentioned the 2nd break in conjunction with realizing 2 retainings that advance, combination by above-mentioned the 1st clutch and can be from the state of above-mentioned deceleration rotation output mechanism output deceleration rotation 3 retainings of realizing advancing, by above-mentioned the 1st clutch and above-mentioned the 2nd break in conjunction with realizing 4 retainings that advance, combination by above-mentioned the 2nd clutch and can be from the state of above-mentioned deceleration rotation output mechanism output deceleration rotation 5 retainings of realizing advancing, by above-mentioned the 2nd clutch and above-mentioned the 2nd break in conjunction with realizing 6 retainings that advance, the combination by above-mentioned the 3rd clutch and can be from the state of above-mentioned deceleration rotation output mechanism output deceleration rotation 1 retaining of realizing falling back.
Like this, speed changer as realize advancing 6 retainings, 1 retaining that falls back, the the 1st and the 2nd clutch combination simultaneously in 4 retainings that advance, promptly in 4 retainings that advance, be in direct-connected state, so can set the gear ratio of advance 5 retainings and 6 retainings that advance than the highland, when particularly being contained on the vehicle, for the vehicle of running at high speed, can reduce the rotating speed of motor, thereby the quiet characteristic of the vehicle of running at high speed is provided.
In the present invention's 24 the automatic transmission, above-mentioned planetary gear unit is served as reasons and is had the 2nd sun gear, the 2nd planetary carrier, the 1st simple planetary arrangement of the 2nd ring gear, with have the 3rd sun gear, the 3rd planetary carrier, the 2nd simple planetary arrangement of the 3rd ring gear is formed, above-mentioned the 1st rotation key element is the planetary output rotation of the above-mentioned double pinion of input, and above-mentioned the 3rd ring gear is freely fixed in the locking of passing through the 2nd break, above-mentioned the 2nd rotation key element is fixed freely for the locking by the 3rd break, and above-mentioned the 3rd planetary carrier and above-mentioned the 2nd ring gear of the rotation of above-mentioned input shaft are imported in the combination of passing through the 1st clutch, the above-mentioned the 3rd rotates key element is above-mentioned the 2nd sun gear and above-mentioned the 3rd sun gear in conjunction with the rotation of importing above-mentioned input shaft by above-mentioned the 2nd clutch, and above-mentioned the 4th rotation key element is above-mentioned the 2nd planetary carrier that meshes with above-mentioned the 2nd sun gear and above-mentioned the 2nd ring gear.
Like this, in 6 retainings of can realizing for example advancing, 1 retaining that falls back, can also make slow down rotation output mechanism and planetary gear unit, thereby can shorten the length of the parts that transmitting slows down rotates near configuration.
In the present invention's 25 the automatic transmission, has the 1st overrunning clutch that disposes and limit the rotation of above-mentioned the 3rd planetary carrier and above-mentioned the 2nd ring gear with above-mentioned the 3rd break side by side in a direction.
Like this, owing to can utilize 1 retaining that advances when realizing for example just driving of the 2nd clutch and the 1st overrunning clutch, thereby can realize switching to 1 retaining that advances when travelling reposefully from for example non-position of travelling.
In the present invention's 26 the automatic transmission, above-mentioned the 3rd break and above-mentioned the 1st overrunning clutch are configured in the outer circumferential side of above-mentioned planetary gear unit.
Like this, (because with for example the 1st overrunning clutch is compared with the situation of the 1st clutch disposed adjacent, the part that disposes the 1st and the 2nd clutch can realize miniaturization in the axial direction) can make output block for example near the fluid torque converter side.Like this, thus can make driving wheel transfer mechanism portion (particularly in the middle of axial region) realize miniaturization in the axial direction.
In the present invention's 27 the automatic transmission, the inner ring of above-mentioned the 1st overrunning clutch and above-mentioned the 2nd ring gear are integrally formed.
Like this, 1 retaining that advances when travelling can be realized switching to reposefully, the miniaturization of automatic transmission can be realized simultaneously from for example non-position of travelling.
In the present invention's 28 the automatic transmission, have and dispose side by side with above-mentioned the 2nd break and the 2nd overrunning clutch that a direction limits the rotation of above-mentioned the 3rd planetary carrier that is locked in by the 4th break.
Like this, can realize reposefully switching to 3 retainings that advance from 2 retainings that for example advance.
In the present invention's 29 the automatic transmission, represent in rotating speed separately, transverse axis the speed line chart of above-mentioned the 1st, the 2nd, the 3rd and the 4th rotation key element at the longitudinal axis corresponding to the gear ratio of above-mentioned the 1st, the 2nd, the 3rd and the 4th rotation key element, import the longitudinal axis of above-mentioned the 1st rotation key element of above-mentioned deceleration rotation, corresponding successively above-mentioned the 3rd rotation key element of other longitudinal axis, above-mentioned the 4th rotation key element that is connected with above-mentioned output block, above-mentioned the 2nd rotation key element corresponding to lateral ends.
Like this, shown in the speed line chart, when 6 retainings, 1 retaining that falls back are advanced in realization, can make slow down rotation output mechanism and the close configuration of planetary gear unit, thereby can shorten the length of the parts that transmit the rotation of slowing down.Like this, can realize the miniaturization and the light of automatic transmission, so and since can reduce inertial force can improve automatic transmission controlled, reduce the generation that speed change is impacted.
In the present invention's 30 the automatic transmission, respectively by above-mentioned the 2nd clutch and above-mentioned the 3rd break in conjunction with realizing 1 retaining that advances, by above-mentioned the 2nd clutch and above-mentioned the 2nd break in conjunction with realizing 2 retainings that advance, combination by above-mentioned the 2nd clutch and can be from the state of above-mentioned deceleration rotation output mechanism output deceleration rotation 3 retainings of realizing advancing, by above-mentioned the 1st clutch and above-mentioned the 2nd clutch in conjunction with realizing 4 retainings that advance, combination by above-mentioned the 1st clutch and can be from the state of above-mentioned deceleration rotation output mechanism output deceleration rotation 5 retainings of realizing advancing, by above-mentioned the 1st clutch and above-mentioned the 2nd break in conjunction with realizing 6 retainings that advance, the combination by above-mentioned the 3rd clutch and can be from the state of above-mentioned deceleration rotation output mechanism output deceleration rotation 1 retaining of realizing falling back.
Like this, speed changer as realize advancing 6 retainings, 1 retaining that falls back, the the 1st and the 2nd clutch combination simultaneously in 4 retainings that advance, promptly in 4 retainings that advance, be in direct-connected state, so can set the gear ratio of advance 5 retainings and 6 retainings that advance than the highland, when particularly being contained on the vehicle, for the vehicle of running at high speed, can reduce the rotating speed of motor, thereby the quiet characteristic of the vehicle of running at high speed is provided.
In the present invention's 31 the automatic transmission, above-mentioned planetary gear unit is served as reasons and is had the 2nd sun gear, the 3rd sun gear, the 2nd planetary carrier, and drawing of the 2nd ring gear composition tieed up Nao formula planetary pinion, above-mentioned the 3rd sun gear that above-mentioned the 1st rotation key element is rotated for the output that can import above-mentioned deceleration rotation output mechanism, above-mentioned the 2nd rotation key element is to have the long small gear that meshes with above-mentioned the 2nd sun gear, with with the short and small gear of above-mentioned the 3rd sun gear engagement, fix freely by the locking of the 2nd break, and above-mentioned the 2nd planetary carrier of the rotation of above-mentioned input shaft is imported in the combination of passing through the 1st clutch, above-mentioned the 3rd rotation key element is the rotation in conjunction with the above-mentioned input shaft of input by above-mentioned the 2nd clutch, and the locking by the 3rd break fix the 2nd sun gear freely, and the above-mentioned the 4th to rotate key element be above-mentioned the 2nd ring gear with above-mentioned long pinion.
Like this, in 6 retainings of can realizing for example advancing, 1 retaining that falls back, can also make slow down rotation output mechanism and planetary gear unit, thereby can shorten the length of the parts that transmitting slows down rotates near configuration.
In the present invention's 32 the automatic transmission, has the 1st overrunning clutch that disposes and limit the rotation of above-mentioned the 2nd planetary carrier with above-mentioned the 2nd break side by side in a direction.
Like this, owing to can utilize 1 retaining that advances when realizing for example just driving of the 3rd clutch and the 1st overrunning clutch, thereby can realize switching to 1 retaining that advances when travelling reposefully from for example non-position of travelling.
Among the present invention 33 automatic transmission, above-mentioned the 2nd break and above-mentioned the 1st overrunning clutch are configured in the outer circumferential side of above-mentioned planetary gear unit.
Like this, (because with for example the 1st overrunning clutch is compared with the situation of the 1st clutch disposed adjacent, the part that disposes the 1st and the 2nd clutch can realize miniaturization in the axial direction) can make output block near the fluid torque converter side.Like this, can make driving wheel transfer mechanism portion (axial region particularly) realize miniaturization in the axial direction.
In the present invention's 34 the automatic transmission, represent in rotating speed separately, transverse axis the speed line chart of above-mentioned the 1st, the 2nd, the 3rd and the 4th rotation key element at the longitudinal axis corresponding to the gear ratio of above-mentioned the 1st, the 2nd, the 3rd and the 4th rotation key element, import the longitudinal axis of above-mentioned the 1st rotation key element of above-mentioned deceleration rotation, corresponding successively above-mentioned the 4th rotation key element that is connected with above-mentioned output block of other longitudinal axis, above-mentioned the 2nd rotation key element, above-mentioned the 3rd rotation key element corresponding to laterally end.
Like this, shown in the speed line chart, when 6 retainings, 1 retaining that falls back are advanced in realization, can make slow down rotation output mechanism and the close configuration of planetary gear unit, thereby can shorten the length of the parts that transmit the rotation of slowing down.Like this, can realize the miniaturization and the light of automatic transmission, so and since can reduce inertial force can improve automatic transmission controlled, reduce the generation that speed change is impacted.
In the present invention's 35 the automatic transmission, combination by above-mentioned the 2nd break and can be respectively from the state of above-mentioned deceleration rotation output mechanism output deceleration rotation 1 retaining of realizing advancing, combination by above-mentioned the 3rd break and can be from the state of above-mentioned deceleration rotation output mechanism output deceleration rotation 2 retainings of realizing advancing, combination by above-mentioned the 2nd clutch and can be from the state of above-mentioned deceleration rotation output mechanism output deceleration rotation 3 retainings of realizing advancing, combination by above-mentioned the 1st clutch and can be from the state of above-mentioned deceleration rotation output mechanism output deceleration rotation 4 retainings of realizing advancing, by above-mentioned the 1st clutch and above-mentioned the 2nd clutch in conjunction with realizing 5 retainings that advance, by above-mentioned the 1st clutch and above-mentioned the 3rd break in conjunction with realizing 6 retainings that advance, by above-mentioned the 2nd clutch and above-mentioned the 2nd break in conjunction with realizing 1 retaining that falls back.
Like this, speed changer as realize for example advancing 6 retainings, 1 retaining that falls back, the the 1st and the 2nd clutch combination when advancing 5 retainings, be in so-called direct-connected state, can be in the rotation of slowing down from 14 the retaining outputs that block to 4 retainings that advance of advancing, when particularly on vehicle, carrying automatic transmission, the speed change of the middle low-speed region of vehicle is further segmented.Like this,, can use the rotary speed area with optimum efficiency of driving source such as motor more, improve the Economy of fuel particularly at the middle low-speed region of vehicle.In addition, because 6 retainings that advance are driven for hypervelocity, compare for direct-connected state, advance 5 retainings and 6 retainings that advance are the situation that hypervelocity drives, can reduce final reduction speed ratio with 4 retainings that advance.Like this, can reduce for example spider gear diameter of differential mechanism portion, shorten the axle base of the axle of input shaft and differential mechanism portion, when particularly carrying on the FF vehicle, can realize the miniaturization of automatic transmission.
In the present invention's 36 the automatic transmission, above-mentioned driving wheel transfer mechanism has to the differential mechanism portion of driving wheel output rotation and middle the axial region that combines with this differential mechanism portion, and above-mentioned output block is the counter shaft gear that meshes with middle axial region.
Like this, thus automatic transmission can be carried on FF vehicle for example.
Description of drawings
Fig. 1 is the cross section unfolded drawing of the automatic transmission of expression the 1st mode of execution.
Fig. 2 is the sectional view of the automatic transmission of the automatic transmission of expression the 1st mode of execution.
Fig. 3 is the schematic diagram of the automatic transmission of expression the 1st mode of execution.
Fig. 4 is the action schedule of the automatic transmission of the 1st mode of execution.
Fig. 5 is the speed line chart of the automatic transmission of the 1st mode of execution.
Fig. 6 is the cross section unfolded drawing of the automatic transmission of expression the 2nd mode of execution.
Fig. 7 is the sectional view of the automatic transmission of the automatic transmission of expression the 2nd mode of execution.
Fig. 8 is the schematic diagram of the automatic transmission of expression the 2nd mode of execution.
Fig. 9 is the action schedule of the automatic transmission of the 2nd mode of execution.
Figure 10 is the speed line chart of the automatic transmission of the 2nd mode of execution.
Figure 11 is the sectional view of the automatic transmission of the automatic transmission of expression the 3rd mode of execution.
Figure 12 is the schematic diagram of the automatic transmission of expression the 3rd mode of execution.
Figure 13 is the action schedule of the automatic transmission of the 3rd mode of execution.
Figure 14 is the speed line chart of the automatic transmission of the 3rd mode of execution.
Figure 15 is the sectional view of the automatic transmission of the automatic transmission of expression the 4th mode of execution.
Figure 16 is the schematic diagram of the automatic transmission of expression the 4th mode of execution.
Figure 17 is the action schedule of the automatic transmission of the 4th mode of execution.
Figure 18 is the speed line chart of the automatic transmission of the 4th mode of execution.
Figure 19 is the pattern sectional view of the automatic transmission of the automatic transmission of expression the 5th mode of execution.
Figure 20 is the action schedule of the automatic transmission of the 5th mode of execution.
Figure 21 is the speed line chart of the automatic transmission of the 5th mode of execution.
Figure 22 is the pattern sectional view of the automatic transmission of the automatic transmission of expression the 6th mode of execution.
Figure 23 is the pattern sectional view of the automatic transmission of the automatic transmission of expression the 7th mode of execution.
Figure 24 is the action schedule of the automatic transmission of the 7th mode of execution.
Figure 25 is the speed line chart of the automatic transmission of the 7th mode of execution.
Figure 26 is the pattern sectional view of the automatic transmission of the automatic transmission of expression the 8th mode of execution.
Figure 27 is the action schedule of the automatic transmission of the 8th mode of execution.
Figure 28 is the speed line chart of the automatic transmission of the 8th mode of execution.
Figure 29 is the pattern sectional view of the automatic transmission of the automatic transmission of expression the 6th mode of execution.
Figure 30 is the action schedule of the automatic transmission of the 9th mode of execution.
Figure 31 is the speed line chart of the automatic transmission of the 9th mode of execution.
Figure 32 is the pattern sectional view of the automatic transmission of the automatic transmission of expression the 10th mode of execution.
Figure 33 is the action schedule of the automatic transmission of the 10th mode of execution.
Figure 34 is the speed line chart of the automatic transmission of the 10th mode of execution.
Figure 35 is the pattern sectional view of the automatic transmission of the automatic transmission of expression the 11st mode of execution.
Figure 36 is the action schedule of the automatic transmission of the 11st mode of execution.
Figure 37 is the speed line chart of the automatic transmission of the 11st mode of execution.
Embodiment
(the 1st mode of execution)
Below in conjunction with Fig. 1～Fig. 5 the 1st mode of execution of the present invention is described.Fig. 1 is the cross section unfolded drawing of the automatic transmission of expression the 1st mode of execution.Fig. 2 is the sectional view of the automatic transmission of the automatic transmission of expression the 1st mode of execution.Fig. 3 is the schematic diagram of the automatic transmission of expression the 1st mode of execution.Fig. 4 is the action schedule of the automatic transmission of the 1st mode of execution.Fig. 5 is the speed line chart of the automatic transmission of the 1st mode of execution.
The automatic transmission 1 of the 1st mode of execution of the present invention 1Be particularly suitable for FF (front-mounted engine, front-wheel drive) vehicle.As shown in Figure 1, have the housing of forming by frame housing 3a and gearbox casing 3b 3, in this frame housing 3a, dispose fluid torque converter 12, in this gearbox casing 3b, dispose automatic transmission 2 1, middle axial region (driving wheel transfer mechanism) 4 and differential mechanism portion (driving wheel transfer mechanism) 5.This fluid torque converter 12 for example is configured in the automatic transmission 2 coaxial with the output shaft 10 of motor (not shown) 1 Input shaft 20 be the center the axle on, this automatic transmission 2 1Be configured in with the output shaft 10 of this motor, promptly the coaxial central shaft 30 of this input shaft 20 is on the axle at center.In addition, middle axial region 4 is configured on the jack shaft 52 into the axle parallel with these input shafts 20 and central shaft 30, and differential mechanism portion 5 is configured on the axle parallel with this jack shaft 52, and has among the figure the not left and right sides axletree of expression.
In addition, cross section unfolded drawing shown in Figure 1 is with automatic transmission 1 1The figure that planar development is represented, above-mentioned input shaft 20 and central shaft 30, jack shaft 52 and not shown left and right sides axletree see from the side be＜symbol 12 ' expression fluid torque converter among the position of word shape relation, particularly Fig. 1 with respect to jack shaft 52 the position concern.
Dispose disc-shaped part 11 on the output shaft 10 of above-mentioned motor, the outer circumferential side of this disc-shaped part 11 is connected with the pump impeller 12a of fluid torque converter 12.In addition, the all within it sides of the turbine 12b of fluid torque converter 12 are connected with the damping device 13 that absorbs the torque variation, the outer circumferential side of this damping device 13 is connected with the piston element 14 of the lock-up clutch of free combination on above-mentioned pump impeller 12a, and this piston element 14 and above-mentioned automatic transmission 2 1 Input shaft 20 connect.Promptly under this piston element 14 is not combined in state on the pump impeller 12a, by fluid torque converter 12 with the transmission of torque of not shown motor to above-mentioned input shaft 20.Under this piston element 14 is combined in state on the pump impeller 12a, above-mentioned output shaft 10 and input shaft 20 places and direct coupled condition, the torque of motor is directly delivered to input shaft 20.
Then, in conjunction with Fig. 2 automatic transmission 2 is described 1As shown in Figure 2, at an end above-mentioned input shaft 20 and opposition side fluid torque converter 12, all sides are formed with spline 20s in it, combine with the spline 30s that an end outer circumferential side at central shaft 30 forms, and promptly input shaft 20 and jack shaft 30 link together along sense of rotation.Has planetary gear unit PU and epicyclic reduction gear (the rotation output mechanism slows down) PR on this central shaft 30.This planetary gear unit PU has as the sun gear of 4 rotation key elements (the 2nd rotation key element, the 3rd sun gear) S2, planetary carrier (the 3rd rotation key element, the 2nd planetary carrier) CR2, ring gear (the 4th rotation key element, the 2nd ring gear) R2, and sun gear (the 1st rotation key element, the 2nd sun gear) S3, on this planetary carrier CR2, by side plate 42,44 support, with the long small gear PL of sun gear S3 and ring gear R2 engagement with by side plate 43,44 support, be meshing with each other with the short and small gear PS of sun gear S2 engagement, be the so-called dimension Nao formula planetary pinion that draws.In addition, above-mentioned epicyclic reduction gear PR has on planetary carrier (input rotation key element, the 1st planetary carrier) CR1, with ring gear R1 (output rotation key element, the 1st ring gear) the small gear P1 of engagement and the intermeshing form of small gear P2 that meshes with sun gear (fixed factors, the 1st sun gear) S1, be so-called double-pinion type planetary pinion.
On the above-mentioned input shaft 20, all within it sides are disposing has wheelboss part 22 that forms Hydrauservo System 62, friction plate 72, clutch drum (the 1st clutch drum) and multidisc clutch (the 1st clutch) C1 of the wheelboss part that is connected with drum type parts 21, sun gear S2 (parts that are connected with the 2nd rotation key element) 23; Disposing multidisc clutch (the 2nd clutch) C2 of wheelboss part 24 with formation Hydrauservo System 61, friction plate 71, clutch drum (the 2nd clutch drum) and the wheelboss part 25 that is connected with cylinder part 61e, planetary carrier CR2 at its outer circumferential side.
This Hydrauservo System 62 is by the piston element that is used to press friction plate 72 (the 1st piston) 62b, hydraulic chamber (the 1st hydraulic servo hydraulic chamber) 62a that between the drum type parts 21 with the 62e of cylinder portion, this piston element 62b and the 62e of this cylinder portion, utilizes seal ring 62f, 62g sealing to form, this piston element 62b is constituted towards the restoring board 62d that the direction of this hydraulic chamber 62a is subjected to the Returnning spring 62c of spring force and bears the spring force of this Returnning spring 62c.This hydraulic chamber 62a is communicated with the oil circuit 20a, the 20b that form on above-mentioned input shaft 20, and this oil circuit 20a extends to an end of housing 3, is communicated with the oil circuit 91 of the hub portion 3c of sleeve shape on the input shaft 20.Therefore, this oil circuit 91 is communicated with not shown hydraulic control device.Promptly, form the oil circuit of never illustrated hydraulic control device to hydraulic chamber 62a so pass through hub portion 3c and 1 pair of seal ring between the input shaft 20 81 of seal casinghousing 3 because above-mentioned Hydrauservo System 62 is configured on the input shaft 20.
In addition, this Hydrauservo System 61 is by the piston element that is used to press friction plate 71 (the 2nd piston) 61b, hydraulic chamber (the 2nd hydraulic servo hydraulic chamber) 61a that between cylinder part 61e, this piston element 61b and this cylinder part 61e, utilizes seal ring 61f, 61g sealing to form, this piston element 61b is constituted towards stressed Returnning spring 61c of the direction of this hydraulic chamber 61a and the restoring board 61d that bears the spring force of this Returnning spring 61c.This hydraulic chamber 61a is communicated with the oil circuit 92 of above-mentioned hub portion 3c, and this oil circuit 92 is communicated with not shown hydraulic control device.Be the hub portion 3c and 1 pair seal ring cylinder part 61e between 80 formation never illustrated hydraulic control device oil circuit to hydraulic chamber 61a of above-mentioned Hydrauservo System 61 by seal casinghousing 3.
Be that above-mentioned input shaft 20 is connected with above-mentioned drum type parts 21, the outer circumferential side of these drum type parts 21 is connected with above-mentioned wheelboss part 22.All sides dispose by clutch C1 with the spline combination and use Hydrauservo System 62 and the clutch C1 of free combination in the end of this wheelboss part 22, and interior all sides of this clutch C1 are connected with hub portion 23 with the spline combination.Therefore, interior all sides of this hub portion 23 connect integrally formed above-mentioned sun gear S2 on the end outer circumferential side of the other end of this housing part 26 with an end of the housing part that rotates freely (parts that are connected with the 2nd rotation key element) 26 on central shaft 30.
In addition, the end outer circumferential side of above-mentioned hub portion 22 disposes by clutch C2 with the spline combination and uses Hydrauservo System 61 and the clutch C2 of free combination, and the outer circumferential side of this clutch C2 is connected with interior all sides of drum type parts 24 with the spline combination.Dispose overrunning clutch (the 1st overrunning clutch) F3 between one end of these drum type parts 24 (right side among the figure) outer circumferential side and the gearbox casing 3b, the rotation of a direction of these drum type parts 24 is limited.In addition, interior all sides of the other end of these drum type parts (left side among the figure) are connected with connected element 25 with the spline combination, and are connected with the side plate 44 of above line gear rack CR2.
On the other hand, dispose hub portion 32 with formation Hydrauservo System 66, friction plate 76, clutch drum (the 3rd clutch drum) and the multidisc clutch of the hub portion 33 that is connected with drum type parts 31, planetary carrier CR1 (as the 3rd clutch of the rotation output mechanism that slows down) C3 on the central shaft 30.This Hydrauservo System 66 is by the piston element 66b that is used to press friction plate 76, the hydraulic chamber 66a that utilizes seal ring 66f, 66g sealing to form at drum type parts 31, between this piston element 66b and the 66e of this cylinder portion with the 66e of cylinder portion, this piston element 66b is constituted towards stressed Returnning spring 66c of the direction of this hydraulic chamber 66a and the restoring board 66d that bears the spring force of this Returnning spring 66c.In addition, the clutch drum of being made up of hub portion 32 and drum type parts 31 is to the direction opening of epicyclic reduction gear PR, this epicyclic reduction gear PR be configured in Hydrauservo System 66 and planetary gear unit PU axially between.In addition, friction plate 76 is configured in the position with the radial outer diameter side superimposed of epicyclic reduction gear PR.
This hydraulic chamber 66a extends to housing 3 and the other end above-mentioned hub portion 3c opposition side, is communicated with the oil circuit 93 of the hub portion 3d of sleeve shape on the central shaft 30, and this oil circuit 93 is communicated with not shown hydraulic control device.The hub portion 3d that is above-mentioned Hydrauservo System 66 by seal casinghousing 3 and have 1 pair of seal ring 82 between the drum type parts 61 of the 66e of cylinder portion forms the oil circuit of never illustrated hydraulic control device to hydraulic chamber 66a.
Promptly with central shaft 30 that above-mentioned input shaft 20 is connected on, be connected with drum type parts 31 with these input shaft 20 opposition sides (left side among the figure), the outer circumferential side of these drum type parts 31 is connected with hub portion 32.All sides dispose by clutch C3 with the spline combination and use Hydrauservo System 66 and the clutch C3 of free combination in the end of this hub portion 32, and interior all sides of this clutch C3 are connected with the extension of spline combination with the side plate 33 of above line gear rack CR1.This planetary carrier CR1 has above-mentioned small gear P1 and the small gear P2 that is supported by this side plate 33 and side plate 34, the sun gear S1 that can rotate freely on the axle engagement of this small gear P2 and sleeve shape.The end of this sun gear S1 is connected with hub portion 35, the outer circumferential side of this hub portion 35 has break B1 with Hydrauservo System 65 and friction plate 75, and the friction plate 75 of multi-plate brake (the 1st break) B1 by these Hydrauservo System 65 free combinations is with the spline combination.Therefore, the outer circumferential side of the friction plate 75 of this break B1 combines with spline with the spline 3s that interior all side at above-mentioned gearbox casing 3b forms.
In addition, above-mentioned small gear P1 meshes with ring gear R1 as mentioned above, and interior all side one ends of this ring gear R1 are supported on the above-mentioned central shaft 30 with rotating freely, with the transferring elements (as the rotation output mechanism that slows down) 40 of the rotation of transmitting this ring gear R1 1Connect.This transferring elements 40 1The outer circumferential side of opposition side (right side among the figure) of the part that is connected with ring gear R1 be formed with spline 40s, this spline 40s (left side in the drawings) and wheelboss part 46 combine by spline, (right side in the drawings) is by spline combination and housing part 41 simultaneously 1In conjunction with.The outer circumferential side of this wheelboss part 46 has break B2 with Hydrauservo System 64 and friction plate 74, and the friction plate 74 of break (the 2nd break) B2 that freely locks by this Hydrauservo System 64 is with the spline combination.The outer circumferential side of the friction plate 74 of this break B2 and above-mentioned break B1 are same, combine with spline with the spline 3s that interior all side at above-mentioned gearbox casing 3b forms.
Above-mentioned housing part 41 1The sun gear S3 of the integrally formed above-mentioned planetary gear unit PU of interior all sides, this sun gear S1 as mentioned above, with the long small gear PL engagement of being supported by the side plate 42 of planetary carrier CR2 and side plate 44.In addition, as implied above, short and small gear PS is supported between this side plate 44 and the side plate 43, and the outer circumferential side of this side plate 43 is connected with wheelboss part 47.The outer circumferential side of this wheelboss part 47 has break B4 with Hydrauservo System 63 and friction plate 73, and the friction plate 73 of break (the 3rd break) B4 that freely locks with Hydrauservo System 63 by this break B4 is with the spline combination.The outer circumferential side of the friction plate 73 of this break B4 and above-mentioned break B1 and break B2 are same, combine with spline with the spline 3s that interior all side at above-mentioned gearbox casing 3b forms.
Like this, meshing ring gear R2 as mentioned above on above-mentioned long small gear PL, the end of this ring gear R2 is connected with connected element 45, and this ring gear R2 is connected with counter shaft gear 50 by connected element 45.This counter shaft gear 50 as shown in Figure 1, be fixed on above-mentioned in the middle of gear 51 engagements on the jack shaft 52 of axial region 4, this jack shaft 52 meshes with the gear 53 of differential mechanism portion 5 by the gear 52a that forms on the outer circumferential face.Then, this gear 53 is fixed on the case shell 54, and this case shell 54 is connected with not shown left and right sides axletree by differential gear 55.
As above shown in the explanation, dispose clutch C1 and clutch C2 on the input shaft 20, dispose counter shaft gear 50, planetary gear unit PU, epicyclic reduction gear PR on the central shaft 30 successively, be the axial side configuration epicyclic reduction gear PR of planet gear unit PU, axially opposite side disposes clutch C1 and clutch C2, disposes counter shaft gear 50 between clutch C1 and clutch C2 and planetary gear unit PU.In addition, clutch C3 and break B1 are configured in the outer circumferential side of epicyclic reduction gear PR, and break B2 and break B4 are configured in the outer circumferential side of planetary gear unit PU.In addition, epicyclic reduction gear PR, planetary gear unit PU and counter shaft gear 50 are set to coaxial configuration with input shaft 20.
Then, according to said structure, automatic transmission 1 is described in conjunction with Fig. 3, Fig. 4 and Fig. 5 1Effect.And in speed line chart shown in Figure 5, the longitudinal axis is represented the rotating speed of each rotation key element, and transverse axis then rotates the gear ratio of key elements corresponding to these.In addition, in the part of the planetary gear unit PU of this speed line chart, the longitudinal axis of lateral ends (right side among Fig. 5) is corresponding to sun gear S3, and the longitudinal axis is left successively corresponding to planetary carrier CR2, ring gear R2, sun gear S2 among the figure.
As shown in Figure 3, by the combination of clutch C1, the rotation of input shaft 20 is input to above-mentioned sun gear S2.By the combination of clutch C2, the rotation of input shaft 20 is input to above line gear rack CR2, the rotation of this planetary carrier CR2 simultaneously fix freely by the combination of break B4, and limits the rotation of a direction by overrunning clutch F3.
On the other hand, by the combination of clutch C3, the rotation of input shaft 20 is input to above line gear rack CR1.The rotation of above-mentioned sun gear S1 is fixed freely by the combination of break B1.Above-mentioned ring gear R1 is by transferring elements 40 1And housing part 41 1Be connected with above-mentioned sun gear S3, the rotation of this ring gear R1 and sun gear S3 is fixed freely by the combination of break B2.And the rotation of above-mentioned ring gear R2 outputs to above-mentioned counter shaft gear 50, and outputs to not shown driving wheel by this counter shaft gear 50, above-mentioned middle axial region 4 and differential mechanism portion 5 (with reference to Fig. 1).
As shown in Figure 4,1 retaining that advances in D (driving) position, clutch C1 and overrunning clutch F3 combination.Like this, as shown in Figure 5, the rotation of input shaft 20 is input to sun gear S2 by clutch C1, and the rotation of planetary carrier CR2 simultaneously is limited in a direction (being rotated in the forward direction), promptly prevents the counterrotating of planetary carrier CR2 and is in stationary state.Then, the rotation that is input to the input shaft 20 of sun gear S2 outputs to ring gear R2 by fixing planetary carrier CR2, from counter shaft gear 50 outputs being rotated in the forward as 1 retaining that advances.In addition, at this moment among the above-mentioned epicyclic reduction gear PR, by the deceleration rotation of sun gear S3 to ring gear R1 output counter-rotating, and by break B1 in conjunction with fixed stars gear S1, because clutch C3 is released, planetary carrier CR1 is in idling conditions, particularly transmitting torque not.And, during engine braking, break B4 combination, planetary carrier CR2 fixes, thereby prevents being rotated in the forward of this planetary carrier CR2, keeps the state of above-mentioned 1 retaining that advances.
In addition, when this advances 1 retaining, prevent the counterrotating of planetary carrier CR2 by overrunning clutch F3, and make to be rotated in the forward and become possibility, can realize switching to 1 retaining that advances when travelling reposefully by the automatic combination of overrunning clutch from for example non-position of travelling.In addition, this overrunning clutch F3 accepts the rotation of input shaft 20 by sun gear S2, for example the torque when accept slowing down rotation is little, so this overrunning clutch F3 or connect this overrunning clutch F3 and that the drum type parts 24 of clutch C2 just there is no need to do is very big.
As shown in Figure 4,2 retainings that advance in D (driving) position, clutch C1 combination, break B2 braking.Like this, as shown in Figure 5, the rotation of input shaft 20 is input to sun gear S2 by clutch C1, and the braking owing to break B2 simultaneously makes sun gear S3 fix.Like this, the rotation of planetary carrier CR2 is slowed down a little, and the planetary carrier CR2 of rotation by this deceleration rotation that is input to the input shaft 20 of sun gear S2 outputs to ring gear R2, from counter shaft gear 50 outputs being rotated in the forward as 2 retainings that advance.In addition, among the above-mentioned epicyclic reduction gear PR, sun gear S3 and ring gear R1 fix by the braking of break B2 at this moment, and clutch C3 is released, and planetary carrier CR1 and sun gear S1 are in braking state.
As shown in Figure 4,3 retainings that advance in D (driving) position, clutch C1 and clutch C3 combination, break B1 braking.Like this, as shown in Figure 5, the rotation of input shaft 20 is input to planetary carrier CR1 by clutch C3, is input to sun gear S2 by clutch C1.Braking owing to break B1 simultaneously makes sun gear S1 fix.Like this, the rotation of the input shaft 20 by being input to planetary carrier CR1 and fixing sun gear S1, the ring gear R1 rotation of slowing down is by above-mentioned transferring elements 40 1And housing part 41 1The rotation of should slowing down outputs to sun gear S3.Like this, owing to the rotation of the input shaft 20 that is input to sun gear S2 and the deceleration rotation of sun gear S3, planetary carrier CR2 is with only big slightly than the deceleration rotation of this sun gear S3 deceleration rotation.Then, the planetary carrier CR2 of rotation by this deceleration rotation that is input to the input shaft 20 of sun gear S2 outputs to ring gear R2, from counter shaft gear 50 outputs being rotated in the forward as 3 retainings that advance.In addition, this moment is because sun gear S3 and ring gear R1 are the rotation of slowing down, so above-mentioned transferring elements 40 1And housing part 41 1Can transmit bigger torque.
As shown in Figure 4,4 retainings that advance in D (driving) position, clutch C1 and clutch C2 combination.Like this, as shown in Figure 5, the rotation of input shaft 20 is input to sun gear S2 by clutch C1, is input to planetary carrier CR1 by clutch C2.Like this, since be input to sun gear S2 input shaft 20 rotation and be input to the rotation of the input shaft 20 of planetary carrier CR2, promptly be in direct-connected rotation status, the rotation of input shaft 20 intactly outputs to ring gear R2, from counter shaft gear 50 outputs being rotated in the forward as 4 retainings that advance.In addition, at this moment among the above-mentioned epicyclic reduction gear PR, the rotation of input shaft 20 is input to planetary carrier CR1 by clutch C3, and be input to ring gear R1 from the rotation (direct-connected rotation) of the input shaft 20 of sun gear S3, break B1 discharges, sun gear S1 is in idling conditions, not transmitting torque.
As shown in Figure 4,5 retainings that advance in D (driving) position, clutch C2 and clutch C3 combination, break B1 braking.Like this, as shown in Figure 5, the rotation of input shaft 20 is input to planetary carrier CR1 by clutch C3, is input to planetary carrier CR2 by clutch C2.Simultaneously, the braking owing to break B1 makes sun gear S1 fix.Like this, owing to be input to the rotation of input shaft 20 of planetary carrier CR1 and fixing sun gear S1, the ring gear R1 rotation of slowing down is by above-mentioned transferring elements 40 1And housing part 41 1The rotation of should slowing down outputs to sun gear S3.Like this, because the deceleration of sun gear S3 rotation and imported the planetary carrier CR2 of the rotation of input shaft 20 forms the speedup rotation and also outputs to ring gear R2, from counter shaft gear 50 outputs being rotated in the forward as 5 retainings that advance.In addition, this moment is the same with the state of above-mentioned 3 retainings that advance, because sun gear S3 and ring gear R1 are the rotation of slowing down, above-mentioned transferring elements 40 1And housing part 41 1Can transmit bigger torque.
As shown in Figure 4,6 retainings that advance in D (driving) position, clutch C2 combination, break B2 braking.Like this, as shown in Figure 5, the rotation of input shaft 20 is input to planetary carrier CR2 by clutch C2.Simultaneously, the braking owing to break B2 makes sun gear S3 fix.Like this, owing to be input to the rotation of input shaft 20 of planetary carrier CR2 and fixing sun gear S3, form (greater than above-mentioned 5 retainings that advance) speedup rotation, and output to ring gear R2, from counter shaft gear 50 outputs being rotated in the forward as 6 retainings that advance.In addition, among the above-mentioned epicyclic reduction gear PR, identical with the states of above-mentioned 2 retainings that advance at this moment, sun gear S3 and ring gear R1 are owing to the braking of break B2 is fixed, and clutch C3 discharges, and planetary carrier CR1 and sun gear S1 are in halted state.
As shown in Figure 4,1 retaining that falls back in R (reversing gear) position, clutch C3 combination, break B1 and break B4 braking.Like this, as shown in Figure 5, the rotation of input shaft 20 is input to planetary carrier CR1 by clutch C3.Simultaneously, owing to the braking of break B1 makes sun gear S1 fix, owing to the braking of break B4 makes planetary carrier CR2 fix.Like this, owing to be input to the rotation of input shaft 20 of planetary carrier CR1 and fixing sun gear S1, the ring gear R1 rotation of slowing down is by above-mentioned transferring elements 40 1And housing part 41 1The rotation of should slowing down outputs to sun gear S3.Like this, because the deceleration of sun gear S3 is rotated and fixing planetary carrier CR2, to ring gear R2 output, export as 1 counterrotating that keeps off that falls back from counter shaft gear 50 as counterrotating.In addition, this moment is the same with the state of above-mentioned advance 3 retainings or above-mentioned 5 retainings that advance, because sun gear S3 and ring gear R1 are the rotation of slowing down, above-mentioned transferring elements 40 1And housing part 41 1Can transmit bigger torque.
In addition, though break B4 this moment accepts the rotation of the sun gear S3 of input deceleration rotation, but because this break B4 is arranged on the closer position of the outer circumferential side of planetary gear unit PU, can be shorter so transmit the wheelboss part 47 of the torque of rotating based on this deceleration.
P (parking) or N (neutral) position, clutch C1, clutch C2 and clutch C3 discharge, and the transmission of power between input shaft 20 and the counter shaft gear 50 is in dissengaged positions, automatic transmission 2 1Integral body is in idling conditions (neutral state).In addition, though the break B1 of fixed stars gear S1 braking, this just frequently makes this break B1 braking discharge in order to prevent repeatedly, to automatic transmission 2 1The not influence of rotation status of other interior rotation key elements.
In addition, above-mentioned automatic transmission 1 1In, as mentioned above, though above-mentioned clutch C3 combination under the state of 3 retainings that advance, advance 5 retainings and 1 retaining that falls back, the rotation of input shaft 20 is input to planetary carrier CR1, but be not limited thereto, if clutch C3 is placed between ring gear R1 and the sun gear S3, make planetary carrier CR1 and input shaft 20 be in coupled condition always, even under the state of above-mentioned 3 retainings that advance, advance 5 retainings and 1 retaining that falls back, make this clutch C3 combination, also can pass through epicyclic reduction gear PR, clutch C3 and transferring elements 40 equally 1The rotation of will slowing down outputs to sun gear S3, and 6 retainings and 1 retaining that falls back equally obtain advancing.But the clutch C3 of this moment compares with the above-mentioned mode of execution of connecting the rotation that disconnects input shaft 20 for connecting the parts that disconnect the rotation of slowing down, and needs to connect to disconnect bigger torque, thereby needs bigger parts.
As mentioned above, according to automatic transmission 1 of the present invention 1, as epicyclic reduction gear PR, clutch C3 and the transferring elements 40 of the rotation output mechanism that slows down 1Be configured in the axial side (left side among Fig. 1, Fig. 2 and Fig. 3) of planetary gear unit PU, clutch C1 and clutch C2 are configured in the axial opposite side (right side among Fig. 1, Fig. 2 and Fig. 3) of planetary gear unit PU, and, counter shaft gear 50 as output block is configured between clutch C1 and clutch C2 and the planetary gear unit PU, so particularly can make epicyclic reduction gear PR and planetary gear unit PU near configuration, thereby transmit the transferring elements 40 of the rotation of slowing down 1And housing part 41 1Axial length can be shorter.Like this, can realize automatic transmission 1 1Miniaturization, light, simultaneously because transferring elements 40 1And housing part 41 1Light, can reduce inertial force, so can improve automatic transmission 1 1Controlled, reduce speed change and impact.
In addition, because the outer circumferential side of clutch C2 by clutch C1 be connected with planetary carrier CR2, thereby the parts can prevent that respectively rotating key element connects the time interlock realization automatic transmission 1 1Miniaturization.
In addition, though clutch C1 disposes clutch C2 at its outer circumferential side, can not be to the outer circumferential side enlarged, but by Hydrauservo System 62 is set on input shaft 20, (for example with respect to situation about on hub portion 3c, being provided with), can guarantee this bigger Hydrauservo System 62, the especially compression area of Hydrauservo System 62 usefulness hydraulic chamber 62a in interior all sides, thereby can increase the capacity of clutch C1.
In addition and since with input shaft 20 on coaxial epicyclic reduction gear PR, planetary gear unit PU and counter shaft gear 50 are set, so particularly on the FF vehicle, carry automatic transmission 1 1The time, (for example comparing with the situation that epicyclic reduction gear etc. is set on other) can realize the miniaturization of driving wheel transfer mechanism (for example axial region 4 etc.), improves automatic transmission 1 1Vehicle boarded performance.
In addition, for example as disclosed open 2001-263438 communique etc. the spy in, if clutch C3 is configured between ring gear R1 and the sun gear S3, just need to connect and disconnect the rotation of slowing down, thereby need bigger parts, and the distance between epicyclic reduction gear PR and the planetary gear unit PU increases, but owing to be to be configured between input shaft 20 and the planetary carrier CR1, connect the rotation that disconnects input shaft 20 by this clutch C3, thereby connect the deceleration rotation that disconnects from the ring gear R1 output of epicyclic reduction gear PR, therefore can realize the miniaturization of clutch C3, and epicyclic reduction gear PR and planetary gear unit PU are disposed on closer locations.Can realize automatic transmission 1 like this 1Miniaturization.
In addition, because Hydrauservo System 62 is arranged on the input shaft 20, utilize a pair of seal ring 81 to stop leakage and oil circuit 20a, 20b fuel feeding in being arranged on input shaft 20 from housing 3, so needn't between for example input shaft 20 and Hydrauservo System 62, seal ring be set, just can be to the hydraulic chamber 62a of Hydrauservo System 62 fuel feeding.In addition, Hydrauservo System 61,66 can be respectively by extending hub portion 3c, the 3d fuel feeding that is provided with from housing 3, and by for example other parts, just can fuel feeding, promptly can carry out fuel feeding by a pair of seal ring 80,82 is set respectively.Therefore, as long as a pair of seal ring 81,80,82 is set respectively in Hydrauservo System 62,61,66, just can fuel feeding, thus minimum is reduced in the sliding friction that seal ring causes, its result can improve automatic transmission 1 1Efficient.
In addition, because friction plate 33 is configured in the outer radial periphery side of epicyclic reduction gear PR, thereby can make automatic transmission 1 1In axial miniaturization.In addition, because between the Hydrauservo System 66 by epicyclic reduction gear PR being configured in clutch C3 and planetary gear unit PU axial, epicyclic reduction gear PR and planetary gear unit PU can disposed adjacent (because the Hydrauservo System of clutch C3 66 is not between epicyclic reduction gear PR and planetary gear unit PU), thus transferring elements 40 1And housing part 41 1Can be shorter.Like this, can realize automatic transmission 1 1Miniaturization and light, simultaneously owing to can reduce inertial force, so can improve automatic transmission 1 1Controlled, reduce speed change and impact.
In addition, because epicyclic reduction gear PR is the double pinion planetary pinion, thereby the rotation that can make input shaft 20 is as the rotation output of slowing down, even set good automatic transmission 1 simultaneously 1The gear ratio, what also need not increase planetary gear unit, epicyclic reduction gear respectively rotates key element, thereby can suppress high speed rotating, realizes automatic transmission 1 1Miniaturization.
In addition, rotate rows of elements gear rack CR1, fixed factors sun gear S1, output rotation key element ring gear R1 because epicyclic reduction gear PR comprises input, thereby the rotation of input shaft 20 can be exported as the rotation of slowing down.
In addition, because planetary gear unit PU ties up Nao formula planetary pinion for drawing of being made up of sun gear S2, sun gear S3, planetary carrier CR2 and ring gear R2, so in 6 retainings of can realizing for example advancing, 1 retaining that falls back, can also make epicyclic reduction gear PR and planetary gear unit PU near configuration, thereby can shorten the transferring elements 40 that transmits the rotation of slowing down 1And housing part 41 1
In addition, owing to have and dispose side by side with break B4 and at the overrunning clutch F3 of the rotation of a direction restrictions planetary gear frame CR2, therefore 1 retaining that advances when realizing for example just driving of clutch C1 and overrunning clutch F3 can be utilized, thereby 1 retaining that advances when travelling can be realized switching to reposefully from for example non-position of travelling.
In addition, because break B4 is configured in outer circumferential side, overrunning clutch F3 and the clutch C2 disposed adjacent of planetary gear unit PU, when realizing advancing 1 retaining, overrunning clutch F3 combines with the clutch C1 of the rotation of input input shaft simultaneously.Corresponding therewith, break B4 combine to realize falling back and 1 keeps off with connecting the clutch C3 that disconnects the rotation of slowing down simultaneously, so acts on anti-torque on the break B4 greater than the anti-torque that acts on the overrunning clutch F3.Like this, be provided with, can shorten and to arrive the wheelboss part 47 of break B4 based on the transmission of torque of the rotation of slowing down by the outer circumferential side that makes break B4 and planetary gear unit PU is close.In addition, even overrunning clutch F3 is arranged near the clutch C2 that leaves planetary gear unit PU, also there is no need to strengthen wheelboss part 25 and the side plate 44 that connects clutch C2 and planetary carrier CR2.In addition, by not at the periphery configuration overrunning clutch F3 of planetary gear unit PU, can increase the design freedom of break.Like this, can realize automatic transmission 1 1Miniaturization and light.
In addition, shown in the speed line chart, in realize advancing 6 retainings, 1 retaining that falls back, can make epicyclic reduction gear PR and planetary gear unit PU, transmit the transferring elements 40 that slows down and rotate thereby can shorten near configuration 1And housing part 41 1Like this, can realize automatic transmission 1 1Miniaturization and light, simultaneously owing to can reduce inertial force, so can improve automatic transmission 1 1Controlled, reduce speed change and impact.
In addition, structure as realize advancing 6 retainings, 1 retaining that falls back, clutch C1, the C2 combination simultaneously in 4 retainings owing to advance, promptly be in direct-connected state at 4 retainings that advance, thereby can set the gear ratio of higher advance 5 retainings and 6 retainings that advance, when particularly carrying on vehicle, for the vehicle of running at high speed, can reduce the rotating speed of motor, thereby the quiet characteristic of the vehicle of running at high speed is provided.
In addition, as the driving wheel transfer mechanism, have to the differential mechanism portion 5 of driving wheel output rotation and the middle axial region 4 that combines with this differential mechanism portion 5, output block is the counter shaft gear that meshes with middle axial region 4, thereby can be with automatic transmission 1 1Lift-launch is on FF vehicle for example.
(the 2nd mode of execution)
The 1st mode of execution is made the 2nd mode of execution of part change below in conjunction with Fig. 6 to Figure 10 explanation.Fig. 6 is the cross section unfolded drawing of the automatic transmission of expression the 2nd mode of execution.Fig. 7 is the cross section unfolded drawing of the automatic transmission of the automatic transmission of expression the 2nd mode of execution.Fig. 8 is the schematic diagram of the automatic transmission of expression the 2nd mode of execution.Fig. 9 is the action schedule of the automatic transmission of the 2nd mode of execution.Figure 10 is the speed line chart of the automatic transmission of the 2nd mode of execution.In addition, the 2nd mode of execution is except the part change, and the part identical with the 1st mode of execution adopted identical symbol, and it illustrates omission.
As shown in Figure 6, the automatic transmission 1 of the 2nd mode of execution 2The automatic transmission 1 of relative the 1st mode of execution 1(with reference to Fig. 1), between planetary gear unit PU and epicyclic reduction gear (as the rotation output mechanism that slows down) PR, dispose overrunning clutch (the 2nd overrunning clutch) F2, and break (the 4th break) B3 of the combination that disconnects this overrunning clutch F2 is connected in configuration.
As shown in Figure 7, the transferring elements 40 that is connected with the ring gear R1 of epicyclic reduction gear PR 2With the housing part 41 integrally formed with the sun gear S3 of planetary gear unit PU 2By the spline combination.In addition, this housing part 41 2Integrally formed with the inner ring of overrunning clutch F2, outer ring and the wheelboss part 48 of this overrunning clutch F2 are integrally formed.The outer circumferential side of this wheelboss part 48 has break B3 Hydrauservo System 67 and friction plate 77, break (the 4th break) B3 that freely locks with Hydrauservo System 67 by this break B3 and this friction plate 77 combine configuration by spline, and the outer circumferential side of the friction plate 77 of this break B3 combines by spline with the spline 3s of interior all side formation of above-mentioned gearbox casing 3b.In addition, the wheelboss part 46 that combines by spline with break B2 is at interior all sides and housing part 41 2By the spline combination, promptly by this housing part 41 2By spline and transferring elements 40 2In conjunction with.
Then, according to said structure, automatic transmission 1 is described in conjunction with Fig. 8, Fig. 9 and Figure 10 2The effect of overrunning clutch F2.Identical with above-mentioned the 1st mode of execution, in speed line chart shown in Figure 10, the longitudinal axis is represented the rotating speed of each rotation key element, and transverse axis then rotates the gear ratio of key elements corresponding to these.In addition, in the part of the planetary gear unit PU of this speed line chart, the longitudinal axis of lateral ends (right side among Figure 10) is corresponding to sun gear S3, and the longitudinal axis is left successively corresponding to planetary carrier CR2, ring gear R2, sun gear S2 among the figure.
As shown in Figure 8, this overrunning clutch F2 and break B2 dispose side by side, utilize the braking of break B3, by above-mentioned housing part 41 2, be sun gear S3 and transferring elements 40 2Restriction ring gear R1 rotates towards a direction (being rotated in the forward direction).
Like this, as shown in Figure 9,2 retainings that advance in D (driving) position, clutch C1 combination, break B3 combination, thereby overrunning clutch F2 combination.Like this, as shown in figure 10, the rotation of input shaft 20 is input to sun gear S2 by clutch C1, passes through the combination of break B3 simultaneously, overrunning clutch F2 makes the rotation of sun gear S3 be limited in a direction (being rotated in the forward direction), prevents the counterrotating of this sun gear S3.Like this, planetary carrier CR2 slows down a little, and the planetary carrier CR2 of rotation by this deceleration rotation that is input to the input shaft 20 of sun gear S2 outputs to ring gear R2, from the be rotated in the forward output of counter shaft gear 50 as 2 retainings that advance.In addition, among the above-mentioned epicyclic reduction gear PR, sun gear S3 and ring gear R1 are owing to prevent counterrotating by overrunning clutch F2 at this moment, and clutch C3 is released, and planetary carrier CR1 and sun gear S1 are in halted state.
In addition, 1 retaining changes to 2 whens retaining of advancing from advancing, break B3 combination, prevent the counter-rotating of sun gear S3 by overrunning clutch F2, sun gear S2 is for being rotated in the forward, overrunning clutch F3 in the 1 retaining combination of advancing discharges automatically, thereby prevents for example driving of motor, and speed change is advanced to this and 2 kept off reposefully.In addition, during engine braking, with the break B2 braking that overrunning clutch F2 is set up in parallel, fixed stars gear S3 (and ring gear R1) prevents being rotated in the forward of this sun gear S3, keeps the state of above-mentioned 2 retainings that advance.
As mentioned above, utilize automatic transmission 1 of the present invention 2, as epicyclic reduction gear PR, clutch C3 and the transferring elements 40 of the rotation output mechanism that slows down 2Be configured in the axial side (left side among Fig. 6, Fig. 7 and Fig. 8) of planetary gear unit PU, clutch C1 and clutch C2 are configured in the axial opposite side (right side among Fig. 6, Fig. 7 and Fig. 8) of planetary gear unit PU, counter shaft gear 50 as output block is configured between clutch C1 and clutch C2 and the planetary gear unit PU, particularly can make epicyclic reduction gear PR and planetary gear unit PU near configuration, thereby transmit the transferring elements 40 of the rotation of slowing down 2And housing part 41 2Axial length can be shorter.Like this, can realize automatic transmission 1 2Miniaturization, light, simultaneously because transferring elements 40 2And housing part 41 2Light, can reduce inertial force, so can improve automatic transmission 1 2Controlled, reduce speed change and impact.
In addition, because the outer circumferential side of clutch C2 by clutch C1 be connected with planetary carrier CR2, thereby the parts can prevent that respectively rotating key element connects the time interlock realization automatic transmission 1 2Miniaturization.
In addition, though clutch C1 disposes clutch C2 at its outer circumferential side, can not be to the outer circumferential side enlarged, but by Hydrauservo System 62 is set on input shaft 20, (for example with respect to situation about on hub portion 3c, being provided with), can guarantee this bigger Hydrauservo System 62, the especially compression area of Hydrauservo System 62 usefulness hydraulic chamber 62a in interior all sides, thereby can increase the capacity of clutch C1.
In addition, owing on coaxial, epicyclic reduction gear PR, planetary gear unit PU and counter shaft gear 50 are set, particularly on the FF vehicle, carry automatic transmission 1 with input shaft 20 2The time, (for example with respect to the situation that epicyclic reduction gear etc. is set on other) can realize the miniaturization of driving wheel transfer mechanism (for example axial region 4 etc.), improves automatic transmission 1 2Vehicle boarded performance.
In addition, identical with the 1st mode of execution, if clutch C3 is configured between ring gear R1 and the sun gear S3, just need to connect and disconnect the rotation of slowing down, thereby need bigger parts, and the distance between epicyclic reduction gear PR and the planetary gear unit PU increases, but owing to be to be configured between input shaft 20 and the planetary carrier CR1, connect the rotation that disconnects input shaft 20 by this clutch C3, thereby connect the deceleration rotation that disconnects from the ring gear R1 output of epicyclic reduction gear PR, therefore can realize the miniaturization of clutch C3, and epicyclic reduction gear PR and planetary gear unit PU are disposed on closer locations.Can realize automatic transmission 1 like this 2Miniaturization.
In addition, because Hydrauservo System 62 is arranged on the input shaft 20, utilize a pair of seal ring 81 preventions and oil circuit 20a, 20b fuel feeding in being arranged on input shaft 20 from housing 3, so needn't between for example input shaft 20 and Hydrauservo System 62, seal ring be set, just can be to the hydraulic chamber 62a of Hydrauservo System 62 fuel feeding.In addition, Hydrauservo System 61,66 can be respectively by extending hub portion 3c, the 3d fuel feeding that is provided with from housing 3, and by for example other parts, just can fuel feeding, promptly carry out fuel feeding by a pair of seal ring 80,82 is set respectively.Therefore, as long as a pair of seal ring 81,80,82 is set respectively in Hydrauservo System 62,61,66, just can fuel feeding, thus minimum is reduced in the sliding friction that seal ring causes, its result will improve automatic transmission 1 2Efficient.
In addition, because friction plate 33 is configured in the outer radial periphery side of epicyclic reduction gear PR, thereby can make automatic transmission 1 in the axial direction 2Miniaturization.In addition, because between the Hydrauservo System 66 by epicyclic reduction gear PR being configured in clutch C3 and planetary gear unit PU axial, epicyclic reduction gear PR and planetary gear unit PU can disposed adjacent (because the Hydrauservo System of clutch C3 66 is not between epicyclic reduction gear PR and planetary gear unit PU), thus transferring elements 40 2And housing part 41 2Can be shorter.Like this, can realize automatic transmission 1 2Miniaturization and light, simultaneously owing to can reduce inertial force, so can improve automatic transmission 1 2Controlled, reduce speed change and impact.
In addition, because epicyclic reduction gear PR is the double pinion planetary pinion, thereby the rotation that can make input shaft 20 is as the rotation output of slowing down, even set good automatic transmission 1 simultaneously 2The gear ratio, what also need not increase planetary gear unit, epicyclic reduction gear respectively rotates key element, thereby can suppress high speed rotating, realizes automatic transmission 1 2Miniaturization.
In addition, rotate rows of elements gear rack CR1, fixed factors sun gear S1, output rotation key element ring gear R1 because epicyclic reduction gear PR comprises input, thereby the rotation of input shaft 20 can be exported as the rotation of slowing down.
In addition, because planetary gear unit PU ties up Nao formula planetary pinion for drawing of being made up of sun gear S2, sun gear S3, planetary carrier CR2 and ring gear R2, so in 6 retainings of can realizing for example advancing, 1 retaining that falls back, can also make epicyclic reduction gear PR and planetary gear unit PU near configuration, thereby can shorten the transferring elements 40 that transmits the rotation of slowing down 2And housing part 41 2
In addition, owing to have and dispose side by side with break B4 and at the overrunning clutch F3 of the rotation of a direction restrictions planetary gear frame CR2, so can utilize 1 retaining that advances when realizing for example just driving of clutch C1 and overrunning clutch F3, thereby can realize switching to 1 retaining that advances when travelling reposefully from for example non-position of travelling.
In addition, because break B4 is configured in outer circumferential side, overrunning clutch F3 and the clutch C2 disposed adjacent of planetary gear unit PU, when realizing advancing 1 retaining, overrunning clutch F3 combines with the clutch C1 of input input shaft rotation simultaneously.Corresponding therewith, break B4 combine to realize falling back and 1 keeps off with connecting the clutch C3 that disconnects the rotation of slowing down simultaneously, so acts on anti-torque on the break B4 greater than the anti-torque that acts on the overrunning clutch F3.Like this, by making break B4, can shorten and to arrive the wheelboss part 47 of break B4 based on the transmission of torque of the rotation of slowing down in the close setting of the outer circumferential side of planetary gear unit PU.In addition, even overrunning clutch F3 is arranged near the clutch C2 that leaves planetary gear unit PU, also there is no need to strengthen wheelboss part 25 and the side plate 44 that connects clutch C2 and planetary carrier CR2.In addition, by not at the periphery configuration overrunning clutch F3 of planetary gear unit PU, can increase the design freedom of break.Like this, can realize automatic transmission 1 2Miniaturization and light.
In addition, owing to have the overrunning clutch F2 towards a direction rotation with configuration, that the pass through break B3 side by side braking limiting star gear S3 of break B2, thus can change to 3 retainings that advance from 2 retainings that advance reposefully.
In addition, because inner ring and the housing part 41 of overrunning clutch F2 2Integrally formed, thus can change to 3 retainings that advance from 2 retainings that advance reposefully, especially radially can realize automatic transmission 1 simultaneously 2Miniaturization.
In addition, shown in the speed line chart, in realize advancing 6 retainings, 1 retaining that falls back, can make epicyclic reduction gear PR and planetary gear unit PU, transmit the transferring elements 40 that slows down and rotate thereby can shorten near configuration 2And housing part 41 2Like this, can realize automatic transmission 1 2Miniaturization and light, simultaneously owing to can reduce inertial force, so can improve automatic transmission 1 2Controlled, reduce speed change and impact.
In addition, structure as realize advancing 6 retainings, 1 retaining that falls back, clutch C1, the C2 combination simultaneously in 4 retainings owing to advance, promptly be in direct-connected state at 4 retainings that advance, thereby can set the gear ratio of higher advance 5 retainings and 6 retainings that advance, when particularly carrying on vehicle, for the vehicle of running at high speed, can reduce the rotating speed of motor, thereby the quiet characteristic of the vehicle of running at high speed is provided.
In addition, as the driving wheel transfer mechanism, have to the differential mechanism portion 5 of driving wheel output rotation and the middle axial region 4 that combines with this differential mechanism portion 5, output block is the counter shaft gear that meshes with middle axial region 4, thereby can be with automatic transmission 1 2Lift-launch is on FF vehicle for example.
(the 3rd mode of execution)
The 1st mode of execution is made the 3rd mode of execution of part change below in conjunction with Figure 11 to Figure 14 explanation.Figure 11 is the sectional view of the automatic transmission of the automatic transmission of expression the 3rd mode of execution.Figure 12 is the schematic diagram of the automatic transmission of expression the 3rd mode of execution.Figure 13 is the action schedule of the automatic transmission of the 3rd mode of execution.Figure 14 is the speed line chart of the automatic transmission of the 3rd mode of execution.In addition, the 3rd mode of execution is except the part change, and the part identical with the 1st mode of execution adopted identical symbol, omits its explanation.
As shown in figure 11, the automatic transmission 1 of the 3rd mode of execution 3Automatic transmission 1 with respect to the 1st and the 2nd mode of execution 1, 1 2(with reference to Fig. 1 and Fig. 6) changed automatic transmission 2.Automatic transmission 1 3 Automatic transmission 1 with the 1st and the 2nd mode of execution 1, 1 2Similarly, be formed with spline 20s, and at central shaft 30 in interior axle side with an end of fluid torque converter 12 (with reference to Fig. 1 and Fig. 6) opposition side of above-mentioned input shaft 20 3The spline 30s combination that forms of an end outer circumferential side, i.e. input shaft 20 and central shaft 30 3Connect along sense of rotation.This central shaft 30 3Has planetary gear unit PU and epicyclic reduction gear (as the rotation output mechanism that slows down) PR.
This planetary gear unit PU comprises the 1st simple planetary arrangement SP2 and the 2nd simple planetary arrangement SP3, as 4 rotation key elements, has sun gear (the 3rd rotation key element that connects by sleeve 127 described later, the 2nd sun gear) S2 and sun gear (the 3rd rotation key element, the 3rd sun gear) S3, (the 2nd rotates key element to the planetary carrier that is connected by side plate 143, the 3rd planetary carrier) CR3 and ring gear (the 2nd rotation key element, the 2nd ring gear) R2, ring gear (the 1st rotation key element, the 3rd ring gear) R3, planetary carrier (the 4th rotation key element, the 2nd planetary carrier) CR2 is so-called simpson planetary gear.In addition, among the above-mentioned epicyclic reduction gear PR, planetary carrier (input rotation key element, the 1st planetary carrier) on the CR1, with ring gear (output rotation key element, the 1st ring gear) the small gear P1a of R1 engagement and be meshing with each other with the small gear P1b of sun gear (fixed factors, the 1st sun gear) S1 engagement is so-called double pinion planetary pinion.
On the above-mentioned input shaft 20, its outer circumferential side dispose have Hydrauservo System 161, multidisc clutch (the 2nd clutch) C1 of friction plate 172, the cylinder part 161e that forms clutch drum (the 2nd clutch drum) and drum type parts 122, the wheelboss part (parts that are connected with the 3rd rotation key element) 125 that is connected with housing part 127, its interior all side dispose have Hydrauservo System 162, the cylinder part 162e of friction plate 171, formation clutch drum (the 1st clutch drum) and drum type parts 124, and housing part 126 3Multidisc clutch (the 1st clutch) C2 of the wheelboss part that connects (parts that are connected with the 2nd rotation key element) 123.
This Hydrauservo System 161 comprises having piston element (the 2nd piston) 161b that is used to press friction plate 172, combine and import the cylinder part 161e of the rotation of input shaft 20 with spline with cylinder part 162e described later, between this piston element 161b and this cylinder part 161e by seal ring 161f, hydraulic chamber (the 2nd hydraulic servo hydraulic chamber) 161a that the 161g sealing forms, make this piston element 161b towards the stressed Returnning spring 161c of the direction of this hydraulic chamber 161a, bear the restoring board 161d of the spring force of this Returnning spring 161c.This hydraulic chamber 161a is communicated with the oil circuit 192 that forms hub portion (the 1st hub portion) 3c of sleeve shape on above-mentioned input shaft 20 of an end that extends to housing 3.This oil circuit 192 is communicated with not shown hydraulic control device.Be the hub portion 3c and 1 pair seal ring cylinder part 161e between 80 formation never illustrated hydraulic control device oil circuit to hydraulic chamber 161a of above-mentioned Hydrauservo System 161 by housing 3.
In addition, this Hydrauservo System 162 comprise have piston element (the 1st piston) 162b that is used to press friction plate 171, be fixed on hydraulic chamber (the 1st hydraulic servo hydraulic chamber) 162a that forms by seal ring 162f, 162g sealing between cylinder part 162e, this piston element 162b on the input shaft 20 and this cylinder part 162e, make this piston element 162b towards the stressed Returnning spring 162c of the direction of this hydraulic chamber 162a, bear the restoring board 162d of the spring force of this Returnning spring 162c.This hydraulic chamber 162a is communicated with the oil circuit 20a, the 20b that form on above-mentioned input shaft 20, and this oil circuit 20a is communicated with the oil circuit 191 of above-mentioned hub portion 3c.Then, this oil circuit 191 is communicated with not shown hydraulic control device.Be that above-mentioned Hydrauservo System 162 is configured on the input shaft 20, the hub portion 3c by housing 3 and 1 pair of seal ring between the input shaft 20 81 form the oil circuit of never illustrated hydraulic control device to hydraulic chamber 162a.
Be that above-mentioned input shaft 20 is connected with above-mentioned cylinder part 161e by cylinder part 162e, the outer circumferential side of this cylinder part 161e is connected with above-mentioned drum type parts 122.All sides dispose the friction plate 172 with the clutch C1 of Hydrauservo System 161 and free combination by clutch C1 with the spline combination in the end of these drum type parts 122, and interior all sides of the friction plate 172 of this clutch C1 are connected with wheelboss part 125 with the spline combination.Therefore, interior all sides of this wheelboss part 125 with at central shaft 30 3On an end of the housing part 127 that rotates freely connect integrally formed above-mentioned sun gear S2 and sun gear S3 on these housing part 127 outer circumferential sides.
In addition, the outer circumferential side of above-mentioned cylinder part 162e is connected with drum type parts 124, all sides dispose the friction plate 171 with the clutch C2 of Hydrauservo System 162 and free combination by clutch C2 with the spline combination in the end of these drum type parts 124, and interior all sides of the friction plate 171 of this clutch C2 are connected with interior all sides of wheelboss part 123 with the spline combination.Interior all sides of this wheelboss part 123 with at central shaft 30 3On an end of the housing part 126 that rotates freely connect, form spline 126s on the end outer circumferential side of the other end of this housing part 126, by the side plate 142 of above line gear rack CR3 3Spline 142s and this side plate 142 3Connect.
On the other hand, extend on housing 3 and the other end above-mentioned hub portion 3c opposition side be provided with have stationary sleeve shape parts 131 3Hub portion (the 2nd hub portion) 3d 3On dispose and have Hydrauservo System 166, friction plate 176, have multidisc clutch (as the 3rd clutch of the rotation output mechanism that the slows down) C3 of the clutch drum (the 3rd clutch drum) 132 of the 166e of cylinder portion.This Hydrauservo System 166 comprises the hydraulic chamber 166a that has the piston element 166b that is used to press friction plate 176, formed by seal ring 166f, 166g sealing between this piston element 166b and the above-mentioned cylinder 166e of portion, make this piston element 166b towards the stressed Returnning spring 166c of the direction of this hydraulic chamber 166a, bear the restoring board 166d of the spring force of this Returnning spring 166c.In addition, clutch drum 132 is to the direction opening of epicyclic reduction gear PR, this epicyclic reduction gear PR be configured in Hydrauservo System 166 and planetary gear unit PU axially between.In addition, friction plate 176 is configured in the position with the radial outer diameter side superimposed of epicyclic reduction gear PR.
This hydraulic chamber 166a and hub portion 3d 3Oil circuit 193 be communicated with, this oil circuit 193 is communicated with not shown hydraulic control device.Be the hub portion 3d of above-mentioned Hydrauservo System 166 by seal casinghousing 3 3And have 1 pair of seal ring 182 between the drum type parts 132 of the 166e of cylinder portion, form the oil circuit of never illustrated hydraulic control device to hydraulic chamber 166a.
Interior all sides of the clutch drum 132 of above-mentioned clutch C3 and above-mentioned friction plate 176 combine by spline, and interior all sides of this friction plate 176 combine with ring gear R1 by spline, and promptly clutch drum 132 freely combines with ring gear R1 by clutch C3.In addition, the outer circumferential side setting of this clutch drum 132 has break (the 2nd break) B2 of Hydrauservo System 164, friction plate 147, the outer circumferential side of this friction plate 174 combines by spline with the spline 3s that forms in interior week at gearbox casing 3b, interior all sides of this friction plate 174 combine by spline with the end outer circumferential side of clutch drum 132 simultaneously, and promptly clutch drum 132 is freely braked by break B2.
On above-mentioned ring gear R1, has side plate 133 3, side plate 134 3, and by these side plates 133 3, 134 3The planetary carrier CR1 of small gear P1a, the P1b (with reference to Figure 12) that is supported is by this small gear P1a engagement, this side plate 134 3Fixing (rotation of input input always) is at above-mentioned jack shaft 30 3On.In addition, this planetary carrier CR1 meshes by small gear P1b and sun gear S1, and sun gear S3 as mentioned above with the hub portion 3d of housing 3 3By the spline combination, be in the state that can not rotate (fixing always).In addition, ring gear R1 is by disc-shaped part 135 3Support, with respect to jack shaft 30 3Be in free rotation state.
All sides in the end of above-mentioned clutch drum 132 are connecting at above-mentioned central shaft 30 3Go up by housing part 126 3And the side plate 142 of planetary carrier CR3 3Support and transmit with rotating freely the transferring elements (as the rotation output mechanism that slows down) 140 of the rotation of this clutch drum 132 3The ring gear R3 of the 2nd simple planetary arrangement SP3 of above-mentioned planetary gear unit PU is fixed on this transferring elements 140 3About intermediate portion.
The outer circumferential side of this ring gear R3 is provided with overrunning clutch (the 2nd overrunning clutch) F2, and the inner ring 141 of this overrunning clutch F2 combines by spline with the outer circumferential side of this ring gear R3.In addition, the outer circumferential side of the outer ring 148 of this overrunning clutch F2 be provided with have Hydrauservo System 167, the break of friction plate 177 (the 4th break) B3, interior all sides of this friction plate 177 and this outer ring 148 combine by spline, the outer circumferential side of this friction plate 177 combines by spline with the spline 3s that forms in interior week at gearbox casing 3b simultaneously, and promptly this outer ring 148 is fixing freely by break B3.
In addition, interior all sides of above-mentioned ring gear R3 with have as mentioned above and housing part 126 3 Side plate 142 by the spline combination 3, side plate 143 and by these side plates 142 3, the 143 small gear P3 that supported planetary carrier CR3 by this small gear P3 engagement, this planetary carrier CR3 is by this small gear P3 and the sun gear S3 engagement that forms on above-mentioned housing part 127.The side plate 143 of this planetary carrier CR3 is connected by the ring gear R2 of spline with the 1st simple planetary arrangement SP2 of above-mentioned planetary gear unit PU.
This ring gear R2 itself is as the inner ring of overrunning clutch F3, and the end outer circumferential side of this ring gear R2 is provided with overrunning clutch (the 1st clutch) F3, and the outer ring of this overrunning clutch F3 combines with spline with the spline 3s that forms on the interior week of gearbox casing 3b.In addition, the other end outer circumferential side of this ring gear R2 be provided with have Hydrauservo System 163, the break of friction plate 173 (the 3rd break) B4, interior all sides of this friction plate 173 combine by spline with wheelboss part 147 on being fixed on this ring gear R2, the outer circumferential side of this friction plate 173 combines by spline with the spline 3s that forms in interior week at gearbox casing 3b simultaneously, and promptly ring gear R2 is fixing freely by break B4.
In addition, the planetary carrier CR2 of interior all sides of above-mentioned ring gear R2 and the small gear P2 that has side plate 144, side plate 145 and supported by these side plates 144,145 is by this small gear P2 engagement, and this planetary carrier CR2 is by this small gear P2 and the sun gear S2 engagement that forms on above-mentioned housing part 127.This planetary carrier CR2 is connected with counter shaft gear 50 by this side plate 145.
As for example Fig. 1 or automatic transmission 1 shown in Figure 6 1, 1 2The same, this counter shaft gear 50 be fixed on above-mentioned in the middle of gear 51 engagements on the jack shaft 52 of axial region 4, this jack shaft 52 meshes with the gear 53 of differential mechanism portion 5 by the gear 52a that forms on the outer circumferential face.Then, this gear 53 is fixed on the case shell 54, and this case shell 54 is connected with not shown left and right sides axletree by differential gear 55.
As above shown in the explanation, dispose clutch C1 and clutch C2 on the input shaft 20, central shaft 30 3On dispose counter shaft gear 50, planetary gear unit PU, epicyclic reduction gear PR successively, be the axial side configuration epicyclic reduction gear PR of planet gear unit PU, axially opposite side disposes clutch C1 and clutch C2, disposes counter shaft gear 50 between clutch C1 and clutch C2 and planetary gear unit PU.In addition, clutch C3 and break B2 are configured in the outer circumferential side of epicyclic reduction gear PR, and break B3 and break B4 are configured in the outer circumferential side of planetary gear unit PU.In addition, epicyclic reduction gear PR, planetary gear unit PU and counter shaft gear 50 are set to coaxial configuration with input shaft 20.
Then, according to said structure, automatic transmission 1 is described in conjunction with Figure 12, Figure 13 and Figure 14 3Effect.And in speed line chart shown in Figure 14, the longitudinal axis is represented the rotating speed of each rotation key element, and transverse axis then rotates the gear ratio of key elements corresponding to these.In the part of the planetary gear unit PU of this speed line chart, the longitudinal axis of lateral ends (right side among Figure 14) is corresponding to ring gear R3, and the longitudinal axis is left successively corresponding to ring gear R2 and planetary carrier CR3, planetary carrier CR2, sun gear S2 and sun gear S3 among the figure.
As shown in figure 12, by the combination of clutch C1, the rotation of input shaft 20 is input to above-mentioned sun gear S2 and sun gear S3.Combination by clutch C2, the rotation of input shaft 20 is input to above line gear rack CR3 and ring gear R2, the rotation of this planetary carrier CR2 and ring gear R2 is simultaneously fixed freely by the combination of break B4, and limits the rotation of a direction by overrunning clutch F3.
On the other hand, by jack shaft 30 3The rotation of input shaft 20 is input to above line gear rack CR1.The rotation of above-mentioned sun gear S1 is fixed with respect to housing 3.Above-mentioned ring gear R1 is according to the rotation that is input to the input shaft 20 of this planetary carrier CR1 rotation of slowing down.Utilize the combination of clutch C3, by transferring elements 140 3The deceleration rotation of ring gear R1 is input to above-mentioned ring gear R3.In addition, limit the rotation of the direction of this ring gear R3 by the overrunning clutch F3 that braking acted on of break B3, the combination by break B2 simultaneously makes rotation fixing freely.Then, the rotation of above-mentioned ring gear R2 outputs to above-mentioned counter shaft gear 50, and outputs to not shown wheel by this counter shaft gear 50, above-mentioned middle axial region 4 and differential mechanism portion 5 (with reference to Fig. 1 or Fig. 6).
As shown in figure 13,1 retaining that advances in D (driving) position, clutch C1 and overrunning clutch F3 combination.Like this, as shown in Figure 5, the rotation of input shaft 20 is input to sun gear S2 and sun gear S3 by clutch C1, and the rotation of planetary carrier CR3 and ring gear R2 simultaneously is limited in a direction (being rotated in the forward direction), promptly prevents the counterrotating of ring gear R2 and is in stationary state.Then, utilize the rotation of the input shaft 20 be input to sun gear S2 and the fixing ring gear R2 rotation of will slowing down to output to planetary carrier CR2, from counter shaft gear 50 outputs as advance 1 keep off being rotated in the forward.In addition, among the above-mentioned epicyclic reduction gear PR, rotation outputs to ring gear R3 though the planetary carrier CR1 of the rotation of utilization input input shaft 20 and fixing sun gear S1 will slow down, owing to clutch C3 is released, so not to transferring elements 140 at this moment 3Transmitting torque.And, during engine braking, break B4 combination, ring gear R2 fixes, thereby prevents being rotated in the forward of this ring gear R2, keeps the state of above-mentioned 1 retaining that advances.
In addition, when this advances 1 retaining, prevent the counterrotating of ring gear R2 by overrunning clutch F3, and make to be rotated in the forward and become possibility, can realize switching to 1 retaining that advances when travelling reposefully by the automatic combination of overrunning clutch F3 from for example non-position of travelling.
As shown in figure 13,2 retainings that advance in D (driving) position, clutch C1 and overrunning clutch F2 combination.Like this, as shown in figure 14, the rotation of input shaft 20 is input to sun gear S2 and sun gear S3 by clutch C1, limits ring gear R3 simultaneously towards a direction (being rotated in the forward direction) rotation, promptly is in the stationary state of the counterrotating that prevents ring gear R3.Then, utilization is input to the rotation of input shaft 20 of sun gear S3 and fixing ring gear R3, the rotation of will slowing down outputs to planetary carrier CR3 and ring gear R2, utilization be input to sun gear S2 input shaft 20 rotation and be input to the deceleration rotation of this ring gear R2, to the deceleration rotation of planetary carrier CR2 output, from counter shaft gear 50 outputs being rotated in the forward as 2 retainings that advance greater than above-mentioned 1 retaining that advances.In addition, among the above-mentioned epicyclic reduction gear PR, output to ring gear R3 at this moment though utilize the planetary carrier CR1 of the rotation of having imported input shaft 20 will slow down to rotate with fixing sun gear S1, owing to clutch C3 is released, thereby not to transferring elements 140 3Transmitting torque.And, during engine braking, break B2 combination, ring gear R3 fixes, thereby prevents being rotated in the forward of this ring gear R3, keeps the state of above-mentioned 2 retainings that advance.
In addition, 1 retaining changes to 2 whens retaining of advancing from advancing, break B3 combination, prevent the counter-rotating of ring gear R3 by overrunning clutch F2, planetary carrier CR3 and ring gear R2 are for being rotated in the forward, automatically discharge at the 1 overrunning clutch F3 of retaining by combination that advance, thereby prevent for example driving of motor, speed change is advanced to this and 2 is kept off reposefully.
As shown in figure 13,3 retainings that advance in D (driving) position, clutch C1 and clutch C3 combination.Like this, as shown in figure 14, the rotation of input shaft 20 is input to planetary carrier CR1, and ring gear R1 is by the fixing sun gear S1 rotation of slowing down.In addition, by the combination of clutch C3, by above-mentioned transferring elements 40 3The deceleration rotation of this ring gear R1 is input to ring gear R3.On the other hand, the rotation of input shaft 20 is input to sun gear S3, the rotation of the input shaft 20 by being input to this sun gear S3 and the deceleration of ring gear R3 rotation, to planetary carrier CR3 and the big slightly deceleration rotation of ring gear R2 output, the rotation of the input shaft 20 by being input to sun gear S2 and be input to the big slightly deceleration rotation of this ring gear R2, to the deceleration rotation that above-mentioned 2 retainings that advance are a bit larger tham in planetary carrier CR2 output, export being rotated in the forward as 3 retainings that advance from counter shaft gear 50.In addition, this moment is because ring gear R1 and ring gear R3 are the rotation of slowing down, so above-mentioned transferring elements 140 3Can transmit bigger torque.
As shown in figure 13,4 retainings that advance in D (driving) position, clutch C1 and clutch C2 combination.Like this, as shown in figure 14, the rotation of input shaft 20 is input to sun gear S2 and sun gear S2, is input to planetary carrier CR3 and ring gear R2 by clutch C2 by clutch C1.Like this, since be input to sun gear S2 input shaft 20 rotation and be input to the rotation of the input shaft 20 of ring gear R2, promptly be in direct-connected rotation status, the rotation of input shaft 20 is intactly outputed to planetary carrier CR2, from counter shaft gear 50 outputs being rotated in the forward as 4 retainings that advance.In addition, in above-mentioned epicyclic reduction gear PR, export the deceleration rotation with fixing sun gear S1 to ring gear R3 at this moment though pass through the planetary carrier CR1 of the rotation of input input shaft 20, owing to clutch C3 is released, thereby not to transferring elements 140 3Transmitting torque.
As shown in figure 13,5 retainings that advance in D (driving) position, clutch C2 and clutch C3 combination.Like this, as shown in figure 14, the rotation of input shaft 20 is input to planetary carrier CR1, and ring gear R1 is by the fixing sun gear S1 rotation of slowing down.In addition, because the combination of clutch C3, by above-mentioned transferring elements 140 3The deceleration rotation of this ring gear R1 is outputed to ring gear R3.On the other hand, the rotation of input shaft 20 is input to planetary carrier CR3 and ring gear R2, the rotation of the input shaft 20 by being input to this planetary carrier CR3 and the deceleration of ring gear R3 rotation, to sun gear S3 and the rotation of sun gear S3 output speedup, the rotation of the input shaft 20 by being input to ring gear R2 and be input to the speedup rotation of this sun gear S2, to the rotation of planetary carrier CR2 output speedup, from counter shaft gear 50 outputs being rotated in the forward as 5 retainings that advance.In addition, advance 3 states that keep off in the same manner with above-mentioned this moment, because ring gear R1 and ring gear R3 are the rotation of slowing down, so above-mentioned transferring elements 140 3Can transmit bigger torque.
As shown in figure 13,6 retainings that advance in D (driving) position, clutch C2 combination, break B2 braking.Like this, as shown in figure 14, the rotation of input shaft 20 is input to planetary carrier CR3 and ring gear R2 by clutch C2, simultaneously, and owing to the braking of break B2 makes ring gear R3 fix.Like this, the rotation of the input shaft 20 by being input to planetary carrier CR3 and fixing ring gear R3, form (greater than above-mentioned 5 retainings that advance) speedup rotation, and output to sun gear S3 and sun gear S2, the rotation of the input shaft 20 by being input to ring gear R2 and be input to the speedup rotation of this sun gear S2, to the speedup rotation of planetary carrier CR2 output greater than 5 retainings that advance, and from counter shaft gear 50 outputs being rotated in the forward as 6 retainings that advance.In addition, among the above-mentioned epicyclic reduction gear PR,, export the deceleration rotation at this moment to ring gear R3 though pass through the planetary carrier CR1 and fixing sun gear S1 of the rotation of input input shaft 20, owing to clutch C3 is released, thereby not to transferring elements 140 3Transmitting torque.
As shown in figure 13,1 retaining that falls back in R (reversing gear) position, clutch C3 combination, break B4 braking.Like this, as shown in figure 14, the rotation of input shaft 20 is input to planetary carrier CR1, and ring gear R1 is by the fixing sun gear S1 rotation of slowing down.In addition, by the combination of clutch C3, the deceleration of this ring gear R1 rotation is by above-mentioned transferring elements 140 3Be input to ring gear R3.On the other hand, because the braking of break B4, the rotation of planetary carrier CR3 and ring gear R2 is fixed, deceleration rotation by fixing planetary carrier CR3 and ring gear R3, to sun gear S3 and sun gear S3 output counterrotating, by fixing ring gear R2 and the counterrotating that is input to this sun gear S2, to planetary carrier CR2 output counterrotating, from the counterrotating of counter shaft gear 50 outputs as 1 retaining that falls back.In addition, this moment is the same with the state of above-mentioned advance 3 retainings or above-mentioned 5 retainings that advance, because ring gear R1 and ring gear R3 are the rotation of slowing down, so above-mentioned transferring elements 140 3Can transmit bigger torque.
P (parking) or N (neutral) position, clutch C1, clutch C2 and clutch C3 discharge, and the transmission of power between input shaft 20 and the counter shaft gear 50 is in dissengaged positions, automatic transmission 2 3Integral body is in idling conditions (neutral state).
As mentioned above, according to automatic transmission 1 of the present invention 3, as epicyclic reduction gear PR, clutch C3 and the transferring elements 140 of the rotation output mechanism that slows down 3Be configured in the axial side (left side among Figure 11 and Figure 12) of planetary gear unit PU, clutch C1 and clutch C2 are configured in the axial opposite side (right side among Figure 11 and Figure 12) of planetary gear unit PU, and, counter shaft gear 50 as output block is configured between clutch C1 and clutch C2 and the planetary gear unit PU, particularly can make epicyclic reduction gear PR and planetary gear unit PU near configuration, thereby transmit the transferring elements 140 of the rotation of slowing down 3Axial length can be shorter.Like this, can realize automatic transmission 1 3Miniaturization, light, simultaneously because transferring elements 140 3Light, can reduce inertial force, so can improve automatic transmission 1 3Controlled, reduce speed change and impact.
In addition, because the outer circumferential side of clutch C1 by clutch C2 be connected with sun gear S3 with sun gear S2, thereby the parts can prevent that respectively rotating key element connects the time interlock realization automatic transmission 1 3Miniaturization.
In addition, though clutch C2 disposes clutch C1 at its outer circumferential side, can not be to the outer circumferential side enlarged, but by Hydrauservo System 162 is set on input shaft 20, (for example with respect to situation about on hub portion 3c, being provided with), can guarantee this bigger Hydrauservo System 162, the especially compression area of Hydrauservo System 162 usefulness hydraulic chamber 162a in interior all sides, thereby can increase the capacity of clutch C1.
In addition since with input shaft 20 coaxial epicyclic reduction gear PR, planetary gear unit PU and the counter shaft gears 50 of being provided with, particularly on the FF vehicle, carry automatic transmission 1 3The time, (for example with respect to the situation that epicyclic reduction gear etc. is set on other) can realize the miniaturization of driving wheel transfer mechanism (for example axial region 4 etc.), prevents and the interference of for example vehicle body component, improves automatic transmission 1 3Vehicle boarded performance.
In addition, because clutch C3 connects the output that disconnects the rotation of slowing down, can freely slow down and rotate,, be rotated in epicyclic reduction gear PR, especially the ring gear R1 of the input shaft that is input to planetary carrier CR1 are dallied simultaneously by releasing clutch C3 to ring gear R3 output.Like this, can break be set and sun gear S1 directly is fixed on the housing 3, thereby can realize automatic transmission 1 3Miniaturization and light.In addition, because the break of fixed stars gear S1 is not set, thus the break B2 that ring gear R3 is freely braked can be arranged on the outer circumferential side of epicyclic reduction gear PR.
In addition, because Hydrauservo System 162 is arranged on the input shaft 20, utilize a pair of seal ring 181 to stop leakage and oil circuit 20a, 20b fuel feeding in being arranged on input shaft 20 from housing 3, so needn't between for example input shaft 20 and Hydrauservo System 162, seal ring be set, just can be to the hydraulic chamber 162a of Hydrauservo System 162 fuel feeding.In addition, Hydrauservo System 161,166 can be respectively by extending hub portion 3c, the 3d that is provided with from housing 3 3Fuel feeding, and, promptly can carry out fuel feeding by a pair of seal ring 180,182 is set respectively not by for example other parts.Therefore, as long as a pair of seal ring 181,180,182 is set respectively in Hydrauservo System 162,161,166, just can fuel feeding, thus minimum is reduced in the sliding friction that seal ring causes, its result will improve automatic transmission 1 3Efficient.
In addition, because friction plate 176 is configured in the outer radial periphery side of epicyclic reduction gear PR, thereby can make automatic transmission 1 3In axial miniaturization.In addition, because between the Hydrauservo System 166 by epicyclic reduction gear PR being configured in clutch C3 and planetary gear unit PU axial, can disposed adjacent epicyclic reduction gear PR and planetary gear unit PU (because the Hydrauservo System of clutch C3 166 is not between epicyclic reduction gear PR and planetary gear unit PU), thus transferring elements 140 3Can be shorter.Like this, can realize automatic transmission 1 3Miniaturization and light, simultaneously owing to can reduce inertial force, so can improve automatic transmission 1 3Controlled, reduce speed change and impact.
In addition, because epicyclic reduction gear PR is the double pinion planetary pinion, thereby the rotation that can make input shaft 20 is as the rotation output of slowing down, even set good automatic transmission 1 simultaneously 3The gear ratio, what also need not increase planetary gear unit, epicyclic reduction gear respectively rotates key element, thereby can suppress high speed rotating, realizes automatic transmission 1 3Miniaturization.
In addition, rotate rows of elements gear rack CR1, fixed factors sun gear S1, output rotation key element ring gear R1 because epicyclic reduction gear PR comprises input, thereby the rotation of input shaft 20 can be exported as the rotation of slowing down.
In addition, because planetary gear unit PU is made up of the 1st simple planetary arrangement SP2 with sun gear S2, planetary carrier CR2, ring gear R2 and the 2nd simple planetary arrangement SP3 with sun gear S3, planetary carrier CR3, ring gear R3, so in 6 retainings of can realizing for example advancing, 1 retaining that falls back, can also make epicyclic reduction gear PR and planetary gear unit PU near configuration, thereby can shorten the transferring elements 140 that transmits the rotation of slowing down 3
In addition, owing to have and dispose side by side with break B4 and at the overrunning clutch F3 of the rotation of a direction restrictions planetary gear frame CR3 and ring gear R2, so can utilize 1 retaining that advances when realizing for example just driving of clutch C1 and overrunning clutch F3, thereby can realize switching to 1 retaining that advances when travelling reposefully from for example non-position of travelling.
In addition, because break B4 and overrunning clutch F3 are configured in the outer circumferential side of planetary gear unit PU, with for example the situation of overrunning clutch F3 adjacent with clutch C2 the rotation of a direction of limited wheel boss assembly 123 (particularly for) configuration is compared, can make the partly miniaturization in the axial direction that is provided with of clutch C1, C2, thereby make counter shaft gear 50 near the fluid torque converter sides.Like this, because the gear 51 of jack shaft 52 also can be near the fluid torque converter side, thereby can make jack shaft portion 4 miniaturization in the axial direction.
In addition,, thereby can make jack shaft portion 4 miniaturization in the axial direction, make automatic transmission 1 simultaneously because inner ring and the ring gear R2 of overrunning clutch F3 are integrally formed 3 Automatic transmission 2 3Radially realizing miniaturization.
In addition since have dispose side by side with break B2 and the braking by break B3 at the overrunning clutch F2 of direction restriction ring gear R3 rotation, thereby can realize reposefully switching to 3 retainings that advance from 2 retainings that for example advance.
In addition, shown in the speed line chart, in realize advancing 6 retainings, 1 retaining that falls back, can make epicyclic reduction gear PR and planetary gear unit PU, transmit the transferring elements 140 that slows down and rotate thereby can shorten near configuration 3Like this, can realize automatic transmission 1 3Miniaturization and light, simultaneously owing to can reduce inertial force, so can improve automatic transmission 1 3Controlled, reduce speed change and impact.
In addition, structure as realize advancing 6 retainings, 1 retaining that falls back, because clutch C1, C2 combination simultaneously in 4 retainings that advance, promptly be in direct-connected state at 4 retainings that advance, thereby can set the gear ratio of higher advance 5 retainings and 6 retainings that advance, when particularly carrying on vehicle, for the vehicle of running at high speed, can reduce the rotating speed of motor, thereby the quiet characteristic of the vehicle of running at high speed is provided.
In addition, as the driving wheel transfer mechanism, have to the differential mechanism portion 5 of driving wheel output rotation and the middle axial region 4 that combines with this differential mechanism portion 5, output block is the counter shaft gear that meshes with middle axial region 4, thereby can be with automatic transmission 1 3Lift-launch is on FF vehicle for example.
(the 4th mode of execution)
The 3rd mode of execution is made the 4th mode of execution of part change below in conjunction with Figure 15 to Figure 18 explanation.Figure 15 is the sectional view of the automatic transmission of the automatic transmission of expression the 4th mode of execution.Figure 16 is the schematic diagram of the automatic transmission of expression the 4th mode of execution.Figure 17 is the action schedule of the automatic transmission of the 4th mode of execution.Figure 18 is the speed line chart of the automatic transmission of the 4th mode of execution.In addition, the 4th mode of execution is except the part change, and the part identical with the 3rd mode of execution adopted identical symbol, and it illustrates omission.
As Figure 15 and shown in Figure 16, the automatic transmission 1 of the 4th mode of execution 4The automatic transmission 1 of relative the 3rd mode of execution 3(with reference to Figure 11 and Figure 12), the rotation of input shaft 20 is not the planetary carrier CR1 that is input to planetary pinion (as the rotation output mechanism that slows down, epicyclic reduction gear) PR, but is input to sun gear (as the 1st sun gear of input rotation key element) S1.
As shown in figure 15, automatic transmission 2 4In, sun gear S1 and jack shaft 30 are integrally formed at the end outer circumferential side (left side among Figure 15) with the side opposite with input shaft 20 of jack shaft 304, and input always has the input rotation.In addition, have stationary sleeve shape parts 131 4 Hub portion 3d 4On, the side plate 133 of planetary carrier (fixed factors, the 1st planetary carrier) CR1 4With this sleeve-like part 131 4By the spline combination, fixing simultaneously (fixing always) is at this hub portion 3d 4On.Planetary carrier CR1 is by another side plate 134 4Support small gear P1a, P1b (with reference to Figure 16), this small gear P1b and above-mentioned sun gear S1 engagement, this small gear P1a and ring gear (output rotation key element, the 1st ring gear) R1 engagement simultaneously.This ring gear R1 is by disc-shaped part 135 4Rotation is supported on above-mentioned sleeve-like part 131 freely 4On.
On the other hand, rotation is supported on above-mentioned central shaft 30 freely 4Go up and transmit the transferring elements (as the rotation output mechanism that slows down) 140 of the rotation of clutch drum 132 4Be connected with all sides in the end of clutch drum (the 3rd clutch) 132.And the ring gear R3 of the 2nd simple planetary arrangement SP3 of above-mentioned planetary gear unit PU is fixed on this transferring elements 140 4About intermediate portion.In addition, the side plate 142 of the planetary carrier CR3 of the 2nd simple planetary arrangement SP3 4The housing part 126 that combines with wheelboss part 123 by spline and clutch C2 4Integrally formed.In addition, clutch drum 132 is to the direction opening of epicyclic reduction gear PR, this epicyclic reduction gear PR be configured in Hydrauservo System 166 and planetary gear unit PU axially between.In addition, friction plate 176 is configured in the position with the radial outer diameter side superimposed of epicyclic reduction gear PR.
Then, according to said structure, automatic transmission 1 is described in conjunction with Figure 16, Figure 17 and Figure 18 2The effect of epicyclic reduction gear PR.Identical with above-mentioned the 3rd mode of execution, in speed line chart shown in Figure 180, the longitudinal axis is represented the rotating speed of each rotation key element, and transverse axis then rotates the gear ratio of key elements corresponding to these.In addition, in the part of the planetary gear unit PU of this speed line chart, the longitudinal axis of lateral ends (right side among Figure 18) is corresponding to ring gear R3, and the longitudinal axis is left successively corresponding to ring gear R2, planetary carrier CR3, planetary carrier CR2, sun gear S2 and sun gear S3 among the figure.
As shown in figure 16, the rotation of input shaft 20 is by jack shaft 30 4Be input to above-mentioned sun gear S1, the rotation of above line gear rack CR1 is fixing with respect to housing 3, and above-mentioned ring gear R1 is according to the rotation that is input to the input shaft 20 of this sun gear S1 rotation of slowing down.By the combination of clutch C3, the deceleration of ring gear R1 rotation is by transferring elements 140 4Be input to above-mentioned ring gear R3.
Like this, as Figure 17 and shown in Figure 180, advance 1 the retaining, advance 2 the retaining, advance 4 the retaining, advance 6 the retaining, in epicyclic reduction gear PR, rotation outputs to ring gear R3 by the sun gear S1 and the fixing planetary carrier CR1 of the rotation of input input shaft 20 though slow down, but because clutch C3 release, so not to transferring elements 140 4Transmitting torque.On the other hand, advance 3 the retaining, advance 5 the retaining, fall back 1 the retaining, in epicyclic reduction gear PR, because clutch C3 combination, the sun gear S1 of the rotation by input input shaft 20 and fixing planetary carrier CR1, the ring gear R3 rotation of slowing down, the deceleration rotation of this ring gear R1 is by this clutch C3 and transferring elements 140 4Output to ring gear R3.This moment is because ring gear R1 and ring gear R3 are the rotation of slowing down, so above-mentioned transferring elements 140 4Can transmit bigger torque.
In addition, the effect outside the above-mentioned epicyclic reduction gear PR is identical with above-mentioned the 3rd mode of execution, the Therefore, omited explanation.
As mentioned above, according to automatic transmission 1 of the present invention 4, as epicyclic reduction gear PR, clutch C3 and the transferring elements 140 of the rotation output mechanism that slows down 4Be configured in the axial side (left side among Figure 15 and Figure 16) of planetary gear unit PU, clutch C1 and clutch C2 are configured in the axial opposite side (right side among Figure 15 and Figure 16) of planetary gear unit PU, and, counter shaft gear 50 as output block is configured between clutch C1 and clutch C2 and the planetary gear unit PU, particularly can make epicyclic reduction gear PR and planetary gear unit PU near configuration, thereby transmit the transferring elements 140 of the rotation of slowing down 4Axial length can be shorter.Like this, can realize automatic transmission 1 4Miniaturization, light, simultaneously because transferring elements 140 4Light, can reduce inertial force, so can improve automatic transmission 1 4Controlled, reduce speed change and impact.
In addition, because the outer circumferential side of clutch C1 by clutch C2 be connected with sun gear S3 with sun gear S2, thereby the parts can prevent that respectively rotating key element connects the time interlock realization automatic transmission 1 4Miniaturization.
In addition, though clutch C2 disposes clutch C1 at its outer circumferential side, can not be to the outer circumferential side enlarged, but by Hydrauservo System 162 is set on input shaft 20, (for example with respect to situation about on hub portion 3c, being provided with), can guarantee this bigger Hydrauservo System 162, the especially compression area of Hydrauservo System 162 usefulness hydraulic chamber 162a in interior all sides, thereby can increase the capacity of clutch C1.
In addition since with input shaft 20 coaxial epicyclic reduction gear PR, planetary gear unit PU and the counter shaft gears 50 of being provided with, particularly on the FF vehicle, carry automatic transmission 1 4The time, (for example with respect to the situation that epicyclic reduction gear etc. is set on other) can realize the miniaturization of driving wheel transfer mechanism (for example axial region 4 etc.), prevents and the interference of for example vehicle body component, improves automatic transmission 1 4Vehicle boarded performance.
In addition, because clutch C3 connects the output that disconnects the rotation of slowing down, event can freely be slowed down to ring gear R3 output and be rotated, and simultaneously by releasing clutch C3, be rotated in epicyclic reduction gear PR, especially the ring gear R1 of the input shaft that is input to sun gear S1 is dallied.Like this, can break be set and planetary carrier CR1 directly is fixed on housing 3 grades, thereby can realize automatic transmission 1 4Miniaturization and light.In addition, because the fixedly break of planetary carrier CR1 is not set, thus the break B2 that ring gear R3 is freely braked can be arranged on the outer circumferential side of epicyclic reduction gear PR.
In addition, because Hydrauservo System 162 is arranged on the input shaft 20, so by utilize a pair of seal ring 181 to stop leakage and oil circuit 20a, 20b fuel feeding in being arranged on input shaft 20 from housing 3, needn't between for example input shaft 20 and Hydrauservo System 162, seal ring be set, just can be to the hydraulic chamber 162a of Hydrauservo System 162 fuel feeding.In addition, Hydrauservo System 161,166 is hub portion 3c, the 3d fuel feeding by being provided with from housing 3 extensions respectively, and by for example other parts, promptly can carry out fuel feeding by a pair of seal ring 180,182 is set respectively.Therefore, as long as a pair of seal ring 181,180,182 is set respectively in Hydrauservo System 162,161,166, just can fuel feeding, thus minimum is reduced in the sliding friction that seal ring causes, its result will improve automatic transmission 1 4Efficient.
In addition, because friction plate 176 is configured in the outer radial periphery side of epicyclic reduction gear PR, thereby can make automatic transmission 1 in the axial direction 4Miniaturization.In addition, because between the Hydrauservo System 166 by epicyclic reduction gear PR being configured in clutch C3 and planetary gear unit PU axial, epicyclic reduction gear PR and planetary gear unit PU can disposed adjacent (because the Hydrauservo System of clutch C3 166 is not between epicyclic reduction gear PR and planetary gear unit PU), thus transferring elements 140 4Can be shorter.Like this, can realize automatic transmission 1 4Miniaturization and light, simultaneously owing to can reduce inertial force, so can improve automatic transmission 1 4Controlled, reduce speed change and impact.
In addition, because epicyclic reduction gear PR is the double pinion planetary pinion, thereby the rotation that can make input shaft 20 is as the rotation output of slowing down, even set good automatic transmission 1 simultaneously 4The gear ratio, what also need not increase planetary gear unit, epicyclic reduction gear respectively rotates key element, thereby can suppress high speed rotating, realizes automatic transmission 1 4Miniaturization.
In addition, rotate key element sun gear S1, fixed factors planetary carrier CR1, output rotation key element ring gear R1 because epicyclic reduction gear PR comprises input, thereby the rotation of input shaft 20 can be exported as the rotation of slowing down.
In addition, since planetary gear unit PU serve as reasons have sun gear S2, the 1st simple planetary arrangement SP2 of planetary carrier CR2, ring gear R2 and the 2nd simple planetary arrangement SP3 with sun gear S3, planetary carrier CR3, ring gear R3 form, so in 6 retainings of can realizing for example advancing, 1 retaining that falls back, can also make epicyclic reduction gear PR and planetary gear unit PU near configuration, thereby can shorten the transferring elements 140 that transmits the rotation of slowing down 4
In addition, owing to have and dispose side by side with break B4 and at the overrunning clutch F3 of the rotation of a direction restrictions planetary gear frame CR3 and ring gear R2,1 retaining that advances when realizing for example just driving of clutch C1 and overrunning clutch F3 can be utilized, thereby 1 retaining that advances when travelling can be realized switching to reposefully from for example non-position of travelling.
In addition, because break B4 and overrunning clutch F3 are configured in the outer circumferential side of planetary gear unit PU, with for example the situation of overrunning clutch F3 adjacent with clutch C2 the rotation of a direction of limited wheel boss assembly 123 (particularly for) configuration is compared, can make the partly miniaturization in the axial direction that is provided with of clutch C1, C2, thereby make counter shaft gear 50 near the fluid torque converter sides.Like this, because the gear 51 of jack shaft 52 also can be near the fluid torque converter side, thereby can make jack shaft portion 4 miniaturization in the axial direction.
In addition,, thereby can make jack shaft portion 4 miniaturization in the axial direction, make automatic transmission 1 simultaneously because inner ring and the ring gear R2 of overrunning clutch F3 are integrally formed 4 Automatic transmission 2 4Radially realizing miniaturization.
In addition since have dispose side by side with break B2 and the braking by break B3 at the overrunning clutch F2 of direction restriction ring gear R3 rotation, thereby can realize reposefully from 2 speed changes of keeping off 3 retainings that advance of for example advancing.
In addition, shown in the speed line chart, in realize advancing 6 retainings, 1 retaining that falls back, can make epicyclic reduction gear PR and planetary gear unit PU, transmit the transferring elements 140 that slows down and rotate thereby can shorten near configuration 4Like this, can realize automatic transmission 1 4Miniaturization and light, simultaneously owing to can reduce inertial force, so can improve automatic transmission 1 4Controlled, reduce speed change and impact.
In addition, structure as realize advancing 6 retainings, 1 retaining that falls back, because clutch C1, C2 combination simultaneously in 4 retainings that advance, promptly be in direct-connected state at 4 retainings that advance, thereby can set the gear ratio of higher advance 5 retainings and 6 retainings that advance, when particularly carrying on vehicle, for the vehicle of running at high speed, can reduce the rotating speed of motor, thereby the quiet characteristic of the vehicle of running at high speed is provided.
In addition, as the driving wheel transfer mechanism, have to the differential mechanism portion 5 of driving wheel output rotation and the middle axial region 4 that combines with this differential mechanism portion 5, output block is the counter shaft gear that meshes with middle axial region 4, thereby can be with automatic transmission 1 4Lift-launch is on FF vehicle for example.
In addition, in the 1st to the 4th mode of execution of the invention described above, although understand to have the automatic transmission 1 of fluid torque converter 12 4An example, but be not limited thereto, so long as the take-off device of transmitting torque (rotation) during starting can be an any kind.In addition, adopting motor as the situation on the vehicle of driving source although understand lift-launch, but be not limited thereto, can certainly carry on motor vehicle driven by mixed power, driving source can be an any kind.In addition, above-mentioned automatic transmission 1 4Be suitable for the FF vehicle, but be not limited thereto, also can be used for the vehicle of other driving mode such as FR vehicle, 4 wd vehicles.
(the 5th mode of execution)
The the 1st and the 2nd mode of execution is made the 5th mode of execution of part change below in conjunction with Figure 19 to Figure 21 explanation.Figure 19 is the pattern sectional view of the automatic transmission of the automatic transmission of expression the 5th mode of execution.Figure 20 is the action schedule of the automatic transmission of the 5th mode of execution.Figure 21 is the speed line chart of the automatic transmission of the 5th mode of execution.In addition, the 5th mode of execution is except the part change, and the part identical with the 1st and the 2nd mode of execution adopted identical symbol, and it illustrates omission.
The automatic transmission 2 of the automatic transmission 1 of the 5th mode of execution at first, is described in conjunction with Figure 19 5As shown in figure 19, on above-mentioned input shaft 20, has planetary gear unit PU and epicyclic reduction gear (as the rotation output mechanism that slows down) PR.This planetary gear unit PU has as the sun gear of 4 rotation key elements (the 2nd rotation key element, the 3rd sun gear) S2, planetary carrier (the 3rd rotation key element, the 2nd planetary carrier) CR2, ring gear (the 4th rotation key element, the 2nd ring gear) R2 and sun gear (the 1st rotation key element, the 2nd sun gear) S3.On this planetary carrier CR2, supported by side plate 242,244 and be meshing with each other with the long small gear PL of sun gear S3 and ring gear R2 engagement with the short and small gear PS of sun gear S2 engagement, be so-called drawing and tie up Nao formula planetary pinion.In addition, planetary carrier (the fixed factors of above-mentioned epicyclic reduction gear PR, the 1st planetary carrier) on the CR1, with ring gear (output rotation key element, the 1st ring gear) the small gear P2 of R1 engagement and with sun gear (input rotation key element, the 1st sun gear) the small gear P1 of S1 engagement is meshing with each other, and is so-called double pinion planetary pinion.
On the above-mentioned input shaft 20, all sides dispose and have Hydrauservo System 262 in it, friction plate 272, form the drum type parts 222 of clutch drum (the 1st clutch drum), multidisc clutch (the 1st clutch) C1 of the wheelboss part that is connected with sun gear S2 (parts that are connected with the 2nd rotation key element) 223, its outer circumferential side disposes has Hydrauservo System 261, friction plate 271, form the tympanic part spare 224 of clutch drum (the 2nd clutch drum), multidisc clutch (the 2nd clutch) C2 of the wheelboss part that is connected with planetary carrier CR2 (parts that are connected with the 3rd rotation key element) 225.
This Hydrauservo System 262 comprise have piston element (the 1st piston) 262b that is used to press friction plate 272, the drum type parts 222 with the 262e of cylinder portion, hydraulic chamber (the 1st hydraulic servo hydraulic chamber) 262a that between this piston element 262b and the 262e of this cylinder portion, forms by seal ring 262f, 262g sealing, make this piston element 262b towards the stressed Returnning spring 262c of the direction of this hydraulic chamber 262a, bear the restoring board 262d of the spring force of this Returnning spring 262c.The oil circuit 20a, the 20b that form on this hydraulic chamber 262a and the above-mentioned input shaft 20 are communicated with, and this oil circuit 20a extends to an end of housing 3, are communicated with the oil circuit 291 of the hub portion 3c of sleeve shape on the input shaft 20.Therefore, this oil circuit 291 is communicated with not shown hydraulic control device.Promptly, form the oil circuit of never illustrated hydraulic control device to hydraulic chamber 262a so pass through hub portion 3c and 1 pair of seal ring between the input shaft 20 281 of seal casinghousing 3 because above-mentioned Hydrauservo System 262 is configured on the input shaft 20.
In addition, this Hydrauservo System 261 comprise have piston element (the 2nd piston) 261b that is used to press friction plate 271, the drum type parts 224 with the 261e of cylinder portion, hydraulic chamber (the 2nd hydraulic servo hydraulic chamber) 261a that between this piston element 261b and the 261e of this cylinder portion, forms by seal ring 261f, 261g sealing, make this piston element 261b towards the stressed Returnning spring 261c of the direction of this hydraulic chamber 261a, bear the restoring board 261d of the spring force of this Returnning spring 261c.This hydraulic chamber 261a is communicated with the oil circuit 292 of above-mentioned hub portion 3c, and this oil circuit 292 is communicated with not shown hydraulic control device.Be the hub portion 3c and 1 pair seal ring cylinder portion 261e between 280 formation never illustrated hydraulic control device oil circuit to hydraulic chamber 261a of above-mentioned Hydrauservo System 261 by seal casinghousing 3.
Be that above-mentioned input shaft 20 is connected with above-mentioned drum type parts 222, all sides dispose by clutch C1 with the spline combination and use Hydrauservo System 262 and the clutch C1 of free combination in the end of these drum type parts 222, and interior all sides of this clutch C1 are connected with wheelboss part 223 with the spline combination.This wheelboss part 223 is connected with above-mentioned sun gear S2.In addition, all sides dispose by clutch C2 with the spline combination and use Hydrauservo System 261 and the clutch C2 of free combination in the end of above-mentioned drum type parts 224, and interior all sides of this clutch C2 are connected with wheelboss part 225 with the spline combination.And interior all sides of this wheelboss part 225 are connected with above line gear rack CR2.
On the other hand, (left among the figure) disposes and has Hydrauservo System 265, friction plate 275, forms the drum type parts 232 of clutch drum (the 3rd clutch drum), the multidisc clutch C3 of the wheelboss part 235 that is connected with ring gear R1 on the other end of input shaft 20.This Hydrauservo System 265 comprise have the piston element 265b that is used to press friction plate 275, the drum type parts 232 with the 265e of cylinder portion, the hydraulic chamber 265a that between this piston element 265b and the 265e of this cylinder portion, forms by seal ring 265f, 265g sealing, make this piston element 265b towards the stressed Returnning spring 265c of the direction of this hydraulic chamber 265a, bear the restoring board 265d of the spring force of this Returnning spring 265c.In addition, the clutch drum of being made up of drum type parts 232 is to the direction opening of epicyclic reduction gear PR, this epicyclic reduction gear PR be configured in Hydrauservo System 265 and planetary gear unit PU axially between.In addition, friction plate 275 is configured in the position with the radial outer diameter side superimposed of epicyclic reduction gear PR.
This hydraulic chamber 265a extends to housing 3 and the other end above-mentioned hub portion 3c opposition side, is communicated with the oil circuit 293 of the hub portion 3d of sleeve shape on the input shaft 20, and this oil circuit 293 is communicated with not shown hydraulic control device.The hub portion 3d that is above-mentioned Hydrauservo System 265 by seal casinghousing 3 and have 1 pair of seal ring 282 between the drum type parts 232 of the 265e of cylinder portion forms the oil circuit of never illustrated hydraulic control device to hydraulic chamber 265a.
In addition, dispose on interior all sides of the outer circumferential side of clutch C3 and housing 3b have Hydrauservo System 264, the multi-plate brake B1 of friction plate 274.This Hydrauservo System 264 comprise have the piston element 264b that is used to press friction plate 274, the 264e of cylinder portion that forms on the housing 3b part, the hydraulic chamber 264a that between this piston element 264b and the 264e of this cylinder portion, forms by seal ring 264f, 264g sealing, make this piston element 264b towards the stressed Returnning spring 264c of the direction of this hydraulic chamber 264a, bear the restoring board 264d of the spring force of this Returnning spring 264c.
Promptly in the figure left side, above-mentioned hub portion 3d upper support has the drum type parts 232 that can rotate freely, and all sides dispose clutch (the 3rd clutch) C3 with Hydrauservo System 265 free combinations by clutch C3 with the spline combination in the end of these drum type parts 232.Interior all sides at this clutch C3 dispose the wheelboss part 235 that forms above-mentioned ring gear R1 with the spline combination, and this wheelboss part 235 is transfused to axle 20 to be supported and can rotate freely.In addition, the outer circumferential side at these drum type parts 232 disposes break (the 2nd break) B1 that freely brakes with Hydrauservo System 264 by break B1 with the spline combination.In addition, planetary carrier CR1 has small gear P1 and small gear P2, this small gear P2 and above-mentioned ring gear R1 engagement, this small gear P1 and the sun gear S1 engagement that is connected on the input shaft 20.This planetary carrier CR1 is fixed on the hub portion 3d of housing 3b by side plate 231.
Then, above-mentioned clutch C3 and break B1 are supported and can rotate freely by above-mentioned hub portion 3d by the drum type parts 232 of spline combination, when clutch C3 in conjunction with the time, be connected with the transferring elements 240 of the rotation of transmitting ring gear R1, in addition, the opposite side of this transferring elements 240 is connected with the sun gear S3 of above-mentioned planetary gear unit PU.
On the other hand, at the outer circumferential side of planetary gear unit PU, dispose have Hydrauservo System 263, multi-plate brake (the 3rd break) B2 of friction plate 273, wheelboss part 247.This Hydrauservo System 263 comprise have the piston element 263b that is used to press friction plate 273, the 263e of cylinder portion that forms on the part of housing 3b, the hydraulic chamber 263a that between this piston element 263b and the 263e of this cylinder portion, forms by seal ring 263f, 263g sealing, make this piston element 263b towards the stressed Returnning spring 263c of the direction of this hydraulic chamber 263a, bear the restoring board 263d of the spring force of this Returnning spring 263c.
In addition, the outer circumferential side of planetary gear unit PU disposes overrunning clutch (the 1st overrunning clutch) F3, and the outer ring of this overrunning clutch F3 combines with the interior Zhou Huajian of gearbox casing 3b.The side plate 242 of the planetary carrier CR2 of above-mentioned planetary gear unit PU is connected with the wheelboss part 247 that is connected with above-mentioned break B2 by spline, and this wheelboss part 247 is connected with the inner ring of overrunning clutch F3.Then, the long small gear PL of this planetary carrier CR2 and above-mentioned ring gear R2 engagement, the end of this ring gear R2 is connected with connected element 245, and this ring gear R2 is connected with counter shaft gear 50 by this connected element 245.
As above shown in the explanation, the axial side of planetary gear unit PU disposes epicyclic reduction gear PR, and axially opposite side disposes clutch C1 and clutch C2, disposes counter shaft gear 50 between clutch C1 and clutch C2 and planetary gear unit PU.In addition, clutch C3 and break B1 are configured in the outer circumferential side of epicyclic reduction gear PR, and break B2 is configured in the outer circumferential side of planetary gear unit PU.In addition, epicyclic reduction gear PR, planetary gear unit PU and counter shaft gear 50 are set to coaxial configuration with input shaft 20.
Then, according to said structure, automatic transmission 2 is described in conjunction with Figure 19, Figure 20 and Figure 21 5Effect.In speed line chart shown in Figure 21, the longitudinal axis is represented the rotating speed of each rotation key element, and transverse axis then rotates the gear ratio of key elements corresponding to these.In the part of the planetary gear unit PU of this speed line chart, the longitudinal axis of lateral ends (right side among Figure 21) is corresponding to sun gear S3, and the longitudinal axis is left successively corresponding to planetary carrier CR2, ring gear R2, sun gear S2 among the figure.
As shown in figure 19, by the combination of clutch C1, the rotation of input shaft 20 is input to above-mentioned sun gear S2.By the combination of clutch C2, the rotation of input shaft 20 is input to above line gear rack CR2, the rotation of this planetary carrier CR2 simultaneously fix freely by the braking of break B2, and limits the rotation of a direction by overrunning clutch F3.In addition, the rotation of sun gear S3 is fixed freely by the braking of break B1.
On the other hand, above-mentioned sun gear S1 is connected with input shaft 20, and imports the rotation of this input shaft 20.In addition, above-mentioned ring gear R1 is connected with housing 3b, and rotation is fixing, so ring gear R1 deceleration rotation.In addition, by the combination of clutch C3, the deceleration of this ring gear R1 rotation is input to sun gear S3.
Then, the rotation of above-mentioned ring gear R2 outputs to above-mentioned counter shaft gear 50, and outputs to not shown wheel by this counter shaft gear 50, above-mentioned middle axial region 4 and differential mechanism portion 5 (with reference to Fig. 1).
As shown in figure 20,1 retaining that advances in D (driving) position, clutch C1 and overrunning clutch F3 combination.Like this, as shown in figure 21, the rotation of input shaft 20 is input to sun gear S2 by clutch C1, and the rotation of planetary carrier CR2 simultaneously is limited in a direction (being rotated in the forward direction), promptly prevents the counterrotating of planetary carrier CR2 and is in stationary state.Then, the rotation that is input to the input shaft 20 of sun gear S2 outputs to ring gear R2 by fixing planetary carrier CR2, from counter shaft gear 50 outputs being rotated in the forward as 1 retaining that advances.In addition, when engine braking, break B2 braking, planetary carrier CR2 fixes, thereby to prevent the form that is rotated in the forward of this planetary carrier CR2, to keep 1 state that keeps off that advances.In addition,, prevent planetary carrier CR2 counterrotating by overrunning clutch F3, and it can be rotated in the forward, thereby can realize switching to 1 retaining that advances when travelling reposefully by the automatic combination of overrunning clutch from for example non-position of travelling at 1 retaining that advances.
As shown in figure 20,2 retainings that advance in D (driving) position, clutch C1 combination, break B1 braking.Like this, as shown in figure 21, the rotation of input shaft 20 is input to sun gear S2 by clutch C1, and the braking owing to break B1 simultaneously makes sun gear S3 fix.Like this, the rotation of planetary carrier CR2 is slowed down a little, and the planetary carrier CR2 of rotation by this deceleration rotation that is input to the input shaft 20 of sun gear S2 outputs to ring gear R2, from counter shaft gear 50 outputs being rotated in the forward as 2 retainings that advance.
As shown in figure 20,3 retainings that advance in D (driving) position, clutch C1 and clutch C3 combination.Like this, as shown in figure 21, the rotation of input shaft 20 is input to sun gear S2 by clutch C1.In addition, owing to be input to the rotation of input shaft 20 of sun gear S1 and fixing planetary carrier CR1, the ring gear R1 rotation of slowing down, the deceleration of this ring gear R1 is rotated and is outputed to sun gear S3 by clutch C3 and transferring elements 240.Like this, owing to the rotation of the input shaft 20 that is input to sun gear S2 and the deceleration rotation of sun gear S3, planetary carrier CR2 is only big slightly than the deceleration rotation of this sun gear S3 deceleration rotation.Then, the planetary carrier CR2 of rotation by this deceleration rotation that is input to the input shaft 20 of sun gear S2 outputs to ring gear R2, from counter shaft gear 50 outputs being rotated in the forward as 3 retainings that advance.In addition, this moment is because sun gear S3 and ring gear R1 are the rotation of slowing down, so above-mentioned transferring elements 240 can transmit bigger torque.
As shown in figure 20,4 retainings that advance in D (driving) position, clutch C1 and clutch C2 combination.Like this, as shown in figure 21, the rotation of input shaft 20 is input to sun gear S2, is input to planetary carrier CR1 by clutch C2 by clutch C1.Like this, since be input to sun gear S2 input shaft 20 rotation and be input to the rotation of the input shaft 20 of planetary carrier CR2, promptly be in direct-connected rotation status, the rotation of input shaft 20 intactly outputs to ring gear R2, from counter shaft gear 50 outputs being rotated in the forward as 4 retainings that advance.
As shown in figure 20,5 retainings that advance in D (driving) position, clutch C2 and clutch C3 combination.Like this, as shown in figure 21, the rotation of input shaft 20 is input to planetary carrier CR2 by clutch C2.In addition, owing to be input to the rotation of input shaft 20 of sun gear S1 and fixing planetary carrier CR1, the ring gear R1 rotation of slowing down is rotated the deceleration of this ring gear R1 by clutch C3, above-mentioned transferring elements 240 and to be outputed to sun gear S3.Like this because the deceleration of sun gear S3 rotation and and imported the planetary carrier CR2 of the rotation of input shaft 20, form the speedup rotation and also output to ring gear R2, from counter shaft gear 50 outputs being rotated in the forward as 5 retainings that advance.In addition, this moment is the same with the state of above-mentioned 3 retainings that advance, because sun gear S3 and ring gear R1 are the rotation of slowing down, so above-mentioned transferring elements 240 can transmit bigger torque.
As shown in figure 20,6 retainings that advance in D (driving) position, clutch C2 combination, break B1 braking.Like this, as shown in figure 21, the rotation of input shaft 20 is input to planetary carrier CR2 by clutch C2.Simultaneously, the braking owing to break B1 makes sun gear S3 fix.Like this, owing to be input to the rotation of input shaft 20 of planetary carrier CR2 and fixing sun gear S3, form (greater than above-mentioned 5 retainings that advance) speedup rotation, and output to ring gear R2, from counter shaft gear 50 outputs being rotated in the forward as 5 retainings that advance.
As shown in figure 20,1 retaining that falls back in R (reversing gear) position, clutch C3 combination, break B2 braking.Like this, as shown in figure 21, owing to be input to the rotation of input shaft 20 of sun gear S1 and fixing planetary carrier CR1, the ring gear R1 rotation of slowing down, should slow down to rotate by clutch C3 and above-mentioned transferring elements 240 outputs to sun gear S3.In addition, because the braking of break B2, planetary carrier CR2 is fixed.Like this, because the deceleration of sun gear S3 rotation and fixing planetary carrier CR2, to ring gear R2 output counterrotating, from the counterrotating of counter shaft gear 50 outputs as 1 retaining that falls back.In addition, this moment is the same with the state of above-mentioned advance 3 retainings or above-mentioned 5 retainings that advance, because sun gear S3 and ring gear R1 are the rotation of slowing down, above-mentioned transferring elements 240 can transmit bigger torque.
P (parking) or N (neutral) position, clutch C1, clutch C2 and clutch C3 discharge, and the transmission of power between input shaft 20 and the counter shaft gear 50 is in dissengaged positions, automatic transmission 2 5Integral body is in idling conditions (neutral state).
As mentioned above, according to automatic transmission 2 of the present invention 5Epicyclic reduction gear PR as the rotation output mechanism that slows down, clutch C3, and transferring elements 240 is configured in the axial side (left side among Figure 19) of planetary gear unit PU, clutch C1 and clutch C2 are configured in the axial opposite side (right side among Figure 19) of planetary gear unit PU, and, counter shaft gear 50 as output block is configured between clutch C1 and clutch C2 and the planetary gear unit PU, particularly can make epicyclic reduction gear PR and planetary gear unit PU near configuration, thereby the axial length of transmitting the transferring elements 240 of the rotation of slowing down can be shorter.Like this, can realize automatic transmission 1 5Miniaturization, light, simultaneously because the light of transferring elements 240 can reduce inertial force, so can improve automatic transmission 1 5Controlled, reduce speed change and impact.
In addition, because the outer circumferential side of clutch C2 by clutch C1 be connected with planetary carrier CR2, thereby the parts can prevent that respectively rotating key element connects the time interlock realization automatic transmission 1 5Miniaturization.
In addition, though the outer circumferential side of clutch C1 disposes clutch C2, can not be to the outer circumferential side enlarged, but by Hydrauservo System 262 is set on input shaft 20, (for example comparing situation about on hub portion 3c, being provided with), can guarantee this bigger Hydrauservo System 262, the especially compression area of Hydrauservo System 262 usefulness hydraulic chamber 262a in interior all sides, thereby can increase the capacity of clutch C1.
In addition since with input shaft 20 coaxial epicyclic reduction gear PR, planetary gear unit PU and the counter shaft gears 50 of being provided with, particularly on the FF vehicle, carry automatic transmission 1 5The time, (for example with respect to the situation that epicyclic reduction gear etc. is set on other) can realize the miniaturization of driving wheel transfer mechanism (for example axial region 4 etc.), improves automatic transmission 1 6Vehicle boarded performance.
In addition, because connecting, clutch C3 disconnects the rotation of slowing down, thereby the rotation of slowing down freely can be input to sun gear S3,, be rotated in epicyclic reduction gear PR, particularly the ring gear R1 place of the input shaft that is input on the sun gear S1 be dallied simultaneously by the release of clutch C3.Like this, can break be set and planetary carrier CR1 directly is fixed on the housing 3, thereby can realize automatic transmission 1 5Miniaturization and light.In addition, because the fixedly break of planetary carrier CR1 is not set, thus the break B1 that sun gear S3 is freely braked can be arranged on the outer circumferential side of epicyclic reduction gear PR.
In addition, because Hydrauservo System 262 is arranged on the input shaft 20, utilize a pair of seal ring 281 to stop leakage and oil circuit 20a, 20b fuel feeding in being arranged on input shaft 20 from housing 3, so needn't between for example input shaft 20 and Hydrauservo System 262, seal ring be set, just can be to the hydraulic chamber 262a of Hydrauservo System 262 fuel feeding.In addition, Hydrauservo System 261,265 is hub portion 3c, the 3d fuel feeding by being provided with from housing 3 extensions respectively, and by for example other parts, promptly can carry out fuel feeding by a pair of seal ring 280,282 is set respectively.Therefore, as long as a pair of seal ring 281,280,282 is set respectively in Hydrauservo System 262,261,266, just can fuel feeding, thus minimum is reduced in the sliding friction that seal ring causes, its result will improve automatic transmission 1 5Efficient.
In addition, because friction plate 275 is configured in the outer radial periphery side of epicyclic reduction gear PR, thereby can make automatic transmission 1 in the axial direction 5Miniaturization.In addition, because between the Hydrauservo System 265 by epicyclic reduction gear PR being configured in clutch C3 and planetary gear unit PU axial, epicyclic reduction gear PR and planetary gear unit PU can disposed adjacent (because the Hydrauservo System of clutch C3 265 is not between epicyclic reduction gear PR and planetary gear unit PU), thereby transferring elements 240 can be shorter.Like this, can realize automatic transmission 1 5Miniaturization and light, simultaneously owing to can reduce inertial force, so can improve automatic transmission 1 5Controlled, reduce speed change and impact.
In addition, because epicyclic reduction gear PR is the double pinion planetary pinion, thereby the rotation that can make input shaft 20 is as the rotation output of slowing down, even set good automatic transmission 1 simultaneously 5The gear ratio, what also need not increase planetary gear unit, epicyclic reduction gear respectively rotates key element, thereby can suppress high speed rotating, realizes automatic transmission 1 5Miniaturization.
In addition, rotate key element sun gear S1, fixed factors planetary carrier CR1, output rotation key element ring gear R1 because epicyclic reduction gear PR comprises input, thereby the rotation of input shaft 20 can be exported as the rotation of slowing down.
In addition, because planetary gear unit PU has drawing of sun gear S2, sun gear S3, planetary carrier CR2, ring gear R2 to tie up Nao formula planetary pinion, so in 6 retainings of can realizing for example advancing, 1 retaining that falls back, can also make epicyclic reduction gear PR and planetary gear unit PU near configuration, thereby can shorten the transferring elements 240 that transmits the rotation of slowing down.
In addition, owing to have and dispose side by side with break B2 and at the overrunning clutch F3 of the rotation of a direction restrictions planetary gear frame CR2, so can utilize 1 retaining that advances when realizing for example just driving of clutch C1 and overrunning clutch F3, thereby can realize switching to 1 retaining that advances when travelling reposefully from for example non-position of travelling.
In addition, because break B2 and overrunning clutch F3 are configured in the outer circumferential side of planetary gear unit PU, with for example the situation of overrunning clutch F3 adjacent with clutch C2 the rotation of a direction of limited wheel boss assembly 223 (particularly for) configuration is compared, can make the partly miniaturization in the axial direction that is provided with of clutch C1, C2, thereby make counter shaft gear 50 near the fluid torque converter sides.Like this, because the gear 51 of jack shaft 52 also can be near the fluid torque converter side, thereby can make jack shaft portion 4 miniaturization in the axial direction.
In addition, shown in the speed line chart, in realize advancing 6 retainings, 1 retaining that falls back, can make epicyclic reduction gear PR and planetary gear unit PU, transmit the transferring elements 240 that slows down and rotate thereby can shorten near configuration.Like this, can realize automatic transmission 1 5Miniaturization and light, simultaneously owing to can reduce inertial force, so can improve automatic transmission 1 5Controlled, reduce speed change and impact.
In addition, structure as realize advancing 6 retainings, 1 retaining that falls back, because clutch C1, C2 combination simultaneously in 4 retainings that advance, promptly be in direct-connected state at 4 retainings that advance, thereby can set the gear ratio of higher advance 5 retainings and 6 retainings that advance, when particularly carrying on vehicle, for the vehicle of running at high speed, can reduce the rotating speed of motor, thereby the quiet characteristic of the vehicle of running at high speed is provided.
In addition, as the driving wheel transfer mechanism, have to the differential mechanism portion 5 of driving wheel output rotation and the middle axial region 4 that combines with this differential mechanism portion 5, output block is the counter shaft gear that meshes with middle axial region 4, thereby can be with automatic transmission 1 5Lift-launch is on FF vehicle for example.
(the 6th mode of execution)
The 5th mode of execution is made the 6th mode of execution of part change below in conjunction with Figure 22 explanation.Figure 22 is the pattern sectional view of the automatic transmission of the automatic transmission of expression the 6th mode of execution.In addition, the 6th mode of execution is except the part change, and the part identical with the 5th mode of execution adopted identical symbol, and it illustrates omission.
As shown in figure 22, the automatic transmission 2 of the automatic transmission 1 of the 6th mode of execution 6The automatic transmission 2 of the automatic transmission 1 relevant with respect to the 5th mode of execution 5(with reference to Figure 19), input side and outlet side are just opposite.In addition, for advance 1 block to advance 6 the retaining, and fall back 1 the retaining, its effect identical (with reference to Figure 20 and Figure 21).
Thus, the same with the 5th mode of execution, utilize automatic transmission 2 of the present invention 6As epicyclic reduction gear PR, the clutch C3 of rotation output mechanism and the axial side (right side among Figure 22) that transferring elements 240 is configured in planetary gear unit PU of slowing down, clutch C1 and clutch C2 are configured in the axial opposite side (left side among Figure 22) of planetary gear unit PU, counter shaft gear 50 as output block is configured between clutch C1 and clutch C2 and the planetary gear unit PU, particularly can make epicyclic reduction gear PR and planetary gear unit PU near configuration, thereby the axial length of transmitting the transferring elements 240 of the rotation of slowing down can be shorter.Like this, can realize automatic transmission 1 6Miniaturization, light, simultaneously because the light of transferring elements 240 can reduce inertial force, so can improve automatic transmission 1 6Controlled, reduce speed change and impact.
In addition, because the outer circumferential side of clutch C2 by clutch C1 be connected with planetary carrier CR2, thereby the parts can prevent that respectively rotating key element connects the time interlock realization automatic transmission 1 6Miniaturization.
In addition, though the outer circumferential side of clutch C1 disposes clutch C2, can not be to the outer circumferential side enlarged, but by Hydrauservo System 262 is set on input shaft 20, (for example with respect to situation about on hub portion 3c, being provided with), can guarantee this bigger Hydrauservo System 262, the especially compression area of Hydrauservo System 262 usefulness hydraulic chamber 262a in interior all sides, thereby can increase the capacity of clutch C1.
In addition since with input shaft 20 coaxial epicyclic reduction gear PR, planetary gear unit PU and the counter shaft gears 50 of being provided with, particularly on the FF vehicle, carry automatic transmission 1 6The time, (for example with respect to the situation that epicyclic reduction gear etc. is set on other) can realize the miniaturization of driving wheel transfer mechanism (for example axial region 4 etc.), improves automatic transmission 1 6Vehicle boarded performance.
In addition, because clutch C3 connects the output that disconnects the rotation of slowing down, can freely slow down and rotate,, be rotated in epicyclic reduction gear PR, especially the ring gear R1 of the input shaft that is input to sun gear S1 are dallied simultaneously by releasing clutch C3 to sun gear S3 output.Like this, can break be set and planetary carrier CR1 directly is fixed on the housing 3, thereby can realize automatic transmission 1 6Miniaturization and light.In addition, because the fixedly break of planetary carrier CR1 is not set, thus the break B1 that sun gear S3 is freely braked can be arranged on the outer circumferential side of epicyclic reduction gear PR.
In addition, because Hydrauservo System 262 is arranged on the input shaft 20, utilize a pair of seal ring 281 to stop leakage and oil circuit 20a, 20b fuel feeding in being arranged on input shaft 20 from housing 3, so needn't between for example input shaft 20 and Hydrauservo System 262, seal ring be set, just can be to the hydraulic chamber 262a of Hydrauservo System 262 fuel feeding.In addition, Hydrauservo System 261,265 is hub portion 3c, the 3d fuel feeding by being provided with from housing 3 extensions respectively, and by for example other parts, promptly can carry out fuel feeding by a pair of seal ring 280,282 is set respectively.Therefore, as long as a pair of seal ring 281,280,282 is set respectively in Hydrauservo System 262,261,265, just can fuel feeding, thus minimum is reduced in the sliding friction that seal ring causes, its result will improve automatic transmission 1 6Efficient.
In addition, because friction plate 275 is configured in the outer radial periphery side of epicyclic reduction gear PR, thereby can make automatic transmission 1 in the axial direction 6Miniaturization.In addition, because between the Hydrauservo System 265 by epicyclic reduction gear PR being configured in clutch C3 and planetary gear unit PU axial, epicyclic reduction gear PR and planetary gear unit PU can disposed adjacent (because the Hydrauservo System of clutch C3 265 is not between epicyclic reduction gear PR and planetary gear unit PU), thereby transferring elements 240 can be shorter.Like this, can realize automatic transmission 1 6Miniaturization and light, simultaneously owing to can reduce inertial force, so can improve automatic transmission 1 2Controlled, reduce speed change and impact.
In addition, because epicyclic reduction gear PR is the double pinion planetary pinion, thereby the rotation that can make input shaft 20 is as the rotation output of slowing down, even set good automatic transmission 1 simultaneously 6The gear ratio, what also need not increase planetary gear unit, epicyclic reduction gear respectively rotates key element, thereby can suppress high speed rotating, realizes automatic transmission 1 6Miniaturization.
In addition, rotate key element sun gear S1, fixed factors planetary carrier CR1, output rotation key element ring gear R1 because epicyclic reduction gear PR comprises input, thereby the rotation of input shaft 20 can be exported as the rotation of slowing down.
In addition, because planetary gear unit PU ties up Nao formula planetary pinion for drawing of being made up of sun gear S2, sun gear S3, planetary carrier CR2 and ring gear R2, so in 6 retainings of can realizing for example advancing, 1 retaining that falls back, can also make epicyclic reduction gear PR and planetary gear unit PU near configuration, thereby can shorten the transferring elements 240 that transmits the rotation of slowing down.
In addition, owing to have and dispose side by side with break B2 and at the overrunning clutch F3 of the rotation of a direction restrictions planetary gear frame CR2,1 retaining that advances when realizing for example just driving of clutch C1 and overrunning clutch F3 can be utilized, thereby 1 retaining that advances when travelling can be realized switching to reposefully from for example non-position of travelling.
In addition, because break B2 and overrunning clutch F3 are configured in the outer circumferential side of planetary gear unit PU, with for example the situation of overrunning clutch F3 adjacent with clutch C2 the rotation of a direction of limited wheel boss assembly 223 (particularly for) configuration is compared, can make the partly miniaturization in the axial direction that is provided with of clutch C1, C2, thereby make counter shaft gear 50 near the fluid torque converter sides.Like this, because the gear 51 of jack shaft 52 also can be near the fluid torque converter side, thereby can make jack shaft portion 4 miniaturization in the axial direction.
In addition, shown in the speed line chart, in realize advancing 6 retainings, 1 retaining that falls back, can make epicyclic reduction gear PR and planetary gear unit PU, transmit the transferring elements 240 that slows down and rotate thereby can shorten near configuration.Like this, can realize automatic transmission 1 6Miniaturization and light, simultaneously owing to can reduce inertial force, so can improve automatic transmission 1 6Controlled, reduce speed change and impact.
In addition, structure as realize advancing 6 retainings, 1 retaining that falls back, because clutch C1, C2 combination simultaneously in 4 retainings that advance, promptly be in direct-connected state at 4 retainings that advance, thereby can set the gear ratio of higher advance 5 retainings and 6 retainings that advance, when particularly carrying on vehicle, for the vehicle of running at high speed, can reduce the rotating speed of motor, thereby the quiet characteristic of the vehicle of running at high speed is provided.
In addition, as the driving wheel transfer mechanism, have to the differential mechanism portion 5 of driving wheel output rotation and the middle axial region 4 that combines with this differential mechanism portion 5, output block is the counter shaft gear that meshes with middle axial region 4, thereby can be with automatic transmission 1 6Lift-launch is on FF vehicle for example.
(the 7th mode of execution)
The 5th mode of execution is made the 7th mode of execution of part change below in conjunction with Figure 23 to Figure 25 explanation.Figure 23 is the pattern sectional view of the automatic transmission of the automatic transmission of expression the 7th mode of execution.Figure 24 is the action schedule of the automatic transmission of the 7th mode of execution.Figure 25 is the speed line chart of the automatic transmission of the 7th mode of execution.In addition, the 7th mode of execution is except the part change, and the part identical with the 5th mode of execution adopted identical symbol, and it illustrates omission.
As shown in figure 23, the automatic transmission 2 of the automatic transmission 1 of the 7th mode of execution 7Automatic transmission 2 with respect to the 5th mode of execution 5(with reference to Figure 19), the configuration of having changed epicyclic reduction gear PR and clutch C3.
This automatic transmission 2 7In, clutch (the 3rd clutch) C3 be configured in planetary pinion (as the epicyclic reduction gear of the rotation output mechanism that slows down) PR with planetary gear unit PU opposition side (left side among the figure), all sides combine with friction plate 275 by spline in the end of the drum type parts 331 of this clutch C3.In addition, the drum type parts 331 of this clutch C3 are connected with input shaft 20.
On the other hand, sun gear (input rotation key element, the 1st sun gear) S1 is transfused to axle 20 to be supported and can rotate freely, and is connected with hub portion 332 simultaneously, and the end outer shaft side of this hub portion 332 and above-mentioned friction plate 275 are connected by spline.In addition, the side plate of planetary carrier (fixed factors, the 1st planetary carrier) CR1 is connected with fixed component 330, is fixedly supported on the housing 3b.And the outer circumferential side of ring gear (output rotation key element, the 1st ring gear) R1 is connected with the friction plate 274 of break B1 by spline, and this ring gear R1 is connected with transferring elements 340 simultaneously, is connected with sun gear S3 by this transferring elements 340.
In addition, clutch C3 is communicated with oil circuit 20c, the 20d of formation on the hydraulic chamber 265a of Hydrauservo System 265 and the above-mentioned input shaft 20, and this oil circuit 20c is communicated with the oil circuit 293 of hub portion 3d.And this oil circuit 293 is communicated with not shown hydraulic control device.Promptly, form the oil circuit of never illustrated hydraulic control device to hydraulic chamber 265a so pass through hub portion 3d and 1 pair of seal ring between the input shaft 20 283 of seal casinghousing 3 because above-mentioned Hydrauservo System 265 is configured on the input shaft 20.
Then, according to said structure, the effect of automatic transmission 27 is described in conjunction with Figure 23, Figure 24 and Figure 25.In addition, the same with above-mentioned the 5th mode of execution, in speed line chart shown in Figure 25, the longitudinal axis is represented the rotating speed of each rotation key element, and transverse axis then rotates the gear ratio of key elements corresponding to these.In the part of the planetary gear unit PU of this speed line chart, the longitudinal axis of lateral ends (right side among Figure 25) is corresponding to sun gear S3, and the longitudinal axis is left successively corresponding to planetary carrier CR2, ring gear R2, sun gear S2 among the figure.
As shown in figure 23, by the combination of clutch C3, the rotation of input shaft 20 is input to above-mentioned sun gear S1.Because the rotation of above line gear rack CR1 is fixing with respect to housing 3, above-mentioned ring gear R1 does the rotation of slowing down according to the rotation of the input shaft 20 that is input to this sun gear S1.Promptly by the combination of clutch C3, the deceleration rotation of ring gear R1 is input to sun gear S3 by transferring elements 340.
Therefore, as Figure 21 and shown in Figure 22, for epicyclic reduction gear PR, advance 3 the retaining, advance 5 the retaining, fall back 1 the retaining, because the combination of clutch C3, the rotation of input shaft 20 is input to sun gear S1, slows down to ring gear R3 input by fixing planetary carrier CR1 and rotates, and exports the rotation of slowing down by transferring elements 340 to sun gear S3.At this moment, because ring gear R1 and sun gear S3 are for the rotation of slowing down, so above-mentioned transferring elements 340 can transmit bigger torque.On the other hand, since advance 1 the retaining, advance 2 the retaining, advance 4 the retaining, advance 6 the retaining, the rotation of sun gear S3 is input to ring gear R1 by transferring elements 340, clutch C3 discharges, therefore as shown in figure 25, sun gear S1 rotates for the rotation of each gear stage and fixing planetary carrier CR1 according to this ring gear R1.
In addition, the effect outside the above-mentioned epicyclic reduction gear PR is the same with above-mentioned the 5th mode of execution, its explanation of Therefore, omited.
As mentioned above, according to automatic transmission 2 of the present invention 7As epicyclic reduction gear PR, the clutch C3 of rotation output mechanism and the axial side that transferring elements 340 is configured in planetary gear unit PU (left side among Figure 23) of slowing down, clutch C1 and clutch C2 are configured in the axial opposite side (right side among Figure 23) of planetary gear unit PU, counter shaft gear 50 as output block is configured between clutch C1 and clutch C2 and the planetary gear unit PU, particularly can make epicyclic reduction gear PR and planetary gear unit PU near configuration, thereby the axial length of transmitting the transferring elements 340 of the rotation of slowing down can be shorter.Like this, can realize automatic transmission 1 7Miniaturization, light, simultaneously because the light of transferring elements 340 can reduce inertial force, so can improve automatic transmission 1 7Controlled, reduce speed change and impact.
In addition, because the outer circumferential side of clutch C2 by clutch C1 be connected with planetary carrier CR2, thereby the parts can prevent that respectively rotating key element connects the time interlock realization automatic transmission 1 7Miniaturization.
In addition, though the outer circumferential side of clutch C1 disposes clutch C2, can not be to the outer circumferential side enlarged, but by Hydrauservo System 262 is set on input shaft 20, (for example with respect to situation about on hub portion 3c, being provided with), can guarantee this bigger Hydrauservo System 262, the especially compression area of Hydrauservo System 262 usefulness hydraulic chamber 262a in interior all sides, thereby can increase the capacity of clutch C1.
In addition since with input shaft 20 coaxial epicyclic reduction gear PR, planetary gear unit PU and the counter shaft gears 50 of being provided with, particularly on the FF vehicle, carry automatic transmission 1 7The time, (for example with respect to the situation that epicyclic reduction gear etc. is set on other) can realize the miniaturization of driving wheel transfer mechanism (for example axial region 4 etc.), prevents and the interference of for example body part, improves automatic transmission 1 7Vehicle boarded performance.
In addition, for example the spy open on the 2001-263438 communique etc. disclosed like that, if clutch C3 is configured between ring gear R1 and the sun gear S3, just need to connect and disconnect the rotation of slowing down, thereby form bigger structure, and the distance between epicyclic reduction gear PR and the planetary gear unit PU increases, but by being configured between input shaft 20 and the sun gear S1, connect the rotation that disconnects input shaft 20 by this clutch C3, thereby connect the deceleration rotation that disconnects from the ring gear R1 output of epicyclic reduction gear PR, therefore can realize the miniaturization of clutch C3, and epicyclic reduction gear PR and planetary gear unit PU are disposed on closer locations.Can realize automatic transmission 1 like this 7Miniaturization.
In addition, because Hydrauservo System 262,265 is arranged on the input shaft 20, utilizing a pair of seal ring 281,283 to stop from housing 3 leaks, and oil circuit 20a, 20b in being arranged on input shaft 20,20c, 20d fuel feeding, so needn't between for example input shaft 20 and Hydrauservo System 262,265, seal ring be set, just can be to hydraulic chamber 262a, the 265a fuel feeding of Hydrauservo System 262,265.In addition, Hydrauservo System 261 is the hub portion 3c fuel feeding by being provided with from housing 3 extensions respectively, and by for example other parts, promptly can carry out fuel feeding by a pair of seal ring 280 is set respectively.Therefore, as long as a pair of seal ring 281,280,283 is set respectively in Hydrauservo System 262,261,265, just can fuel feeding, thus minimum is reduced in the sliding friction that seal ring causes, its result will improve automatic transmission 1 7Efficient.In addition, though Hydrauservo System 262,265 is arranged on the input shaft 20, but owing to be separately positioned on one distolateral (Figure 23 right side) and another distolateral (Figure 23 left side) of input shaft 20, so do not need to repeat to be provided with Hydrauservo System in the input shaft 20 with oil circuit (for example oil circuit 20a and oil circuit 20c), can make input shaft 20 thinner, realize automatic transmission 1 7Miniaturization.
In addition, because epicyclic reduction gear PR is the double pinion planetary pinion, thereby the rotation that can make input shaft 20 is as the rotation output of slowing down, even set good automatic transmission 1 simultaneously 7The gear ratio, what also need not increase planetary gear unit, epicyclic reduction gear respectively rotates key element, thereby can suppress high speed rotating, realizes automatic transmission 1 7Miniaturization.
In addition, rotate key element sun gear S1, fixed factors planetary carrier CR1, output rotation key element ring gear R1 because epicyclic reduction gear PR comprises input, thereby the rotation of input shaft 20 can be exported as the rotation of slowing down.
In addition, because planetary gear unit PU ties up Nao formula planetary pinion for drawing of being made up of sun gear S2, sun gear S3, planetary carrier CR2 and ring gear R2, so in 6 retainings of can realizing for example advancing, 1 retaining that falls back, can also make epicyclic reduction gear PR and planetary gear unit PU near configuration, thereby can shorten the transferring elements 340 that transmits the rotation of slowing down.
In addition, owing to have and dispose side by side with break B2 and at the overrunning clutch F3 of the rotation of a direction restrictions planetary gear frame CR2,1 retaining that advances when realizing for example just driving of clutch C1 and overrunning clutch F3 can be utilized, thereby 1 retaining that advances when travelling can be realized switching to reposefully from for example non-position of travelling.
In addition, because break B2 and overrunning clutch F3 are configured in the outer circumferential side of planetary gear unit PU, with for example the situation of overrunning clutch F3 adjacent with clutch C2 the rotation of a direction of limited wheel boss assembly 223 (particularly for) configuration is compared, can make the partly miniaturization in the axial direction that is provided with of clutch C1, C2, thereby make counter shaft gear 50 near the fluid torque converter sides.Like this, because the gear 51 of jack shaft 52 also can be near the fluid torque converter side, thereby can make jack shaft portion 4 miniaturization in the axial direction.
In addition, shown in the speed line chart, in realize advancing 6 retainings, 1 retaining that falls back, can make epicyclic reduction gear PR and planetary gear unit PU, transmit the transferring elements 340 that slows down and rotate thereby can shorten near configuration.Like this, can realize automatic transmission 1 7Miniaturization and light, simultaneously owing to can reduce inertial force, so can improve automatic transmission 1 7Controlled, reduce speed change and impact.
In addition, structure as realize advancing 6 retainings, 1 retaining that falls back, because clutch C1, C2 combination simultaneously in 4 retainings that advance, promptly be in direct-connected state at 4 retainings that advance, thereby can set the gear ratio of higher advance 5 retainings and 6 retainings that advance, when particularly carrying on vehicle, for the vehicle of running at high speed, can reduce the rotating speed of motor, thereby the quiet characteristic of the vehicle of running at high speed is provided.
In addition, as the driving wheel transfer mechanism, have to the differential mechanism portion 5 of driving wheel output rotation and the middle axial region 4 that combines with this differential mechanism portion 5, output block is the counter shaft gear that meshes with middle axial region 4, thereby can be with automatic transmission 1 7Lift-launch is on FF vehicle for example.
(the 8th mode of execution)
The 5th mode of execution is made the 8th mode of execution of part change below in conjunction with Figure 26 to Figure 28 explanation.Figure 26 is the pattern sectional view of the automatic transmission of the automatic transmission of expression the 8th mode of execution.Figure 27 is the action schedule of the automatic transmission of the 8th mode of execution.Figure 28 is the speed line chart of the automatic transmission of the 8th mode of execution.In addition, the 8th mode of execution is except the part change, and the part identical with the 5th mode of execution adopted identical symbol, and it illustrates omission.
As shown in figure 26, the automatic transmission 2 of the automatic transmission 1 of the 8th mode of execution 8Automatic transmission 2 with respect to the 5th mode of execution 5(with reference to Figure 19) utilizes break (the 3rd break) B3 to replace clutch C3, makes planetary carrier (fixed factors, the 1st planetary carrier) CR1 of epicyclic reduction gear PR fixing freely by break B3.
This automatic transmission 2 7In, break B3 is configured in the side opposite with planetary gear unit PU (left side among the figure) of epicyclic reduction gear (as the rotation output mechanism that slows down) PR, this break B3 has Hydrauservo System 266, friction plate 276, wheelboss part 432, this Hydrauservo System 266 comprise having the piston element 266b that is used to press friction plate 276, the 266e of cylinder portion that on housing 3b, forms, between this piston element 266b and the 266e of this cylinder portion by seal ring 266f, the hydraulic chamber 266a that the 266g sealing forms, make this piston element 266b towards the stressed Returnning spring 266c of the direction of this hydraulic chamber 266a, bear the restoring board 266d of the spring force of this Returnning spring 266c.
The wheelboss part 432 of this break B3 is connected with the side plate of planetary carrier CR1, and another side plate 434 of this planetary carrier CR1 is transfused to axle 20 to be supported and can rotate freely.In addition, sun gear (input rotation key element, the 1st sun gear) S1 is connected with input shaft 20.And the outer circumferential side of ring gear (output rotation key element, the 1st ring gear) R1 is connected with the friction plate 274 of break B1 by spline, and this ring gear R1 is connected with transferring elements 440 simultaneously, is connected with sun gear S3 by this transferring elements 440.
Then, according to said structure, automatic transmission 2 is described in conjunction with Figure 26, Figure 27 and Figure 28 8Effect.In addition, the same with above-mentioned the 5th mode of execution, in speed line chart shown in Figure 28, the longitudinal axis is represented the rotating speed of each rotation key element, and transverse axis then rotates the gear ratio of key elements corresponding to these.In the part of the planetary gear unit PU of this speed line chart, the longitudinal axis of lateral ends (right side among Figure 28) is corresponding to sun gear S3, and the longitudinal axis is left successively corresponding to planetary carrier CR2, ring gear R2, sun gear S2 among the figure.
As shown in figure 26, by the braking of break B3, above line gear rack CR1 fixes with respect to housing 3b.In addition, the rotation of input shaft 20 is input to sun gear S1.Because above line gear rack CR1's is fixing, this planetary carrier CR1 is according to the rotation that is input to the input shaft 20 of this sun gear S1 rotation of slowing down.Promptly by the combination of break B3, the deceleration rotation of ring gear R1 is input to sun gear S3.
Therefore, as Figure 27 and shown in Figure 28, for epicyclic reduction gear PR, advance 3 the retaining, advance 5 the retaining, fall back 1 the retaining, because break B3 braking, planetary carrier CR1 is fixed, owing to import the rotation of the sun gear S1 of the rotation that input shaft 20 is arranged, the rotation of slowing down is input to ring gear R3, and will slow down to rotate by transferring elements 440 is input to sun gear S3.At this moment, because ring gear R1 and sun gear S3 are the rotation of slowing down, above-mentioned transferring elements 440 can transmit bigger torque.On the other hand, since advance 1 the retaining, advance 2 the retaining, advance 4 the retaining, advance 6 the retaining, the rotation of sun gear S3 is input to ring gear R1 by transferring elements 440, break B3 discharges, as shown in figure 28, planetary carrier CR1 is rotated at the sun gear S1 of the rotation of the rotation of each gear stage and input shaft 20 according to this ring gear R1.
In addition, the effect outside the above-mentioned epicyclic reduction gear PR is the same with above-mentioned the 5th mode of execution, its explanation of Therefore, omited.
As mentioned above, according to automatic transmission 2 of the present invention 8As epicyclic reduction gear PR, the break B3 of rotation output mechanism and the axial side that transferring elements 440 is configured in planetary gear unit PU (left side among Figure 26) of slowing down, clutch C1 and clutch C2 are configured in the axial opposite side (right side among Figure 26) of planetary gear unit PU, counter shaft gear 50 as output block is configured between clutch C1 and clutch C2 and the planetary gear unit PU, particularly can make epicyclic reduction gear PR and planetary gear unit PU near configuration, thereby the axial length of transmitting the transferring elements 340 of the rotation of slowing down can be shorter.Like this, can realize automatic transmission 1 8Miniaturization, light, simultaneously because the light of transferring elements 440 can reduce inertial force, so can improve automatic transmission 1 8Controlled, reduce speed change and impact.
In addition, because the outer circumferential side of clutch C2 by clutch C1 be connected with planetary carrier CR2, thereby the parts can prevent that respectively rotating key element connects the time interlock realization automatic transmission 1 8Miniaturization.
In addition, though the outer circumferential side of clutch C1 disposes clutch C2, can not be to the outer circumferential side enlarged, but by Hydrauservo System 262 is set on input shaft 20, (for example with respect to situation about on hub portion 3c, being provided with), can guarantee this bigger Hydrauservo System 262, the especially compression area of Hydrauservo System 262 usefulness hydraulic chamber 262a in interior all sides, thereby can increase the capacity of clutch C1.
In addition since with input shaft 20 coaxial epicyclic reduction gear PR, planetary gear unit PU and the counter shaft gears 50 of being provided with, particularly on the FF vehicle, carry automatic transmission 1 8The time, (for example with respect to the situation that epicyclic reduction gear etc. is set on other) can realize the miniaturization of driving wheel transfer mechanism (for example axial region 4 etc.), prevents the interference of body part, improves automatic transmission 1 8Vehicle boarded performance.
In addition, disconnect the rotation of slowing down because the combination of break B3 is connected, the clutch that disconnects the rotation of slowing down with connection is compared, and can make break B3 miniaturization, thereby can make epicyclic reduction gear PR and planetary gear unit PU near disposing.Can realize automatic transmission 1 like this 8Miniaturization and light.
In addition, because Hydrauservo System 262 is arranged on the input shaft 20, utilizing a pair of seal ring 281 to stop from housing 3 leaks, and the oil circuit 20a in being arranged on input shaft 20,20b fuel feeding, so needn't between for example input shaft 20 and Hydrauservo System 262, seal ring be set, just can be to the hydraulic chamber 262a of Hydrauservo System 262 fuel feeding.In addition, Hydrauservo System 261 is the hub portion 3c fuel feeding by being provided with from housing 3 extensions respectively, and by for example other parts, promptly can carry out fuel feeding by a pair of seal ring 280 is set respectively.Therefore, as long as a pair of seal ring 281,280 is set respectively in Hydrauservo System 262,261, just can fuel feeding, thus minimum is reduced in the sliding friction that seal ring causes, its result will improve automatic transmission 1 8Efficient.
In addition, because epicyclic reduction gear PR is the double pinion planetary pinion, thereby the rotation that can make input shaft 20 is as the rotation output of slowing down, even set good automatic transmission 1 simultaneously 8The gear ratio, what also need not increase planetary gear unit, epicyclic reduction gear respectively rotates key element, thereby can suppress high speed rotating, realizes automatic transmission 1 8Miniaturization.
In addition, rotate key element sun gear S1, fixed factors planetary carrier CR1, output rotation key element ring gear R1 because epicyclic reduction gear PR comprises input, thereby the rotation of input shaft 20 can be exported as the rotation of slowing down.
In addition, because planetary gear unit PU ties up Nao formula planetary pinion for drawing of being made up of sun gear S2, sun gear S3, planetary carrier CR2 and ring gear R2, so in 6 retainings of can realizing for example advancing, 1 retaining that falls back, can also make epicyclic reduction gear PR and planetary gear unit PU near configuration, thereby can shorten the transferring elements 440 that transmits the rotation of slowing down.
In addition, owing to have and dispose side by side with break B2 and at the overrunning clutch F3 of the rotation of a direction restrictions planetary gear frame CR2,1 retaining that advances when realizing for example just driving of clutch C1 and overrunning clutch F3 can be utilized, thereby 1 retaining that advances when travelling can be realized switching to reposefully from for example non-position of travelling.
In addition, because break B2 and overrunning clutch F3 are configured in the outer circumferential side of planetary gear unit PU, with for example the situation of overrunning clutch F3 adjacent with clutch C2 the rotation of a direction of limited wheel boss assembly 223 (particularly for) configuration is compared, can make the partly miniaturization in the axial direction that is provided with of clutch C1, C2, thereby make counter shaft gear 50 near the fluid torque converter sides.Like this, because the gear 51 of jack shaft 52 also can be near the fluid torque converter side, thereby can make jack shaft portion 4 miniaturization in the axial direction.
In addition, shown in the speed line chart, in realize advancing 6 retainings, 1 retaining that falls back, can make epicyclic reduction gear PR and planetary gear unit PU, transmit the transferring elements 440 that slows down and rotate thereby can shorten near configuration.Like this, can realize automatic transmission 1 8Miniaturization and light, simultaneously owing to can reduce inertial force, so can improve automatic transmission 1 5Controlled, reduce speed change and impact.
In addition, structure as realize advancing 6 retainings, 1 retaining that falls back, because clutch C1, C2 combination simultaneously in 4 retainings that advance, promptly be in direct-connected state at 4 retainings that advance, thereby can set the gear ratio of higher advance 5 retainings and 6 retainings that advance, when particularly carrying on vehicle, for the vehicle of running at high speed, can reduce the rotating speed of motor, thereby the quiet characteristic of the vehicle of running at high speed is provided.
In addition, as the driving wheel transfer mechanism, have to the differential mechanism portion 5 of driving wheel output rotation and the middle axial region 4 that combines with this differential mechanism portion 5, output block is the counter shaft gear that meshes with middle axial region 4, thereby can be with automatic transmission 1 8Lift-launch is on FF vehicle for example.
(the 9th mode of execution)
The 1st, the 2nd and 5 mode of executions are made the 9th mode of execution of part change below in conjunction with Figure 29 to Figure 31 explanation.Figure 29 is the pattern sectional view of the automatic transmission of the automatic transmission of expression the 9th mode of execution.Figure 30 is the action schedule of the automatic transmission of the 9th mode of execution.Figure 31 is the speed line chart of the automatic transmission of the 9th mode of execution.In addition, the 9th mode of execution is except the part change, and the part identical with the 1st, the 2nd and the 5th mode of execution adopted identical symbol, and it illustrates omission.
The automatic transmission 2 of the automatic transmission 1 of the 9th mode of execution at first, is described in conjunction with Figure 29 9As shown in figure 29, on above-mentioned input shaft 20, has planetary gear unit PU and epicyclic reduction gear (as the rotation output mechanism that slows down) PR.This planetary gear unit PU has as the sun gear of 4 rotation key elements (the 3rd rotation key element, the 2nd sun gear) S2, planetary carrier (the 2nd rotation key element, the 2nd planetary carrier) CR2, ring gear (the 4th rotation key element, the 2nd ring gear) R2 and sun gear (the 1st rotation key element, the 3rd sun gear) S3.On this planetary carrier CR2, supported by side plate 542,544 and be meshing with each other with the long small gear PL of sun gear S2 and ring gear R2 engagement with the short and small gear PS of sun gear S3 engagement, be so-called drawing and tie up Nao formula planetary pinion.In addition, planetary carrier (the fixed factors of above-mentioned epicyclic reduction gear PR, the 1st planetary carrier) on the CR1, with ring gear (output rotation key element, the 1st ring gear) the small gear P2 of R1 engagement and with sun gear (input rotation key element, the 1st sun gear) the small gear P1 of S1 engagement is meshing with each other, and is so-called double pinion planetary pinion.
On the above-mentioned input shaft 20, all sides dispose and have Hydrauservo System 565 in it, friction plate 572, form the drum type parts 522 of clutch drum (the 1st clutch drum), multidisc clutch (the 1st clutch) C3 of the wheelboss part that is connected with planetary carrier CR2 (parts that are connected with the 2nd rotation key element) 523, its outer circumferential side disposes has Hydrauservo System 262, friction plate 571, form the tympanic part spare 524 of clutch drum (the 2nd clutch drum), multidisc clutch (the 2nd clutch) C2 of the wheelboss part that is connected with sun gear S2 (parts that are connected with the 3rd rotation key element) 525.
This Hydrauservo System 565 comprise have piston element (the 1st piston) 565b that is used to press friction plate 272, the drum type parts 522 with the 565e of cylinder portion, hydraulic chamber (the 1st hydraulic servo hydraulic chamber) 565a that between this piston element 565b and the 565e of this cylinder portion, forms by seal ring 565f, 565g sealing, make this piston element 565b towards the stressed Returnning spring 565c of the direction of this hydraulic chamber 565a, bear the restoring board 565d of the spring force of this Returnning spring 565c.The oil circuit 20a, the 20b that form on this hydraulic chamber 565a and the above-mentioned input shaft 20 are communicated with, and this oil circuit 20a extends to an end of housing 3, are communicated with the oil circuit 591 of the hub portion 3c of sleeve shape on the input shaft 20.Therefore, this oil circuit 591 is communicated with not shown hydraulic control device.Promptly, form the oil circuit of never illustrated hydraulic control device to hydraulic chamber 565a so pass through hub portion 3c and 1 pair of seal ring between the input shaft 20 581 of seal casinghousing 3 because above-mentioned Hydrauservo System 565 is configured on the input shaft 20.
In addition, this Hydrauservo System 562 comprise have piston element (the 2nd piston) 562b that is used to press friction plate 271, the drum type parts 524 with the 562e of cylinder portion, hydraulic chamber (the 2nd hydraulic servo hydraulic chamber) 562a that between this piston element 562b and the 562e of this cylinder portion, forms by seal ring 562f, 562g sealing, make this piston element 562b towards the stressed Returnning spring 562c of the direction of this hydraulic chamber 562a, bear the restoring board 562d of the spring force of this Returnning spring 562c.This hydraulic chamber 562a is communicated with the oil circuit 592 of above-mentioned hub portion 3c, and this oil circuit 592 is communicated with not shown hydraulic control device.Be the hub portion 3c and 1 pair seal ring cylinder portion 562e between 580 formation never illustrated hydraulic control device oil circuit to hydraulic chamber 562a of above-mentioned Hydrauservo System 562 by seal casinghousing 3.
In addition, dispose multi-plate brake (the 3rd break) B2 on the outer circumferential side of wheelboss part 525 with Hydrauservo System 563, friction plate 574.This Hydrauservo System 563 comprise have the piston element 563b that is used to press friction plate 574, the 563e of cylinder portion that forms on the part of housing 3b, the hydraulic chamber 563a that between this piston element 563b and the 563e of this cylinder portion, forms by seal ring 563f, 563g sealing, make this piston element 563b towards the stressed Returnning spring 563c of the direction of this hydraulic chamber 563a, bear the restoring board 563d of the spring force of this Returnning spring 563c.
Be that above-mentioned input shaft 20 is connected with above-mentioned drum type parts 522, all sides dispose the clutch C3 with Hydrauservo System 565 free combinations by clutch C3 with the spline combination in the end of these drum type parts 522.Interior all sides of this clutch C3 are connected with wheelboss part 523 with the spline combination.This wheelboss part 523 is connected with above-mentioned sun gear S2.In addition, dispose the clutch C2 with Hydrauservo System 562 free combinations by clutch C2 with the spline combination on all sides in the end of above-mentioned drum type parts 524, interior all sides of this clutch C2 are connected with wheelboss part 525 with the spline combination.In addition, dispose the break B2 that freely brakes with Hydrauservo System 563 by break B2 with the spline combination on the outer circumferential side of these drum type parts 525.This wheelboss part 525 is connected with above line gear rack CR2.
On the other hand, (left among the figure) disposes and has Hydrauservo System 561, friction plate 575, forms multidisc clutch (the 3rd clutch) C1 of the drum type parts 531 of clutch drum (the 3rd clutch drum) on the other end of input shaft 20.The hydraulic chamber 561a that this Hydrauservo System 561 comprises the piston element 561b that is used to press friction plate 575, the drum type parts 531 with the 561e of cylinder portion, formed by seal ring 561f, 561g sealing between this piston element 561b and the 561e of this cylinder portion, make this piston element 561b towards the stressed Returnning spring 561c of the direction of this hydraulic chamber 561a, bear the restoring board 561d of the spring force of this Returnning spring 561c.In addition, the clutch drum of being made up of drum type parts 531 is to the direction opening of epicyclic reduction gear PR, this epicyclic reduction gear PR be configured in Hydrauservo System 561 and planetary gear unit PU axially between.In addition, friction plate 575 is configured in the position with the radial outer diameter side superimposed of epicyclic reduction gear PR.
This hydraulic chamber 561a extends to the other end of a side opposite with above-mentioned hub portion 3c of housing 3, is communicated with the oil circuit 593 of the hub portion 3d of sleeve shape on the input shaft 20, and this oil circuit 593 is communicated with not shown hydraulic control device.The hub portion 3d that is above-mentioned Hydrauservo System 561 by housing 3 and have 1 pair of seal ring 582 between the drum type parts 532 of the 561e of cylinder portion forms the oil circuit of never illustrated hydraulic control device to hydraulic chamber 561a.
I.e. left side in the drawings, above-mentioned hub portion 3d upper support has the drum type parts 531 that can rotate freely, and all sides dispose the clutch C1 with Hydrauservo System 561 free combinations by clutch C1 with the spline combination in the end of these drum type parts 561.Interior all sides at this clutch C1 dispose the wheelboss part 532 that forms above-mentioned ring gear R1 with the spline combination, and these wheelboss part 532 rotations are supported on the hub portion 3d freely.In addition, planetary carrier CR1 has small gear P1 and small gear P2, this small gear P2 and above-mentioned ring gear R1 engagement, this small gear P1 and the sun gear S1 engagement that is connected on the input shaft 20.This planetary carrier CR1 is fixed on the housing 3b by side plate 633.
And, the drum type parts 531 that combine with above-mentioned clutch C1 spline are supported and can rotate freely by above-mentioned hub portion 3d, when clutch C1 in conjunction with the time, be connected with the transferring elements 540 of the rotation of transmitting ring gear R1, in addition, the opposite side of this transferring elements 540 is connected with the sun gear S3 of above-mentioned planetary gear unit PU.
On the other hand, at the outer circumferential side of planetary gear unit PU, dispose have Hydrauservo System 564, multi-plate brake (the 2nd break) B1 and overrunning clutch (the 1st overrunning clutch) F3 of friction plate 573, wheelboss part 547.This Hydrauservo System 564 comprise have the piston element 564b that is used to press friction plate 573, the 564e of cylinder portion that forms on the part of housing 3b, the hydraulic chamber 564a that between this piston element 564b and the 564e of this cylinder portion, forms by seal ring 564f, 564g sealing, make this piston element 564b towards the stressed Returnning spring 564c of the direction of this hydraulic chamber 564a, bear the restoring board 564d of the spring force of this Returnning spring 564c.
The side plate 542 that is the planetary carrier CR2 of above-mentioned planetary gear unit PU is connected with the wheelboss part 547 that is connected with above-mentioned break B2 by spline, and this wheelboss part 547 is connected with the inner ring of overrunning clutch F3.Then, the long small gear PL of this planetary carrier CR2 and above-mentioned ring gear R2 engagement, the end of this ring gear R2 is connected with connected element 545, and this ring gear R2 is connected with counter shaft gear 50 by connected element 545.
As above shown in the explanation, the axial side configuration epicyclic reduction gear PR of planetary gear unit PU, axially opposite side disposes clutch C2, clutch C3 and break B1, disposes counter shaft gear 50 between clutch C2, clutch C3 and break B1 and planetary gear unit PU.In addition, clutch C1 is configured in the outer circumferential side of epicyclic reduction gear PR, and break B2 is configured in the outer circumferential side of planetary gear unit PU.In addition, epicyclic reduction gear PR, planetary gear unit PU and counter shaft gear 50 are set to coaxial configuration with input shaft 20.
Then, according to said structure, the effect of automatic transmission 29 is described in conjunction with Figure 29, Figure 30 and Figure 31.In speed line chart shown in Figure 31, the longitudinal axis is represented the rotating speed of each rotation key element, and transverse axis then rotates the gear ratio of key elements corresponding to these.In the part of the planetary gear unit PU of this speed line chart, the longitudinal axis of lateral ends (right side among Figure 31) is corresponding to sun gear S3, and the longitudinal axis is left successively corresponding to ring gear R2, planetary carrier CR2, sun gear S2 among the figure.
As shown in figure 29, by the combination of clutch C2, the rotation of input shaft 20 is input to above-mentioned sun gear S2.This sun gear S1 fixes freely by the braking of break B1.By the combination of clutch C3, the rotation of input shaft 20 is input to above line gear rack CR2, the rotation of this planetary carrier CR2 simultaneously fix freely by the braking of break B2, and limits the rotation of a direction by overrunning clutch F3.
On the other hand, above-mentioned sun gear S1 is connected with input shaft 20, and imports the rotation of this input shaft 20.In addition, above line gear rack CR1 is connected with housing 3b, and rotation is fixing, so ring gear R1 deceleration rotation.In addition, by the combination of clutch C1, the deceleration of this ring gear R1 rotation is input to sun gear S3.
Then, the rotation of above-mentioned ring gear R2 outputs to above-mentioned counter shaft gear 50, and outputs to not shown wheel by this counter shaft gear 50, above-mentioned middle axial region 4 and differential mechanism portion 5 (with reference to Fig. 1).
As shown in figure 30,1 retaining that advances in D (driving) position, clutch C1 and overrunning clutch F3 combination.Like this, as shown in figure 31, the deceleration of ring gear R1 rotation is input to sun gear S3 by clutch C1, transferring elements 540.In addition, the rotation of planetary carrier CR2 is limited in a direction (being rotated in the forward direction), i.e. the counterrotating of planetary carrier CR2 is prevented from and is in stationary state.Then, by being input to deceleration rotation and the fixing planetary carrier CR2 of sun gear S3, ring gear R2 becomes being rotated in the forward of 1 retaining that advances, and its rotation is from counter shaft gear 50 outputs.
In addition, when engine braking, break B1 braking, planetary carrier CR2 fixes, thereby to prevent the form that is rotated in the forward of this planetary carrier CR2, to keep 1 state that keeps off that advances.In addition,, prevent planetary carrier CR2 counterrotating by overrunning clutch F3, and it can be rotated in the forward, thereby can realize switching to 1 retaining that advances when travelling reposefully by the automatic combination of overrunning clutch from for example non-position of travelling at 1 retaining that advances.In addition, sun gear S3 and ring gear R1 rotate for slowing down owing to this moment, so above-mentioned transferring elements 540 can transmit bigger torque.
As shown in figure 30,2 retainings that advance in D (driving) position, clutch C1 combination, break B2 braking.Like this, as shown in figure 31, the deceleration of ring gear R1 rotation is input to sun gear S3 by clutch C1, transferring elements 540, passes through the rotation of break B2 fixed stars gear S3 simultaneously.Like this, the rotation of planetary carrier CR2 is slowed down a little, and by the deceleration rotation and this planetary carrier CR2 that slows down a little and rotate that are input to sun gear S3, ring gear R2 becomes being rotated in the forward of 2 retainings that advance, and its rotation is from counter shaft gear 50 outputs.In addition, also since this moment sun gear S3 and ring gear R1 for the rotation of slowing down, so above-mentioned transferring elements 540 can transmit bigger torque.
As shown in figure 30,3 retainings that advance in D (driving) position, clutch C1 and clutch C2 combination.Like this, as shown in figure 31, the deceleration of ring gear R1 rotation is by clutch C1, transferring elements 540 to sun gear S3, and the rotation of input shaft 20 simultaneously is because the combination of clutch C2 is input to sun gear S2.Like this, the rotation of the input shaft 20 by being input to sun gear S2 and the deceleration of sun gear S3 rotation, the deceleration rotation of this sun gear S3 is a bit larger tham in the deceleration rotation of planetary carrier CR2.Then, because the deceleration of the input rotation of sun gear S2 and sun gear S3 rotation, ring gear R2 is being rotated in the forward of 3 retainings of advancing, and its rotation is from counter shaft gear 50 outputs.In addition, also because this moment sun gear S3 and ring gear R1 are the rotation of slowing down, above-mentioned transferring elements 540 can transmit bigger torque.
As shown in figure 30,4 retainings that advance in D (driving) position, clutch C1 and clutch C3 combination.Like this, as shown in figure 31, the deceleration of ring gear R1 rotation is by clutch C1, transferring elements 540 to sun gear S3, and the rotation of input shaft 20 simultaneously is input to planetary carrier CR2 by clutch C3.Like this, owing to be input to the rotation of input shaft 20 of planetary carrier CR2 and the deceleration rotation of sun gear S3, ring gear R2 is being rotated in the forward of 4 retainings of advancing, and its rotation is from counter shaft gear 50 outputs.In addition, this moment is because sun gear S3 and ring gear R1 also are the rotation of slowing down, so above-mentioned transferring elements 540 can transmit bigger torque.
As shown in figure 30,5 retainings that advance in D (driving) position, clutch C2 and clutch C3 combination.Like this, as shown in figure 31, the rotation of input shaft 20 is input to planetary carrier CR2 by clutch C3, and the rotation of input shaft 20 simultaneously is input to sun gear S2 by clutch C2.Like this, since be input to sun gear S2 input shaft 20 rotation and be input to the rotation of the input shaft 20 of planetary carrier CR2, promptly ring gear R2 is direct-connected rotation status, as 5 retainings that advance, for with being rotated in the forward of input shaft 20 identical rotations, its rotation is from counter shaft gear 50 outputs.
As shown in figure 30,6 retainings that advance in D (driving) position, clutch C3 combination, break B2 braking.Like this, as shown in figure 31, the rotation of input shaft 20 is input to planetary carrier CR2 by clutch C3, simultaneously because the braking of break B2 makes sun gear S2 fix.Like this, owing to the rotation of the input shaft 20 that is input to planetary carrier CR2 and fixing sun gear S2, ring gear R2 is the 6 speedups rotations that keep off of advancing, and its rotation is from counter shaft gear 50 outputs.
As shown in figure 30,1 retaining that falls back in R (reversing gear) position, clutch C2 combination, break B1 braking.Like this, as shown in figure 31, the rotation of input shaft 20 is input to sun gear S2 by the combination of clutch C2, simultaneously because the braking of break B1 makes the rotation of planetary carrier CR2 fix.Like this, owing to the rotation of the input shaft 20 that is input to sun gear S2 and fixing planetary carrier CR2, ring gear R2 is 1 counterrotating that keeps off that falls back, and its rotation is from counter shaft gear 50 outputs.
P (parking) or N (neutral) position, clutch C1, clutch C2 and clutch C3 discharge, and the transmission of power between input shaft 20 and the counter shaft gear 50 is in dissengaged positions, automatic transmission 2 9Integral body is in idling conditions (neutral state).In addition, though the fixedly break B1 of planetary carrier CR2 braking, this is for the frequent braking that prevents this break B1 discharges, to automatic transmission 2 9Rotation status of other interior rotation key elements can not exert an influence.
As mentioned above, according to automatic transmission 2 of the present invention 9Epicyclic reduction gear PR as the rotation output mechanism that slows down, clutch C1, and transferring elements 540 is configured in the axial side (left side among Figure 29) of planetary gear unit PU, clutch C2 and clutch C3 are configured in the axial opposite side (right side among Figure 29) of planetary gear unit PU, and, counter shaft gear 50 as output block is configured between clutch C2 and clutch C3 and the planetary gear unit PU, particularly can make epicyclic reduction gear PR and planetary gear unit PU near configuration, thereby the axial length of transmitting the transferring elements 540 of the rotation of slowing down can be shorter.Like this, can realize miniaturization, the light of automatic transmission 19, simultaneously because the light of transferring elements 540 can reduce inertial force, so can improve automatic transmission 1 9Controlled, reduce speed change and impact.
In addition, because the outer circumferential side of clutch C2 by clutch C3 be connected with planetary carrier CR2, thereby the parts can prevent that respectively rotating key element connects the time interlock realization automatic transmission 1 9Miniaturization.
In addition, though the outer circumferential side of clutch C3 can not be to the outer circumferential side enlarged owing to dispose clutch C2, but by Hydrauservo System 565 is set on input shaft 20, (for example comparing situation about on hub portion 3c, being provided with), can guarantee this bigger Hydrauservo System 565, the especially compression area of Hydrauservo System 565 usefulness hydraulic chamber 565a in interior all sides, thereby can increase the capacity of clutch C3.
In addition since with input shaft 20 coaxial epicyclic reduction gear PR, planetary gear unit PU and the counter shaft gears 50 of being provided with, particularly on the FF vehicle, carry automatic transmission 1 9The time, (for example with respect to the situation that epicyclic reduction gear etc. is set on other) can realize the miniaturization of driving wheel transfer mechanism (for example axial region 4 etc.), can prevent and the interference of for example body part, improves automatic transmission 1 9Vehicle boarded performance.
In addition, because connecting, clutch C1 disconnects the rotation of slowing down, thereby the rotation of slowing down freely can be input to sun gear S3,, be rotated in epicyclic reduction gear PR, particularly the ring gear R1 place of the input shaft that is input on the sun gear S1 be dallied simultaneously by the release of clutch C1.Like this, can break be set and planetary carrier CR1 directly is fixed on the housing 3, thereby can realize automatic transmission 1 9Miniaturization and light.
In addition, because Hydrauservo System 565 is arranged on the input shaft 20, utilize a pair of seal ring 281 to stop leakage and oil circuit 20a, 20b fuel feeding in being arranged on input shaft 20 from housing 3, so needn't between for example input shaft 20 and Hydrauservo System 565, seal ring be set, just can be to the hydraulic chamber 565a of Hydrauservo System 565 fuel feeding.In addition, Hydrauservo System 562,561 is hub portion 3c, the 3d fuel feeding by being provided with from housing 3 extensions respectively, and by for example other parts, promptly can carry out fuel feeding by a pair of seal ring 580,582 is set respectively.Therefore, as long as a pair of seal ring 581,580,582 is set respectively in Hydrauservo System 565,562,561, just can fuel feeding, thus minimum is reduced in the sliding friction that seal ring causes, its result will improve automatic transmission 1 9Efficient.
In addition, because friction plate 575 is configured in the outer radial periphery side of epicyclic reduction gear PR, thereby can make automatic transmission 1 in the axial direction 9Miniaturization.In addition, because between the Hydrauservo System 561 by epicyclic reduction gear PR being configured in clutch C1 and planetary gear unit PU axial, epicyclic reduction gear PR and planetary gear unit PU can disposed adjacent (because the Hydrauservo System of clutch C1 561 is not between epicyclic reduction gear PR and planetary gear unit PU), thereby transferring elements 540 can be shorter.Like this, can realize automatic transmission 1 9Miniaturization and light, simultaneously owing to can reduce inertial force, so can improve automatic transmission 1 9Controlled, reduce speed change and impact.
In addition, because epicyclic reduction gear PR is the double pinion planetary pinion, thereby the rotation that can make input shaft 20 is as the rotation output of slowing down, even set good automatic transmission 1 simultaneously 9The gear ratio, what also need not increase planetary gear unit, epicyclic reduction gear respectively rotates key element, thereby can suppress high speed rotating, realizes automatic transmission 1 9Miniaturization.
In addition, rotate key element sun gear S1, fixed factors planetary carrier CR1, output rotation key element ring gear R1 because epicyclic reduction gear PR comprises input, thereby the rotation of input shaft 20 can be exported as the rotation of slowing down.
In addition, because planetary gear unit PU ties up Nao formula planetary pinion for drawing of being made up of sun gear S2, sun gear S3, planetary carrier CR2 and ring gear R2, so in 6 retainings of can realizing for example advancing, 1 retaining that falls back, can also make epicyclic reduction gear PR and planetary gear unit PU near configuration, thereby can shorten the transferring elements 540 that transmits the rotation of slowing down.
In addition, owing to have and dispose side by side with break B1 and at the overrunning clutch F3 of the rotation of a direction restrictions planetary gear frame CR2,1 retaining that advances when realizing for example just driving of clutch C1 and overrunning clutch F3 can be utilized, thereby 1 retaining that advances when travelling can be realized switching to reposefully from for example non-position of travelling.
In addition, because break B1 and overrunning clutch F3 are configured in the outer circumferential side of planetary gear unit PU, with for example the situation of overrunning clutch F3 adjacent with clutch C2 the rotation of a direction of limited wheel boss assembly 523 (particularly for) configuration is compared, can make the partly miniaturization in the axial direction that is provided with of clutch C1, C2, thereby make counter shaft gear 50 near the fluid torque converter sides.Like this, because the gear 51 of jack shaft 52 also can be near the fluid torque converter side, thereby can make jack shaft portion 4 miniaturization in the axial direction.
In addition, shown in the speed line chart, in realize advancing 6 retainings, 1 retaining that falls back, can make epicyclic reduction gear PR and planetary gear unit PU, transmit the transferring elements 540 that slows down and rotate thereby can shorten near configuration.Like this, can realize automatic transmission 1 9Miniaturization and light, simultaneously owing to can reduce inertial force, so can improve automatic transmission 1 9Controlled, reduce speed change and impact.
In addition, this automatic transmission 2 9, promptly 1 block to 4 retainings of 4 retainings that advance and to export the rotation of slowing down for direct-connected state at 5 retainings that advance, particularly on vehicle, carry automatic transmission 2 from above-mentioned advancing 9The time, can segment the low-medium speed zone of vehicle.Like this,, can use the rotary speed area with optimum efficiency of driving source such as motor more, improve the Economy of fuel particularly in the low-medium speed zone of vehicle.In addition,, thereby 6 retainings that advance are driven for hypervelocity, thereby being hypervelocity and driving and compare, can reduce final reduction speed ratio with advance for direct-connected state makes 5 retainings and 6 retainings that advance of 4 retainings that advance because 5 retainings that advance are for direct-connected state.Like this, can reduce for example spider gear diameter of differential mechanism portion 5, shorten the axle base of the axle of input shaft 20 and differential mechanism portion 5, particularly carry when the FF vehicle, can realize automatic transmission 1 9Miniaturization.
In addition, as the driving wheel transfer mechanism, have to the differential mechanism portion 5 of driving wheel output rotation and the middle axial region 4 that combines with this differential mechanism portion 5, output block is the counter shaft gear that meshes with middle axial region 4, thereby can be with automatic transmission 1 9Lift-launch is on FF vehicle for example.
(the 10th mode of execution)
The 9th mode of execution is made the 10th mode of execution of part change below in conjunction with Figure 32 to Figure 34 explanation.Figure 32 is the pattern sectional view of the automatic transmission of the automatic transmission of expression the 10th mode of execution.Figure 33 is the action schedule of the automatic transmission of expression the 10th mode of execution.Figure 34 is the speed line chart of the automatic transmission of the 10th mode of execution.In addition, the 10th mode of execution is except the part change, and the part identical with the 9th mode of execution adopted identical symbol, and it illustrates omission.
Shown in figure 32, the automatic transmission 2 of the automatic transmission 1 of the 10th mode of execution 10Automatic transmission 2 with the 9th mode of execution 9Compare (with reference to Figure 29), changed the configuration of epicyclic reduction gear (as the rotation output mechanism that slows down) PR and clutch (the 3rd clutch) C1.
This automatic transmission 2 10In, clutch C1 is configured in the side opposite with planetary gear unit PU (left side among the figure) of epicyclic reduction gear PR, and all sides combine with friction plate 575 by spline in the end of the drum type parts 631 of this clutch C1.In addition, the drum type parts 631 of this clutch C1 are connected with input shaft 20.
On the other hand, sun gear (input rotation key element, the 1st sun gear) S1 is transfused to axle 20 to be supported and can rotate freely, and is connected with wheelboss part 632 simultaneously, and the end outer shaft side of this wheelboss part 632 and above-mentioned friction plate 575 are connected by spline.In addition, the side plate of planetary carrier (fixed factors, the 1st planetary carrier) CR1 is connected with fixed component 633, is fixed on the housing 3b.Then, the outer circumferential side of ring gear (output rotation key element, the 1st ring gear) R1 is connected with transferring elements 640 by spline, is connected with sun gear S3 by this transferring elements 640.
Then, according to said structure, automatic transmission 2 is described in conjunction with Figure 32, Figure 33 and Figure 34 10Effect.In addition, the same with above-mentioned the 9th mode of execution, in speed line chart shown in Figure 34, the longitudinal axis is represented the rotating speed of each rotation key element, and transverse axis then rotates the gear ratio of key elements corresponding to these.In the part of the planetary gear unit PU of this speed line chart, the longitudinal axis of lateral ends (right side among Figure 34) is corresponding to sun gear S3, and the longitudinal axis is left successively corresponding to planetary carrier CR2, ring gear R2, sun gear S2 among the figure.
Shown in figure 32, by the combination of clutch C1, the rotation of input shaft 20 is input to above-mentioned sun gear S1.The rotation of above line gear rack CR1 is fixing with respect to housing 3, and above-mentioned ring gear R1 does the rotation of slowing down according to the rotation of the input shaft 20 that is input to this sun gear S1.Promptly by the combination of clutch C1, the deceleration rotation of ring gear R1 is input to sun gear S3 by transferring elements 640.
Therefore, as Figure 33 and shown in Figure 34, for epicyclic reduction gear PR, advance 1 the retaining, advance 2 the retaining, advance 3 the retaining, advance 4 the retaining, because the combination of clutch C1, the rotation of input shaft 20 is input to sun gear S1, rotates because fixing planetary carrier CR1 imports deceleration to ring gear R3, and rotates to sun gear S3 input deceleration by transferring elements 640.At this moment, because ring gear R1 and sun gear S3 are for the rotation of slowing down, so above-mentioned transferring elements 640 can transmit bigger torque.On the other hand, advance 5 the retaining, advance 6 the retaining, fall back 1 the retaining, the rotation of sun gear S3 is input to ring gear R1 by transferring elements 640, because the release of clutch C1, as shown in figure 34, sun gear S1 is rotated in the rotation of each gear stage and fixing planetary carrier CR1 according to this ring gear R1.
In addition, the effect outside the above-mentioned epicyclic reduction gear PR is the same with above-mentioned the 9th mode of execution, its explanation of Therefore, omited.
As mentioned above, according to automatic transmission 2 of the present invention 10As epicyclic reduction gear PR, the clutch C1 of rotation output mechanism and the axial side that transferring elements 640 is configured in planetary gear unit PU (left side among Figure 32) of slowing down, clutch C2 and clutch C3 are configured in the axial opposite side (right side among Figure 32) of planetary gear unit PU, counter shaft gear 50 as output block is configured between clutch C2 and clutch C3 and the planetary gear unit PU, particularly can make epicyclic reduction gear PR and planetary gear unit PU near configuration, thereby the axial length of transmitting the transferring elements 640 of the rotation of slowing down can be shorter.Like this, can realize automatic transmission 1 10Miniaturization, light, simultaneously because the light of transferring elements 640 can reduce inertial force, so can improve automatic transmission 1 10Controlled, reduce speed change and impact.
In addition, because the outer circumferential side of clutch C2 by clutch C3 be connected with planetary carrier CR2, thereby the parts can prevent that respectively rotating key element connects the time interlock realization automatic transmission 1 10Miniaturization.
In addition, though clutch C3 disposes clutch C2 at its outer circumferential side, can not be to the outer circumferential side enlarged, but by Hydrauservo System 565 is set on input shaft 20, (for example with respect to situation about on hub portion 3c, being provided with), can guarantee this bigger Hydrauservo System 565, the especially compression area of Hydrauservo System 565 usefulness hydraulic chamber 565a in interior all sides, thereby can increase the capacity of clutch C3.
In addition since with input shaft 20 coaxial epicyclic reduction gear PR, planetary gear unit PU and the counter shaft gears 50 of being provided with, particularly on the FF vehicle, carry automatic transmission 1 10The time, (for example with respect to the situation that epicyclic reduction gear etc. is set on other) can realize the miniaturization of driving wheel transfer mechanism (for example axial region 4 etc.), prevents the interference of body part, improves automatic transmission 1 10Vehicle boarded performance.
In addition, for example the spy to open 2001-263438 communique etc. disclosed like that, if clutch C1 is configured between ring gear R1 and the sun gear S3, just need to connect and disconnect the rotation of slowing down, thereby need bigger parts, and the distance between epicyclic reduction gear PR and the planetary gear unit PU increases, but owing to be configured between input shaft 20 and the sun gear S1, connect the rotation that disconnects input shaft 20 by this clutch C1, thereby connect the deceleration rotation that disconnects from the ring gear R1 output of epicyclic reduction gear PR, therefore can realize the miniaturization of clutch C1, and epicyclic reduction gear PR and planetary gear unit PU are disposed on closer locations.Can realize automatic transmission 1 like this 10Miniaturization.
In addition, because Hydrauservo System 565 is arranged on the input shaft 20, utilize a pair of seal ring 281 to stop leakage and oil circuit 20a, 20b fuel feeding in being arranged on input shaft 20 from housing 3, so needn't between for example input shaft 20 and Hydrauservo System 565, seal ring be set, just can be to the hydraulic chamber 565a of Hydrauservo System 565 fuel feeding.In addition, Hydrauservo System 562,561 is hub portion 3c, the 3d fuel feeding by being provided with from housing 3 extensions respectively, and by for example other parts, promptly can carry out fuel feeding by a pair of seal ring 580,582 is set respectively.Therefore, as long as a pair of seal ring 581,580,582 is set respectively in Hydrauservo System 565,562,561, just can fuel feeding, thus minimum is reduced in the sliding friction that seal ring causes, its result will improve automatic transmission 1 10Efficient.
In addition, because epicyclic reduction gear PR is the double pinion planetary pinion, thereby the rotation that can make input shaft 20 is as the rotation output of slowing down, even set good automatic transmission 1 simultaneously 10The gear ratio, what also need not increase planetary gear unit, epicyclic reduction gear respectively rotates key element, thereby can suppress high speed rotating, realizes automatic transmission 1 10Miniaturization.
In addition, rotate key element sun gear S1, fixed factors planetary carrier CR1, output rotation key element ring gear R1 because epicyclic reduction gear PR comprises input, thereby the rotation of input shaft 20 can be exported as the rotation of slowing down.
In addition, because planetary gear unit PU ties up Nao formula planetary pinion for drawing of being made up of sun gear S2, sun gear S3, planetary carrier CR2 and ring gear R2, so in 6 retainings of can realizing for example advancing, 1 retaining that falls back, can also make epicyclic reduction gear PR and planetary gear unit PU near configuration, thereby can shorten the transferring elements 640 that transmits the rotation of slowing down.
In addition, owing to have and dispose side by side with break B1 and at the overrunning clutch F3 of the rotation of a direction restrictions planetary gear frame CR2,1 retaining that advances when realizing for example just driving of clutch C1 and overrunning clutch F3 can be utilized, thereby 1 retaining that advances when travelling can be realized switching to reposefully from for example non-position of travelling.
In addition, because break B1 and overrunning clutch F3 are configured in the outer circumferential side of planetary gear unit PU, with for example the situation of overrunning clutch F3 adjacent with clutch C2 the rotation of a direction of limited wheel boss assembly 523 (particularly for) configuration is compared, can make the partly miniaturization in the axial direction that is provided with of clutch C1, C2, thereby make counter shaft gear 50 near the fluid torque converter sides.Like this, because the gear 51 of jack shaft 52 also can be near the fluid torque converter side, thereby can make jack shaft portion 4 miniaturization in the axial direction.
In addition, shown in the speed line chart, in realize advancing 6 retainings, 1 retaining that falls back, can make epicyclic reduction gear PR and planetary gear unit PU, transmit the transferring elements 640 that slows down and rotate thereby can shorten near configuration.Like this, can realize automatic transmission 1 10Miniaturization and light, simultaneously owing to can reduce inertial force, so can improve automatic transmission 1 10Controlled, reduce speed change and impact.
In addition, this automatic transmission 2 10, promptly 1 block to 4 retainings of 4 retainings that advance and to export the rotation of slowing down for direct-connected state at 5 retainings that advance, particularly on vehicle, carry automatic transmission 2 from above-mentioned advancing 10The time, can segment the speed change in the low-medium speed zone of vehicle.Like this,, can use the rotary speed area with optimum efficiency of driving source such as motor more, improve the Economy of fuel particularly in the low-medium speed zone of vehicle.In addition,, thereby 6 retainings that advance are driven for hypervelocity, thereby being hypervelocity and driving and compare, can reduce final deceleration with advance for direct-connected state makes 5 retainings and 6 retainings that advance of 4 retainings that advance because 5 retainings that advance are for direct-connected state.Like this, can reduce for example spider gear diameter of differential mechanism portion 5, shorten the axle base of the axle of input shaft 20 and differential mechanism portion 5, when particularly carrying on the FF vehicle, can realize automatic transmission 1 10Miniaturization.
In addition, as the driving wheel transfer mechanism, have to the differential mechanism portion 5 of driving wheel output rotation and the middle axial region 4 that combines with this differential mechanism portion 5, output block is the counter shaft gear that meshes with middle axial region 4, thereby can be with automatic transmission 1 10Lift-launch is on FF vehicle for example.
(the 11st mode of execution)
The 9th mode of execution is made the 11st mode of execution of part change below in conjunction with Figure 35 to Figure 37 explanation.Figure 35 is the pattern sectional view of the automatic transmission of the automatic transmission of expression the 11st mode of execution.Figure 36 is the action schedule of the automatic transmission of the 11st mode of execution.Figure 37 is the speed line chart of the automatic transmission of the 11st mode of execution.In addition, the 11st mode of execution is except the part change, and the part identical with the 9th mode of execution adopted identical symbol, and it illustrates omission.
As shown in figure 35, the automatic transmission 2 of the automatic transmission 1 of the 11st mode of execution 11Automatic transmission 2 with the 9th mode of execution 9Compare (with reference to Figure 29), arrangement brake device (the 3rd break) B3 is to substitute clutch C1, and it is fixing freely that planetary carrier (fixed factors, the 1st planetary carrier) CR1 of epicyclic reduction gear (as the rotation output mechanism that slows down) PR is braked device B3.
This automatic transmission 2 11In, break B3 is configured in the side opposite with planetary gear unit PU (left side among the figure) of epicyclic reduction gear PR, this break B3 has Hydrauservo System 566, friction plate 576, wheelboss part 731, this Hydrauservo System 566 comprise having the piston element 566b that is used to press friction plate 576, the 566e of cylinder portion that on the part of housing 3b, forms, between this piston element 566b and the 566e of this cylinder portion by seal ring 566f, the hydraulic chamber 566a that the 566g sealing forms, make this piston element 566b towards the stressed Returnning spring 566c of the direction of this hydraulic chamber 566a, bear the restoring board 566d of the spring force of this Returnning spring 566c.
The wheelboss part 731 of this break B3 is connected with the side plate 732 of planetary carrier CR1, and this side plate 732 is supported and can rotate freely by hub portion 3d.Then, sun gear (input rotation key element with the small gear P1 of this planetary carrier CR1 engagement, the 1st sun gear) S1 is connected with input shaft 20, while (is exported the rotation key element with the ring gear of the small gear P2 engagement of this planetary carrier CR1, the 1st ring gear) R1 is connected with transferring elements 740, is connected with sun gear S3 by this transferring elements 740.
Then, according to said structure, automatic transmission 2 is described in conjunction with Figure 35, Figure 36 and Figure 37 11Effect.In addition, the same with above-mentioned the 9th mode of execution, in speed line chart shown in Figure 37, the longitudinal axis is represented the rotating speed of each rotation key element, and transverse axis then rotates the gear ratio of key elements corresponding to these.In the part of the planetary gear unit PU of this speed line chart, the longitudinal axis of lateral ends (right side among Figure 37) is corresponding to sun gear S3, and the longitudinal axis is left successively corresponding to ring gear R2, planetary carrier CR2, sun gear S2 among the figure.
As shown in figure 35, braking by break B3, the rotation of above line gear rack CR1 is fixed with respect to housing 3b, in addition, the rotation of input shaft 20 is input to sun gear S1, above-mentioned ring gear R1 does the rotation of slowing down by fixing this planetary carrier CR1 according to the rotation of the input shaft 20 that is input to this sun gear S1.Promptly by the braking of break B3, the deceleration rotation of ring gear R1 is input to sun gear S3 by transferring elements 740.
Therefore, as Figure 36 and shown in Figure 37, for epicyclic reduction gear PR, advance 1 the retaining, advance 2 the retaining, advance 3 the retaining, advance 4 the retaining, because the braking of break B3, planetary carrier CR1 fixes, the sun gear S1 of the rotation by having imported input shaft 20, the rotation of slowing down outputs to ring gear R3, and imports the rotation of slowing down by transferring elements 740 to sun gear S3.At this moment, because ring gear R1 and sun gear S3 are for the rotation of slowing down, so above-mentioned transferring elements 740 can transmit bigger torque.On the other hand, since advance 5 the retaining, advance 6 the retaining, fall back 1 the retaining, the rotation of sun gear S3 is input to ring gear R1 by transferring elements 740, break B3 discharges, as shown in figure 37, planetary carrier CR1 is rotated at the sun gear S1 of the rotation of the rotation of each gear stage and input shaft 20 according to this ring gear R1.
In addition, the effect outside the above-mentioned epicyclic reduction gear PR is the same with above-mentioned the 9th mode of execution, its explanation of Therefore, omited.
As mentioned above, according to automatic transmission 2 of the present invention 11As epicyclic reduction gear PR, the break B3 of rotation output mechanism and the axial side that transferring elements 740 is configured in planetary gear unit PU (left side among Figure 35) of slowing down, clutch C2 and clutch C3 are configured in the axial opposite side (right side among Figure 35) of planetary gear unit PU, counter shaft gear 50 as output block is configured between clutch C2 and clutch C3 and the planetary gear unit PU, particularly can make epicyclic reduction gear PR and planetary gear unit PU near configuration, thereby the axial length of transmitting the transferring elements 740 of the rotation of slowing down can be shorter.Like this, can realize automatic transmission 1 11Miniaturization, light, simultaneously because the light of transferring elements 740 can reduce inertial force, so can improve automatic transmission 1 11Controlled, reduce speed change and impact.
In addition, because the outer circumferential side of clutch C2 by clutch C3 be connected with planetary carrier CR2, thereby the parts can prevent that respectively rotating key element connects the time interlock realization automatic transmission 1 11Miniaturization.
In addition, though clutch C3 disposes clutch C2 at its outer circumferential side, can not be to the outer circumferential side enlarged, but by Hydrauservo System 565 is set on input shaft 20, (for example with respect to situation about on hub portion 3c, being provided with), can guarantee this bigger Hydrauservo System 565, the especially compression area of Hydrauservo System 565 usefulness hydraulic chamber 565a in interior all sides, thereby can increase the capacity of clutch C3.
In addition since with input shaft 20 coaxial epicyclic reduction gear PR, planetary gear unit PU and the counter shaft gears 50 of being provided with, particularly on the FF vehicle, carry automatic transmission 1 11The time, (for example with respect to the situation that epicyclic reduction gear etc. is set on other) can realize the miniaturization of driving wheel transfer mechanism (for example axial region 4 etc.), prevents and the interference of body part, improves automatic transmission 1 11Vehicle boarded performance.
In addition, connect the output that disconnection is slowed down and rotated owing to pass through the combination of break B3, the clutch that disconnects the deceleration rotation with connection is compared, and can realize the miniaturization of break B3, and epicyclic reduction gear PR and planetary gear unit PU are disposed close.Can realize automatic transmission 1 like this 11Miniaturization and light.
In addition, because Hydrauservo System 565 is arranged on the input shaft 20, utilize a pair of seal ring 581 to stop leakage and oil circuit 20a, 20b fuel feeding in being arranged on input shaft 20 from housing 3, so needn't between for example input shaft 20 and Hydrauservo System 565, seal ring be set, just can be to the hydraulic chamber 565a of Hydrauservo System 565 fuel feeding.In addition, Hydrauservo System 562 is the hub portion 3c fuel feeding by being provided with from housing 3 extensions respectively, and by for example other parts, promptly can carry out fuel feeding by a pair of seal ring 580 is set respectively.Therefore, as long as a pair of seal ring 581,580 is set respectively in Hydrauservo System 565,562, just can fuel feeding, thus minimum is reduced in the sliding friction that seal ring causes, its result will improve automatic transmission 1 11Efficient.
In addition, because epicyclic reduction gear PR is the double pinion planetary pinion, thereby the rotation that can make input shaft 20 is as the rotation output of slowing down, even set good automatic transmission 1 simultaneously 11The gear ratio, what also need not increase planetary gear unit, epicyclic reduction gear respectively rotates key element, thereby can suppress high speed rotating, realizes automatic transmission 1 11Miniaturization.
In addition, rotate key element sun gear S1, fixed factors planetary carrier CR1, output rotation key element ring gear R1 because epicyclic reduction gear PR comprises input, thereby the rotation of input shaft 20 can be exported as the rotation of slowing down.
In addition, because planetary gear unit PU ties up Nao formula planetary pinion for drawing of being made up of sun gear S2, sun gear S3, planetary carrier CR2 and ring gear R2, so in 6 retainings of can realizing for example advancing, 1 retaining that falls back, can also make epicyclic reduction gear PR and planetary gear unit PU near configuration, thereby can shorten the transferring elements 740 that transmits the rotation of slowing down.
In addition, owing to have and dispose side by side with break B1 and at the overrunning clutch F3 of the rotation of a direction restrictions planetary gear frame CR2,1 retaining that advances when realizing for example just driving of clutch C1 and overrunning clutch F3 can be utilized, thereby 1 retaining that advances when travelling can be realized switching to reposefully from for example non-position of travelling.
In addition, because break B1 and overrunning clutch F3 are configured in the outer circumferential side of planetary gear unit PU, with for example the situation of overrunning clutch F3 adjacent with clutch C2 the rotation of a direction of limited wheel boss assembly 523 (particularly for) configuration is compared, can make the partly miniaturization in the axial direction that is provided with of clutch C1, C2, thereby make counter shaft gear 50 near the fluid torque converter sides.Like this, because the gear 51 of jack shaft 52 also can be near the fluid torque converter side, thereby can make jack shaft portion 4 miniaturization in the axial direction.
In addition, shown in the speed line chart, in realize advancing 6 retainings, 1 retaining that falls back, can make epicyclic reduction gear PR and planetary gear unit PU, transmit the transferring elements 740 that slows down and rotate thereby can shorten near configuration.Like this, can realize automatic transmission 1 11Miniaturization and light, simultaneously owing to can reduce inertial force, so can improve automatic transmission 1 11Controlled, reduce speed change and impact.
In addition, this automatic transmission 2 11, promptly 1 block to 4 retainings of 4 retainings that advance and to export the rotation of slowing down for direct-connected state at 5 retainings that advance, particularly on vehicle, carry automatic transmission 2 from above-mentioned advancing 11The time, can segment the speed change in the low-medium speed zone of vehicle.Like this,, can use the rotary speed area with optimum efficiency of driving source such as motor more, improve the Economy of fuel particularly in the low-medium speed zone of vehicle.In addition,, thereby 6 retainings that advance are driven for hypervelocity, thereby being hypervelocity and driving and compare, can reduce final deceleration with advance for direct-connected state makes 5 retainings and 6 retainings that advance of 4 retainings that advance because 5 retainings that advance are for direct-connected state.Like this, can reduce for example spider gear diameter of differential mechanism portion 5, shorten the axle base of the axle of input shaft 20 and differential mechanism portion 5, particularly carry when the FF vehicle, can realize automatic transmission 1 11Miniaturization.
In addition, as the driving wheel transfer mechanism, have to the differential mechanism portion 5 of driving wheel output rotation and the middle axial region 4 that combines with this differential mechanism portion 5, output block is the counter shaft gear that meshes with middle axial region 4, thereby can be with automatic transmission 1 11Lift-launch is on FF vehicle for example.
In addition, though in the 1st to the 11st mode of execution of the invention described above, the situation of equipping fluid torque converter in automatic transmission has been described, has been not limited thereto as an example, so long as when starting can transmitting torque (rotation) take-off device, can be any kind.In addition, adopting motor as the situation on the vehicle of driving source although understand lift-launch, but be not limited thereto, can certainly carry on motor vehicle driven by mixed power, driving source can be an any kind.In addition, above-mentioned automatic transmission is suitable for the FF vehicle, but is not limited thereto, and also can be used for the vehicle of other driving mode such as FR vehicle, 4 wd vehicles.
In addition, though in above-mentioned the 1st to the 11st mode of execution, illustrated that the structure of the rotation output mechanism that slows down is respectively 1 situation, but also be adapted in these all mode of executions, between input shaft and input rotation key element, clutch is set, between rotation key element and the 1st rotation key element clutch is set slowing down,, between input shaft and input are rotated, clutch is set and passes through freely fixing various situations such as fixed factors of break by the free fixing fixed factors of break.
In addition, though in for example the 5th mode of execution and the 6th mode of execution, illustrated with the input side of automatic transmission and the situation after the outlet side exchange, but be not limited thereto that the automatic transmission of other mode of executions also can exchange input side and outlet side.
(utilizability on the industry)
As mentioned above, automatic transmission of the present invention can be used in and carries at vehicles such as car, truck, buses, is particularly suitable for carrying in those lift-launchs from vehicle, requires miniaturization, light-dutyization and requires to alleviate the vehicle that speed change is impacted.

Claims (33)

1. automatic transmission,
Be provided with the input shaft that rotates according to the output of driving source,
Have the 1st, the 2nd, the 3rd and the 4th the rotation key element planetary gear unit,
The deceleration that deceleration after the rotational delay of described input shaft rotation freely is outputed to described the 1st rotation key element rotate output mechanism,
Be in the 1st clutch between the key element of described input shaft and described the 2nd rotation,
Be in the 2nd clutch between the key element of described input shaft and described the 3rd rotation,
With the output block that the described the 4th rotation of rotating key element is outputed to the driving wheel transfer mechanism,
It is characterized in that:
The axial side that output mechanism is configured in described planetary gear unit is rotated in described deceleration,
The the described the 1st and the 2nd clutch is configured in the axial opposite side of described planetary gear unit,
Described output block is configured between the described the 1st and the 2nd clutch and the planetary gear unit,
Described deceleration rotation output mechanism has epicyclic reduction gear,
Described epicyclic reduction gear, described planetary gear unit and described output block are set to the structure coaxial with described input shaft,
Described deceleration rotation output mechanism is made of the epicyclic reduction gear and the 3rd clutch between described input shaft and described input rotation key element of the output rotation key element that has the input rotation key element of the rotation of importing described input shaft, the fixing fixed factors that rotates and be connected with described the 1st rotation key element always always
By the combination of described the 3rd clutch, can export described deceleration rotation, the friction plate of described the 3rd clutch is configured in the outer circumferential side of described epicyclic reduction gear or with respect to described epicyclic reduction gear and an opposite side with described planetary gear unit.
2. automatic transmission as claimed in claim 1 is characterized in that:
Have the 1st break that the rotation of described fixed factors can be fixed,
Described the 3rd clutch can be exported described deceleration rotation by the combination of described the 1st break.
3. automatic transmission as claimed in claim 1 is characterized in that:
Described epicyclic reduction gear be configured in the Hydrauservo System of described the 3rd clutch and described planetary gear unit axially between.
4. automatic transmission as claimed in claim 1 is characterized in that:
Described the 1st clutch is connected with described the 2nd rotation key element by interior all sides of described output block,
Described the 2nd clutch is connected with described the 3rd rotation key element by the outer circumferential side of described the 1st clutch and interior all sides of described output block.
5. automatic transmission as claimed in claim 1 is characterized in that:
All sides and the friction plate that is connected described the 2nd parts spline combination of rotation on the key element in described the 1st clutch has, comprise Hydrauservo System and with the outer circumferential side spline of this friction plate in conjunction with and the 1st clutch drum that is connected with described input shaft, the 1st piston that presses this friction plate and pass through the close shape of liquid ground and seal between interior all sides of the 1st piston and the described input shaft and the 1st Hydrauservo System hydraulic chamber that forms between outer circumferential side and the 1st clutch drum;
The friction plate of all sides and described the 1st clutch drum spline combination in described the 2nd clutch has, comprise Hydrauservo System and with the outer circumferential side spline of this friction plate in conjunction with and the 2nd clutch drum that is connected with described the 3rd rotation key element, the 2nd piston that presses this friction plate and seal the 2nd Hydrauservo System hydraulic chamber that forms between interior all sides of the 2nd piston and outer circumferential side and the 2nd clutch drum by the close shape of liquid ground.
6. automatic transmission as claimed in claim 1 is characterized in that:
All sides and the friction plate that is connected described the 2nd parts spline combination of rotation on the key element in described the 1st clutch has, comprise Hydrauservo System and with the outer circumferential side spline of this friction plate in conjunction with and the 1st clutch drum that is connected with described input shaft, the 1st piston that presses this friction plate and pass through the close shape of liquid ground and seal between interior all sides of the 1st piston and the described input shaft and the 1st Hydrauservo System hydraulic chamber that forms between outer circumferential side and the 1st clutch drum
The friction plate that parts spline on described the 2nd clutch has interior all sides and is connected described the 3rd rotation key element combines, comprise Hydrauservo System and combine with the outer circumferential side spline of this friction plate, and be configured in the outer circumferential side of described the 1st clutch drum and the 2nd clutch drum that is connected with described input shaft, press the 2nd piston of this friction plate, and the 2nd Hydrauservo System hydraulic chamber that forms between the interior all sides by the close shape of liquid ground sealing the 2nd piston and outer circumferential side and the 2nd clutch drum.
7. automatic transmission as claimed in claim 1 is characterized in that:
Described the 1st clutch, described the 2nd clutch, described the 3rd clutch have Hydrauservo System respectively,
The Hydrauservo System of described the 2nd clutch is configured in from an end of the housing of automatic transmission extends on the 1st hub portion that is provided with, and is communicated with the oil circuit that is arranged on the 1st hub portion,
The Hydrauservo System of described the 1st clutch is configured in an end of described input shaft, and is communicated with the oil circuit of an end of described the 1st hub portion or described housing by the oil circuit that is arranged in the described input shaft,
The Hydrauservo System of described the 3rd clutch is configured in from the other end of the 2nd hub portion of the other end extension setting of described housing or described input shaft, is communicated with the oil circuit that is arranged on described the 2nd hub portion.
8. automatic transmission as claimed in claim 1 is characterized in that:
Described the 1st clutch, described the 2nd clutch, described the 3rd clutch have Hydrauservo System respectively,
The Hydrauservo System of described the 2nd clutch is configured in from an end of the housing of automatic transmission extends on the 1st hub portion that is provided with, and is communicated with the oil circuit that is arranged on the 1st hub portion,
The Hydrauservo System of described the 1st clutch is configured in an end of described input shaft, and is communicated with the oil circuit of an end of described the 1st hub portion or described housing by the oil circuit that is arranged in the described input shaft,
The Hydrauservo System of described the 3rd clutch is configured on the other end of described input shaft, is communicated with oil circuit in being arranged on described input shaft.
9. automatic transmission as claimed in claim 1 is characterized in that:
The friction plate that all sides combined with parts spline on described input rotation key element that is connected described epicyclic reduction gear or the described output rotation key element in described the 3rd clutch had, comprise Hydrauservo System and the 3rd clutch drum that combines with the outer circumferential side spline of this friction plate, press the 3rd piston of this friction plate, seal the 1st Hydrauservo System hydraulic chamber that forms between interior all sides of the 3rd piston and outer circumferential side and the 3rd clutch drum by the close shape of liquid ground.
10. automatic transmission as claimed in claim 1 is characterized in that:
Described epicyclic reduction gear is the double pinion planetary pinion.
11. automatic transmission as claimed in claim 10 is characterized in that:
Described epicyclic reduction gear is included as the 1st planetary carrier of described input rotation key element, rotates the 1st ring gear of key element for the 1st sun gear of described fixed factors, for described output.
12. automatic transmission as claimed in claim 10 is characterized in that:
Described epicyclic reduction gear is included as the 1st sun gear of described input rotation key element, rotates the 1st ring gear of key element for the 1st planetary carrier of described fixed factors, for described output.
13. automatic transmission as claimed in claim 1 is characterized in that:
Described planetary gear unit is tieed up Nao formula planetary pinion for drawing of being made up of the 2nd sun gear, the 3rd sun gear, the 2nd planetary carrier and the 2nd ring gear,
Described the 1st rotation key element for the output rotation of importing described deceleration rotation output mechanism, and fix freely described the 2nd sun gear by the locking of the 2nd break,
Described the 2nd rotation key element is described the 3rd sun gear in conjunction with the rotation of importing described input shaft by described the 1st clutch,
Described the 3rd rotation key element is to have with the long small gear of described the 2nd sun gear engagement with the short and small gear of described the 3rd sun gear engagement, fix freely and described the 2nd planetary carrier that combines the rotation of importing described input shaft by described the 2nd clutch by the locking of the 3rd break
Described the 4th rotation key element is described the 2nd ring gear with described long pinion.
14. automatic transmission as claimed in claim 13 is characterized in that:
Has the 1st overrunning clutch that disposes and limit the rotation of described the 2nd planetary carrier with described the 3rd break side by side in a direction.
15. automatic transmission as claimed in claim 14 is characterized in that:
Described the 3rd break is configured in the outer circumferential side of described planetary gear unit, described the 1st overrunning clutch and described the 2nd clutch disposed adjacent.
16. automatic transmission as claimed in claim 14 is characterized in that:
Described the 3rd break and described the 1st overrunning clutch are configured in the outer circumferential side of described planetary gear unit.
17., it is characterized in that as any described automatic transmission in the claim 13～16:
Have with described the 2nd break dispose side by side, the 2nd overrunning clutch that a direction limits the rotation of described the 2nd sun gear that is locked in by the 4th break.
18. automatic transmission as claimed in claim 17 is characterized in that:
Have between described deceleration rotation output mechanism and described the 2nd sun gear and be connected the output rotation of described deceleration rotation output mechanism and the housing part of the rotation of described the 2nd sun gear,
The inner ring of described the 2nd overrunning clutch and described housing part are integrally formed.
19., it is characterized in that as any described automatic transmission in the claim 13～16:
Represent in rotating speed separately, transverse axis the speed line chart of described the 1st, the 2nd, the 3rd and the 4th rotation key element at the longitudinal axis corresponding to the gear ratio of described the 1st, the 2nd, the 3rd and the 4th rotation key element,
Import the longitudinal axis of described the 1st rotation key element of described deceleration rotation, corresponding successively described the 3rd rotation key element of other longitudinal axis, described the 4th rotation key element that is connected with described output block, described the 2nd rotation key element corresponding to laterally end.
20., it is characterized in that as any described automatic transmission in the claim 13～16:
Respectively by described the 1st clutch and described the 3rd break in conjunction with realizing 1 retaining that advances,
By described the 1st clutch and described the 2nd break in conjunction with realizing 2 retainings that advance,
Combination by described the 1st clutch and can be from the state of described deceleration rotation output mechanism output deceleration rotation 3 retainings of realizing advancing,
By described the 1st clutch and described the 2nd clutch in conjunction with realizing 4 retainings that advance,
Combination by described the 2nd clutch and can be from the state of described deceleration rotation output mechanism output deceleration rotation 5 retainings of realizing advancing,
By described the 2nd clutch and described the 2nd break in conjunction with realizing 6 retainings that advance,
The combination and 1 retaining that can fall back from the state realization of described deceleration rotation output mechanism output deceleration rotation by described the 3rd clutch.
21. automatic transmission as claimed in claim 10 is characterized in that:
Described planetary gear unit serve as reasons have the 2nd sun gear, the 1st simple planetary arrangement of the 2nd planetary carrier, the 2nd ring gear and the 2nd simple planetary arrangement with the 3rd sun gear, the 3rd planetary carrier, the 3rd ring gear form,
Described the 1st rotation key element is for importing the planetary output of described double pinion rotation, and fix freely described the 3rd ring gear by the locking of the 2nd break,
Described the 2nd rotation key element is for the locking by the 3rd break fix freely, and described the 3rd planetary carrier and described the 2nd ring gear in conjunction with the rotation of importing described input shaft by the 1st clutch,
Described the 3rd rotation key element is described the 2nd sun gear and described the 3rd sun gear in conjunction with the rotation of importing described input shaft by described the 2nd clutch,
Described the 4th rotation key element is described the 2nd planetary carrier that meshes with described the 2nd sun gear and described the 2nd ring gear.
22. automatic transmission as claimed in claim 21 is characterized in that:
Has the 1st overrunning clutch that disposes and limit the rotation of described the 3rd planetary carrier and described the 2nd ring gear with described the 3rd break side by side in a direction.
23. automatic transmission as claimed in claim 22 is characterized in that:
Described the 3rd break and described the 1st overrunning clutch are configured in the outer circumferential side of described planetary gear unit.
24. automatic transmission as claimed in claim 23 is characterized in that:
The inner ring of described the 1st overrunning clutch and described the 2nd ring gear are integrally formed.
25., it is characterized in that as any described automatic transmission in the claim 21～24:
Have and dispose side by side with described the 2nd break and the 2nd overrunning clutch that a direction limits the rotation of described the 3rd planetary carrier that is locked in by the 4th break.
26., it is characterized in that as any described automatic transmission in the claim 21～24:
Represent in rotating speed separately, transverse axis the speed line chart of described the 1st, the 2nd, the 3rd and the 4th rotation key element at the longitudinal axis corresponding to the gear ratio of described the 1st, the 2nd, the 3rd and the 4th rotation key element,
Import the longitudinal axis of described the 1st rotation key element of described deceleration rotation, corresponding successively described the 3rd rotation key element of other longitudinal axis, described the 4th rotation key element that is connected with described output block, described the 2nd rotation key element corresponding to laterally end.
27., it is characterized in that as any described automatic transmission in the claim 21～24:
Respectively by described the 2nd clutch and described the 3rd break in conjunction with realizing 1 retaining that advances,
By described the 2nd clutch and described the 2nd break in conjunction with realizing 2 retainings that advance,
Combination by described the 2nd clutch and can be from the state of described deceleration rotation output mechanism output deceleration rotation 3 retainings of realizing advancing,
By described the 1st clutch and described the 2nd clutch in conjunction with realizing 4 retainings that advance,
Combination by described the 1st clutch and can be from the state of described deceleration rotation output mechanism output deceleration rotation 5 retainings of realizing advancing,
By described the 1st clutch and described the 2nd break in conjunction with realizing 6 retainings that advance,
The combination and 1 retaining that can fall back from the state realization of described deceleration rotation output mechanism output deceleration rotation by described the 3rd clutch.
28. automatic transmission as claimed in claim 1 is characterized in that:
Described planetary gear unit serve as reasons have the 2nd sun gear, the 3rd sun gear, the 2nd planetary carrier and the 2nd ring gear are formed draws dimension Nao formula planetary pinion,
Described the 3rd sun gear that described the 1st rotation key element is rotated for the output that can import described deceleration rotation output mechanism,
Described the 2nd rotation key element be have with the long small gear of described the 2nd sun gear engagement and with the short and small gear of described the 3rd sun gear engagement, by the locking of the 2nd break fix freely, described the 2nd planetary carrier that combines the rotation of importing described input shaft by the 1st clutch also
Described the 3rd rotation key element for the rotation by described the 2nd clutch in conjunction with the described input shaft of input, and the locking of passing through the 3rd break fix freely the 2nd sun gear,
Described the 4th rotation key element is described the 2nd ring gear with described long pinion.
29. automatic transmission as claimed in claim 28 is characterized in that:
Has the 1st overrunning clutch that disposes and limit the rotation of described the 2nd planetary carrier with described the 2nd break side by side in a direction.
30. automatic transmission as claimed in claim 29 is characterized in that:
Described the 2nd break and described the 1st overrunning clutch are configured in the outer circumferential side of described planetary gear unit.
31., it is characterized in that as any described automatic transmission in the claim 28～30:
Represent in rotating speed separately, transverse axis the speed line chart of described the 1st, the 2nd, the 3rd and the 4th rotation key element at the longitudinal axis corresponding to the gear ratio of described the 1st, the 2nd, the 3rd and the 4th rotation key element,
Import the longitudinal axis of described the 1st rotation key element of described deceleration rotation, corresponding successively described the 4th rotation key element that is connected with described output block of other longitudinal axis, described the 2nd rotation key element, described the 3rd rotation key element corresponding to laterally end.
32., it is characterized in that as any described automatic transmission in the claim 28～30:
Combination by described the 2nd break and can be respectively from the state of described deceleration rotation output mechanism output deceleration rotation 1 retaining of realizing advancing,
Combination by described the 3rd break and can be from the state of described deceleration rotation output mechanism output deceleration rotation 2 retainings of realizing advancing,
Combination by described the 2nd clutch and can be from the state of described deceleration rotation output mechanism output deceleration rotation 3 retainings of realizing advancing,
Combination by described the 1st clutch and can be from the state of described deceleration rotation output mechanism output deceleration rotation 4 retainings of realizing advancing,
By described the 1st clutch and described the 2nd clutch in conjunction with realizing 5 retainings that advance,
By described the 1st clutch and described the 3rd break in conjunction with realizing 6 retainings that advance,
By described the 2nd clutch and described the 2nd break in conjunction with realizing 1 retaining that falls back.
33. automatic transmission as claimed in claim 1 is characterized in that:
Described driving wheel transfer mechanism has to the differential mechanism portion of driving wheel output rotation and the middle axial region that combines with this differential mechanism portion,
Described output block is the counter shaft gear that meshes with described middle axial region.
CN 200710161113 2002-03-29 2003-03-31 Automatic transmission Expired - Fee Related CN101216093B (en)

Applications Claiming Priority (9)

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JP2002098020 2002-03-29
JP2002098020 2002-03-29
JP2002-098020 2002-03-29
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JP2002-204894 2002-07-12
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JP2002-382147 2002-12-27

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US8419586B2 (en) * 2009-05-22 2013-04-16 Honda Motor Co., Ltd. Automatic transmission
DE112013000950T5 (en) * 2012-03-26 2014-12-11 Aisin Aw Co., Ltd. automatic transmission device
US8931611B2 (en) * 2012-10-24 2015-01-13 Ford Global Technologies, Llc Connected assembly of two shafts and a clutch housing
EP2980450A4 (en) * 2013-03-26 2016-11-23 Jatco Ltd Automatic transmission for vehicles
JP6380352B2 (en) * 2015-11-26 2018-08-29 トヨタ自動車株式会社 Automatic transmission for vehicles

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