WO2016104063A1 - クラッチおよびそれを備えた変速装置 - Google Patents
クラッチおよびそれを備えた変速装置 Download PDFInfo
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- WO2016104063A1 WO2016104063A1 PCT/JP2015/083666 JP2015083666W WO2016104063A1 WO 2016104063 A1 WO2016104063 A1 WO 2016104063A1 JP 2015083666 W JP2015083666 W JP 2015083666W WO 2016104063 A1 WO2016104063 A1 WO 2016104063A1
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- WIPO (PCT)
- Prior art keywords
- clutch
- planetary gear
- gear
- hub
- shaft
- Prior art date
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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
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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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D1/00—Couplings for rigidly connecting two coaxial shafts or other movable machine elements
- F16D1/10—Quick-acting couplings in which the parts are connected by simply bringing them together axially
- F16D1/101—Quick-acting couplings in which the parts are connected by simply bringing them together axially without axial retaining means rotating with the coupling
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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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D13/00—Friction clutches
- F16D13/58—Details
- F16D13/60—Clutching elements
- F16D13/64—Clutch-plates; Clutch-lamellae
- F16D13/644—Hub construction
- F16D13/646—Mounting of the discs on the hub
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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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D13/00—Friction clutches
- F16D13/76—Friction clutches specially adapted to incorporate with other transmission parts, i.e. at least one of the clutch parts also having another function, e.g. being the disc of a pulley
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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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D21/00—Systems comprising a plurality of actuated clutches
- F16D21/02—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways
- F16D21/06—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways at least two driving shafts or two driven shafts being concentric
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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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D25/00—Fluid-actuated clutches
- F16D25/06—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch
- F16D25/062—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces
- F16D25/063—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially
- F16D25/0635—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially with flat friction surfaces, e.g. discs
- F16D25/0638—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially with flat friction surfaces, e.g. discs with more than two discs, e.g. multiple lamellae
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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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D25/00—Fluid-actuated clutches
- F16D25/10—Clutch systems with a plurality of fluid-actuated clutches
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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
- F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
- F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
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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
- F16H57/00—General details of gearing
- F16H57/08—General details of gearing of gearings with members having orbital motion
- F16H57/10—Braking arrangements
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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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D13/00—Friction clutches
- F16D13/58—Details
- F16D13/74—Features relating to lubrication
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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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D1/00—Couplings for rigidly connecting two coaxial shafts or other movable machine elements
- F16D1/10—Quick-acting couplings in which the parts are connected by simply bringing them together axially
- F16D2001/103—Quick-acting couplings in which the parts are connected by simply bringing them together axially the torque is transmitted via splined connections
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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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D21/00—Systems comprising a plurality of actuated clutches
- F16D21/02—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways
- F16D21/06—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways at least two driving shafts or two driven shafts being concentric
- F16D2021/0661—Hydraulically actuated multiple lamellae clutches
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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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D25/00—Fluid-actuated clutches
- F16D25/12—Details not specific to one of the before-mentioned types
- F16D25/123—Details not specific to one of the before-mentioned types in view of cooling and lubrication
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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
- F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
- F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
- F16H2045/0221—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means
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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
- F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
- F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
- F16H2045/0273—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type characterised by the type of the friction surface of the lock-up clutch
- F16H2045/0284—Multiple disk type lock-up clutch
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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
- F16H57/00—General details of gearing
- F16H57/08—General details of gearing of gearings with members having orbital motion
- F16H2057/087—Arrangement and support of friction devices in planetary gearings, e.g. support of clutch drums, stacked arrangements of friction devices
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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
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
- F16H2200/0069—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising ten forward speeds
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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
- 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
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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
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
- F16H2200/2012—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with four sets of orbital gears
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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
- 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
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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
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
- F16H2200/2046—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with six engaging means
Definitions
- the present disclosure relates to a clutch including a friction plate, a separator plate, a clutch hub, and a piston, and a transmission including the clutch.
- this type of clutch includes a clutch hub having a tubular portion into which inner peripheral portions of a plurality of separator plates are fitted and an annular connecting portion extending radially inward from the tubular portion. It is known (see, for example, Patent Document 1).
- the inner peripheral portion of the coupling portion of the clutch hub is always connected (fixed) via a spline to a shaft portion extending in the axial direction from the sun gear of the planetary gear constituting the transmission.
- An oil chamber defining member that defines an engagement oil chamber together with the piston is fixed to the shaft portion of the sun gear using a snap ring.
- the piston is supported by the shaft portion so as to rotate integrally with the shaft portion of the sun gear and be movable in the axial direction, and has a centrifugal oil pressure cancel chamber for canceling the centrifugal oil pressure generated in the engagement oil chamber.
- the sun gear which is an element to be connected to the clutch, rotates at a relatively high speed during operation of the transmission, and rotates all the oil chambers of the clutch, that is, the engagement oil chamber and the centrifugal oil pressure cancel chamber, together with the sun gear.
- the main object of the present disclosure is to ensure good processing accuracy and support accuracy of a gear including a clutch hub that rotates integrally with the planetary gear.
- the clutch according to the present disclosure includes a friction plate, a separator plate, a clutch hub, and a piston that presses the friction plate and the separator plate.
- the clutch hub includes an inner periphery of the friction plate or the separator plate.
- the hub portion is spline-fitted so as to rotate integrally with the gear of the planetary gear, and the shaft portion is rotatably supported by a central axis and is in-fitted to the gear. It is.
- the clutch hub of this clutch defines a hub portion to which a friction plate or a separator plate is fitted, a cylindrical shaft portion that movably supports the piston, and an engagement oil chamber to which engagement hydraulic pressure is supplied together with the piston. And an engaging oil chamber defining part.
- the hub portion is spline-fitted so as to rotate integrally with the planetary gear, and the shaft portion is rotatably supported by the central axis and is inlay-fitted to the gear.
- the gear can be accurately supported (aligned) by the shaft portion.
- the clutch including the clutch hub that rotates integrally with the gear of the planetary gear it is possible to ensure good processing accuracy and support accuracy of the gear.
- FIG. 2 is an operation table showing the relationship between each gear position and the operation states of clutches and brakes in the transmission of FIG. 1.
- FIG. 2 is a velocity diagram showing a ratio of a rotational speed of each rotary element to an input rotational speed in the transmission of FIG.
- FIG. 2 is a principal part expanded sectional view which shows the transmission of FIG.
- FIG. 2 is a principal part expanded sectional view which shows the transmission of FIG.
- It is a principal part expanded sectional view which shows the transmission of FIG.
- It is a perspective view which shows the hub member of the clutch hub contained in the transmission of FIG.
- It is a front view which shows the hub member of the clutch hub contained in the transmission of FIG.
- It is a rear view which shows the hub member of the clutch hub contained in the transmission of FIG.
- It is a principal part expanded sectional view which shows the other transmission of this indication.
- FIG. 1 is a schematic configuration diagram of a power transmission device 10 including an automatic transmission 20 as a transmission device according to an embodiment of the present disclosure.
- a power transmission device 10 shown in the figure is connected to a crankshaft of an engine (internal combustion engine) (not shown) and / or a rotor of an electric motor as a drive source mounted vertically in a front portion of a rear wheel drive vehicle. Power (torque) from an engine or the like can be transmitted to left and right rear wheels (drive wheels) (not shown).
- the power transmission device 10 includes a transmission case in addition to the automatic transmission 20 that shifts the power transmitted from the engine or the like to the input shaft (input member) 20i and transmits it to the output shaft (output member) 20o.
- (Stationary member) 11, starting device (fluid transmission device) 12, oil pump 17 and the like are included.
- the starting device 12 includes a front cover 13 connected to a crankshaft of an engine and / or a rotor of an electric motor via a drive plate or the like (not shown), and an input side having a pump shell closely fixed to the front cover 13.
- the pump impeller 14p, the output-side turbine runner 14t connected to the input shaft 20i of the automatic transmission 20, the pump impeller 14p, and the turbine runner 14t are disposed inside the turbine runner 14t to the pump impeller 14p.
- the torque converter includes a stator 14s for commutation, a one-way clutch 14o that is supported by a stator shaft (not shown) and restricts the rotation direction of the stator 14s in one direction.
- the starting device 12 connects the front cover 13 connected to the crankshaft of the engine and the like and the input shaft 20i of the automatic transmission 20 to each other, and releases the connection between the lockup clutch 15 and the front cover 13. And a damper mechanism 16 that attenuates vibration between the input shaft 20 i of the automatic transmission 20.
- the lockup clutch 15 is configured as a multi-plate friction type hydraulic clutch having a plurality of friction engagement plates (friction plates and separator plates).
- the lockup clutch 15 may be a single plate friction type hydraulic clutch.
- the starting device 12 may include a fluid coupling that does not include the stator 14s.
- the oil pump 17 includes a pump assembly including a pump body and a pump cover, an external gear (inner rotor) connected to the pump impeller 14p of the starting device 12 via a chain or a gear train, and an internal gear meshing with the external gear. It is configured as a gear pump having a tooth gear (outer rotor) or the like.
- the oil pump 17 is driven by power from the engine, sucks hydraulic oil (ATF) stored in an oil pan (not shown), and pumps it to a hydraulic control device (not shown).
- ATF hydraulic oil
- the automatic transmission 20 is configured as a 10-speed transmission, and as shown in FIG. 1, an output shaft connected to the left and right rear wheels via an input shaft 20i, a differential gear (not shown), and a drive shaft.
- a single pinion type first planetary gear 21 and a second planetary gear 22 arranged in the axial direction of the automatic transmission 20 (input shaft 20i and output shaft 20o), a double pinion type planetary gear and a single And a Ravigneaux type planetary gear mechanism 25 as a compound planetary gear train configured by combining with a pinion type planetary gear.
- the automatic transmission 20 includes a clutch C1 (first clutch) as a first engagement element and a clutch C2 (second clutch) as a second engagement element for changing the power transmission path from the input shaft 20i to the output shaft 20o.
- a second clutch), a clutch C3 (third clutch) as a third engagement element, a clutch C4 (fourth clutch) as a fourth engagement element, a brake B1 (first brake) as a fifth engagement element, and A brake B2 (second brake) as a sixth engagement element is included.
- the first and second planetary gears 21 and 22 and the Ravigneaux planetary gear mechanism 25 are connected to the Ravigneaux planetary gear mechanism 25 and the second planetary gear 22 from the starting device 12, that is, the engine side (left side in FIG. 1).
- the Ravigneaux type planetary gear mechanism 25 is arrange
- the first planetary gear 21 is disposed on the rear side of the vehicle so as to be close to the output shaft 20o. Further, the second planetary gear 22 is disposed between the Ravigneaux type planetary gear mechanism 25 and the first planetary gear 21 in the axial direction of the input shaft 20 i, the output shaft 20 o and the like.
- the first planetary gear 21 includes a first sun gear 21s that is an external gear, a first ring gear 21r that is an internal gear disposed concentrically with the first sun gear 21s, and a first sun gear 21s and a first ring gear 21r, respectively. And a first carrier 21c that holds the plurality of first pinion gears 21p so as to freely rotate (rotate) and revolve.
- the first carrier 21c of the first planetary gear 21 is always connected (fixed) to the intermediate shaft (intermediate shaft) 20m of the automatic transmission 20 connected to the input shaft 20i.
- the first carrier 21c functions as an input element of the first planetary gear 21 when the clutch C4 is engaged, and idles when the clutch C4 is released.
- the first ring gear 21r functions as an output element of the first planetary gear 21 when the clutch C4 is engaged.
- the second planetary gear 22 includes a second sun gear 22s that is an external gear, a second ring gear 22r that is an internal gear disposed concentrically with the second sun gear 22s, and a second sun gear 22s and a second ring gear 22r, respectively. And a second carrier (planetary carrier) 22c that holds the plurality of second pinion gears 22p so that they can rotate (rotate) and revolve freely.
- the second sun gear 22s of the second planetary gear 22 is integrated (always connected) with the first sun gear 21s of the first planetary gear 21, and is always integrated with the first sun gear 21s (and Rotate or stop on the same axis.
- the first sun gear 21s and the second sun gear 22s may be configured separately and always connected via a connecting member (first connecting member) (not shown).
- the second carrier 22c of the second planetary gear 22 is always connected to the output shaft 20o, and always rotates or stops integrally (and coaxially) with the output shaft 20o.
- the second carrier 22 c functions as an output element of the second planetary gear 22.
- the second ring gear 22 r of the second planetary gear 22 functions as a fixable element of the second planetary gear 22.
- the Ravigneaux type planetary gear mechanism 25 includes a third sun gear 23s and a fourth sun gear 24s that are external gears, a third ring gear 23r that is an internal gear disposed concentrically with the third sun gear 23s, and a third sun gear 23s.
- the third pinion gear 23p and the plurality of fourth pinion gears 24p are rotatable (rotatable) and revolved to hold the third carrier 23c.
- Such Ravigneaux type planetary gear mechanism 25 is a compound planetary gear train configured by combining a double pinion type planetary gear (third planetary gear) and a single pinion type planetary gear (fourth planetary gear). That is, the third sun gear 23s, the third carrier 23c, the third and fourth pinion gears 23p and 24p, and the third ring gear 23r of the Ravigneaux planetary gear mechanism 25 constitute a double pinion type third planetary gear. Further, the fourth sun gear 24s, the third carrier 23c, the fourth pinion gear 24p, and the third ring gear 23r of the Ravigneaux type planetary gear mechanism 25 constitute a single pinion type fourth planetary gear.
- the fourth sun gear 24s is an element that can be fixed to the Ravigneaux type planetary gear mechanism 25 (the second fixing of the automatic transmission 20). Function as a possible element).
- the third carrier 23 c is always connected (fixed) to the input shaft 20 i, and the first planetary gear 21 is connected via an intermediate shaft 20 m as a connecting member (second connecting member). Always connected to the first carrier 21c.
- the third carrier 23 c functions as an input element of the Ravigneaux planetary gear mechanism 25.
- the third ring gear 23r functions as a first output element of the Ravigneaux planetary gear mechanism 25, and the third sun gear 23s functions as a second output element of the Ravigneaux planetary gear mechanism 25.
- the clutch C1 mutually connects the first sun gear 21s of the first planetary gear 21 and the second sun gear 22s of the second planetary gear 22 and the third ring gear 23r, which is the first output element of the Ravigneaux type planetary gear mechanism 25, to each other. It connects and cancels both connections.
- the clutch C2 mutually connects the first sun gear 21s of the first planetary gear 21 and the second sun gear 22s of the second planetary gear 22 and the third sun gear 23s, which is the second output element of the Ravigneaux type planetary gear mechanism 25, to each other. It connects and cancels both connections.
- the clutch C3 connects and disconnects the second ring gear 22r of the second planetary gear 22 and the third ring gear 23r, which is the first output element of the Ravigneaux type planetary gear mechanism 25, to each other.
- the clutch C4 connects the first ring gear 21r, which is the output element of the first planetary gear 21, and the output shaft 20o to each other and releases the connection between them.
- the brake B1 fixes (connects) the fourth sun gear 24s, which can be fixed to the Ravigneaux type planetary gear mechanism 25, to the transmission case 11 as a stationary member in a non-rotatable manner, and the fourth sun gear 24s to the transmission case 11. In contrast, it is free to rotate.
- the brake B2 fixes (connects) the second ring gear 22r, which is a fixable element of the second planetary gear 22, to the transmission case 11 so as not to rotate, and the second ring gear 22r to the transmission case 11 as a stationary member. And free to rotate.
- a hydraulic servo including a piston, a plurality of friction engagement plates (friction plates and separator plates), an engagement oil chamber to which hydraulic oil is supplied, a centrifugal hydraulic pressure cancellation chamber, and the like.
- a multi-plate friction type hydraulic clutch (friction engagement element) having the above is adopted.
- the brakes B1 and B2 a multi-plate friction hydraulic brake having a hydraulic servo including a piston, a plurality of friction engagement plates (friction plates and separator plates), an engagement oil chamber to which hydraulic oil is supplied, and the like. Is adopted.
- the clutches C1 to C4 and the brakes B1 and B2 operate when hydraulic oil is supplied and discharged by the hydraulic control device.
- FIG. 2 shows an operation table showing the relationship between the respective speeds of the automatic transmission 20 and the operating states of the clutches C1 to C4 and the brakes B1 and B2.
- FIG. 3 shows the rotational speed of the input shaft 20i in the automatic transmission 20 ( The speed diagram which shows the ratio of the rotational speed of each rotation element with respect to (input rotational speed) is shown.
- the automatic transmission 20 provides the forward speed and the reverse speed from the first speed to the tenth speed by setting the clutches C1 to C4 and the brakes B1 and B2 to the states shown in the operation table of FIG.
- first and second planetary gears 21 and 22 and the ten rotating elements of the Ravigneaux type planetary gear mechanism 25 are arranged in the order shown in the figure from the left side in FIG. 3 at intervals according to these gear ratios ⁇ 1, ⁇ 2, ⁇ 3, and ⁇ 4.
- the first sun gear 21s is the first rotating element of the automatic transmission 20
- the first carrier 21c is the second rotating element of the automatic transmission 20
- the first ring gear 21r is the third rotating element of the automatic transmission 20.
- the second sun gear 22s is the fourth rotating element of the automatic transmission 20
- the second carrier 22c is the fifth rotating element of the automatic transmission 20
- the second ring gear 22r is the fourth rotating element of the automatic transmission 20.
- the fourth sun gear 24s is the seventh rotating element of the automatic transmission 20
- the third carrier 23c is the eighth rotating element of the automatic transmission 20
- the third ring gear 23r is the ninth rotating element of the automatic transmission 20.
- the third sun gear 23 s is the tenth rotating element of the automatic transmission 20.
- the gear ratios ⁇ 1 to ⁇ 4 of the first and second planetary gears 21 and 22 and the third and fourth planetary gears are not limited to those described above.
- at least one of the clutches C1 to C4 and the brakes B1 and B2 may be a meshing engagement element such as a dog clutch or a dog brake.
- a dog brake is employed as the brake B2 that is continuously engaged when the first forward speed is established to the fourth forward speed and is engaged when the reverse speed is formed. Good.
- At least one of the first and second planetary gears 21 and 22 may be a double pinion type planetary gear
- the Ravigneaux type planetary gear mechanism 25 is, for example, a Simpson type or CR- It may be replaced with a compound planetary gear train such as a CR type.
- the automatic transmission 20 described above may be modified to a transmission mounted on a front wheel drive vehicle.
- FIG. 4 and 5 are enlarged cross-sectional views showing the main part of the automatic transmission 20.
- FIG. These drawings show the configuration around the clutches C1 and C2 included in the automatic transmission 20.
- the clutch C ⁇ b> 1 is disposed between the second planetary gear 22 and the Ravigneaux planetary gear mechanism 25 so as to be close to the second planetary gear 22.
- the clutch C2 is surrounded at least in part by the constituent members of the clutch C1 and is connected to the Ravigneaux planetary gear mechanism 25 so as to be close to the Ravigneaux planetary gear mechanism 25 (third planetary gear). Arranged between.
- the clutches C1 and C2 use the first sun gear 21s of the first planetary gear 21 and the second sun gear 22s of the second planetary gear 22 as common connection target elements. Therefore, as shown in FIGS. 4 and 5, the clutches C1 and C2 are always connected (fixed) to the first sun gear 21s and the second sun gear 22s of the second planetary gear 22, and the clutch hub and clutch of the clutch C1.
- the drum member 120 that functions as a C2 clutch drum is shared.
- the clutch C1 uses the third ring gear 23r of the Ravigneaux type planetary gear mechanism 25 as a common connection target element as in the clutch C3. Therefore, the clutches C1 and C3 are always connected (fixed) to the third ring gear 23r and share the drum member 130 that functions as the clutch drum of the clutch C1 and the clutch hub of the clutch C3.
- the drum member 120 includes a cylindrical portion 121 shared by the clutches C ⁇ b> 1 and C ⁇ b> 2 and an annular portion 122 extending radially inward from the inner peripheral surface of the cylindrical portion 121.
- a spline 121a is formed on the outer peripheral surface of the half of the cylindrical portion 121 on the second planetary gear 22 side (the right side in FIGS. 3 and 4), and the Ravigneaux planetary gear mechanism 25 side of the cylindrical portion 121 (
- a spline 121b is formed on the inner peripheral surface of the half portion on the left side in FIGS.
- the inner peripheral portion of the annular portion 122 is welded to the connecting member 125, and the drum member 120 is connected to the first sun gear of the first planetary gear 21 that is an element to be connected to the clutches C ⁇ b> 1 and C ⁇ b> 2 via the connecting member 125. 21s and the second sun gear 22s of the second planetary gear 22 are always connected (fixed).
- the drum member 130 includes a drum part 131 used by the clutch C1, an annular wall part 132 extending radially inward from the drum part 131, a hub part (not shown) used by the clutch C3, and a cylindrical support. Part 135.
- the drum part 131, the annular wall part 132, the hub part, and the support part 135 are integrally formed by casting, for example, an aluminum alloy or the like.
- the drum portion 131 has an opening-side end portion (left end portion in FIGS. 4 and 5) that is always connected (fixed) to the third ring gear 23r of the Ravigneaux planetary gear mechanism 25 that is an element to be connected to the clutches C1 and C3. .
- a spline 131a see FIG.
- the hub portion of the drum member 130 extends from the annular wall portion 132 to the side opposite to the opening side end portion of the drum portion 131 (the right side in FIGS. 4 and 5), and is smaller than the drum portion 131 in the present embodiment. It is formed in a cylindrical shape having an outer diameter. Further, splines are formed on the outer peripheral surface of the hub portion, and the inner peripheral surface of the hub portion is formed in a concave cylindrical surface shape having no irregularities. Thereby, the strength of the hub portion can be ensured without increasing the thickness.
- the support portion 135 extends in the axial direction from the inner peripheral portion of the annular wall portion 132 toward the second planetary gear 22 and the Ravigneaux planetary gear mechanism 25, and is connected to the above-described connection via a bush or a radial bearing.
- the member 125 is rotatably supported by the outer peripheral surface.
- the clutch C ⁇ b> 1 including the drum members 120 and 130 is a plurality of friction plates (friction engagement plates) 101 and a plurality of friction plates 101 arranged alternately. Separator plate (friction engagement plate) 102 and backing plate, piston 140 that frictionally engages friction plate 101 and separator plate 102, and piston 140 that is spaced from friction plate 101 and separator plate 102.
- a plurality of return springs (coil springs) SP1 and an annular cancel plate (cancellation chamber defining member) 170 are included.
- the plurality of friction plates 101 (respective inner peripheral portions) of the clutch C1 are fitted to the splines 121a of the cylindrical portion 121 of the drum member 120 surrounded by the drum portion 131 of the drum member 130. Accordingly, the plurality of friction plates 101 are supported by the drum member 120 that functions as a clutch hub so as to rotate integrally with the cylindrical portion 121 and to be movable in the axial direction. Further, the plurality of separator plates 102 (the respective outer peripheral portions) of the clutch C1 are fitted into splines 131a formed on the inner peripheral surface of the drum portion 131 of the drum member 130. Accordingly, the plurality of separator plates 102 are supported by the drum member 130 that functions as a clutch drum so as to rotate integrally with the drum portion 131 and be movable in the axial direction.
- the piston 140 is disposed between the annular wall portion 132 of the drum member 130 and the cylindrical portion 121 of the drum member 120 in the axial direction, and rotates in unison with the drum member 130 and is movable in the axial direction. It is supported by the support part 135 of the drum member 130. As shown in FIGS. 4 and 5, the piston 140, together with the annular wall portion 132 and the support portion 135 of the drum member 130, defines an engagement oil chamber (first engagement oil chamber) 150 of the clutch C ⁇ b> 1.
- the cancel plate 170 is disposed between the piston 140 and the annular portion 122 of the drum member 120 in the axial direction, that is, on the opposite side of the piston 140 from the annular wall portion 132 of the drum member 130, and uses a snap ring.
- the cancel plate 170 together with the piston 140 and the support portion 135, cancels the centrifugal hydraulic pressure generated in the engagement oil chamber 150 (first centrifugal hydraulic pressure cancellation chamber). 190 is defined.
- the engagement oil chamber 150 and the centrifugal hydraulic pressure cancellation chamber 190 of the clutch C1 are rotated together with the third ring gear 23r (first output element) of the Ravigneaux planetary gear mechanism 25, the piston 140, and the cancel plate. 170.
- the engagement oil chamber 150 of the clutch C1 is engaged with the clutch C1 regulated by the hydraulic control device through an oil passage formed in the input shaft 20i, the connecting member 125, the support portion 135 of the drum member 130, and the like. Hydraulic pressure (hydraulic oil) is supplied.
- the centrifugal oil pressure cancellation chamber 190 has hydraulic oil (for example, for lubrication / cooling, for example) via an oil passage formed in the input shaft 20i, the connecting member 125, the support portion 135 of the drum member 130, and the like. Drain oil) is supplied.
- the plurality of return springs SP1 are disposed in the centrifugal hydraulic pressure cancellation chamber 190 at intervals in the circumferential direction so as to be positioned between the piston 140 and the cancellation plate 170. Note that a single leaf spring may be used instead of the plurality of coil springs as the return spring SP1 of the clutch C1.
- the clutch C ⁇ b> 2 including the drum member 120 described above includes first and second sun gears 21 s and 22 s that are always connected from the third sun gear 23 s of the Ravigneaux planetary gear mechanism 25.
- a clutch hub 200 as a power transmission member that transmits power to the rotating element), a plurality of friction plates (first friction engagement plates) 201, a plurality of separator plates 202 (second friction engagement plates), and a backing plate;
- a piston 240 that presses and frictionally engages the friction plate 201 and the separator plate 202; a cancel chamber defining member 270; and a plurality of return springs that bias the piston 240 away from the friction plate 201 and the separator plate 202 (Coil spring) SP2.
- the clutch hub 200 includes a hub member (hub portion) 210 into which the inner peripheral portions of the plurality of separator plates 202 and the backing plate are fitted, and a support member 220 that supports the piston 240.
- the hub member 210 is formed of, for example, an aluminum alloy or the like, and includes a tubular portion 211 and an annular wall portion 212 that extends radially inward from one end (the left end in FIGS. 4 and 5) of the tubular portion 211. That is, the cylindrical portion 211 and the annular wall portion 212 are integrally formed by casting an aluminum alloy or the like.
- the support member 220 is formed of an iron alloy or the like, and includes a cylindrical shaft portion 221 and an annular engagement oil chamber defining portion 222 that extends radially outward from one end of the shaft portion 221. That is, the shaft portion 221 and the engagement oil chamber defining portion 222 are integrally formed by forging an iron alloy or the like. As shown in FIGS. 4 and 5, the support member 220 (shaft portion 221) of the clutch hub 200 is supported coaxially and rotatably by the input shaft 20i via a radial bearing.
- the cylindrical portion 211 of the hub member 210 includes a plurality of splines 211 s formed on the outer peripheral surface and a cylindrical portion 211, that is, a plurality of teeth that penetrate the tooth tips of the splines 211 s in the radial direction.
- Oil hole 211h A part of the plurality of oil holes 211h located on both ends of the cylindrical portion 211 is formed so as to be slightly inclined with respect to the radial direction of the cylindrical portion 211, as shown in FIGS. Is done.
- the annular wall portion 212 of the hub member 210 has an inner peripheral portion 213 that is loosely splined (freely fitted) to the shaft portion 221 of the support member 220.
- a spline 213 s is formed on the inner peripheral surface of the inner peripheral portion 213, and the spline 213 s is an outer peripheral surface of the distal end portion (free end portion) of the shaft portion 221. Is loosely fitted to the spline 221s (see FIG. 4) formed in the above.
- the spline 213s of the inner peripheral part 213 and the spline 221s of the shaft part 221 constitute an inner spline fitting part SLi.
- annular wall portion 212 is radially inward of the tubular portion 211 and radially outward of the inner peripheral portion 213 and opposite to the tubular portion 211 (the left side in FIGS. 4 and 5, that is, the Ravigneaux type planetary gear). It has a cylindrical protrusion 214 protruding toward the mechanism 25 side. As shown in FIGS. 4 and 5, the axial length of the protruding portion 214 is set to be longer than the axial length of the inner peripheral portion 213 of the annular wall portion 212. As shown in FIG. 7, a spline 214s is formed.
- the spline 214s of the protruding portion 214 is fitted to a spline formed on the outer peripheral surface of the shaft portion 23sa extending in the axial direction from the third sun gear 23s (second output element) of the Ravigneaux type planetary gear mechanism 25.
- the spline 214s of the projecting portion 214 and the spline of the third sun gear 23s constitute an outer spline fitting portion SLo.
- the protruding portion 214 is located on the radially outer side than the inner peripheral portion 213 of the annular wall portion 212. Therefore, the outer spline fitting portion SLo that is a fitting portion between the hub member 210 and the third sun gear 23s is an inner spline fitting portion SLi that is a fitting portion between the hub member 210 and the shaft portion 221 (support member 220). It will be located radially outside. Moreover, the inner peripheral part 213 of the annular wall part 212 has an axial length shorter than the axial length of the protrusion part 214 as mentioned above. Therefore, the length of the inner spline fitting portion SLi in the axial direction is shorter than the length of the outer spline fitting portion SLo in the axial direction.
- the clearance in the circumferential direction of the outer spline fitting portion SLo that is, the clearance in the circumferential direction between the tooth surface of the spline 214s of the protruding portion 214 and the tooth surface of the spline of the shaft portion 23sa is determined to be extremely small. ing. Thereby, the inner peripheral part of the protrusion part 214 is tightly spline-fitted to the shaft part 23sa so as to rotate integrally with the third sun gear 23s that is an element to be connected to the clutch C2.
- the clearance in the circumferential direction of the inner spline fitting portion SLi that is, the clearance in the circumferential direction between the tooth surface of the spline 213s of the inner peripheral portion 213 and the tooth surface of the spline 221s of the shaft portion 221 is the outer spline.
- the clearance is set larger than the clearance in the circumferential direction of the fitting portion SLo.
- the protrusion 214 of the hub member 210 that is spline-fitted to the third sun gear 23 s is a part of the third carrier 23 c of the Ravigneaux type planetary gear mechanism 25, that is, the third pinion gear. 23p and the 4th pinion gear 24p, it is located in the radial direction inner side of the shaft support part 23cs which supports the edge part of the pinion shaft 26 penetrated.
- an oil collecting portion is connected to an inner circumferential surface of the shaft support portion 23cs of the third carrier 23c so as to communicate with an axial oil passage (an oil passage in the shaft) 26a formed inside each pinion shaft 26.
- a (recess) 23ca is formed.
- the protruding portion 214 is surrounded by the oil collecting portion 23ca. Note that the oil collecting portion 23ca is not necessarily formed on the third carrier 23c (shaft support portion 23cs), and may be formed on an oil receiver attached to the third carrier 23c.
- each raised portion 214p protrudes from the outer peripheral surface of the protruding portion 214 toward the oil collecting portion 23ca formed on the shaft support portion 23cs of the third carrier 23c, and has a substantially flat top surface 214ps.
- each of the protrusions 214 has a plurality (for example, four in this embodiment) of oil holes 214h that pass through the corresponding protrusions 214p (protrusion 214) and open at the top surface 214ps of the protrusion 214p.
- each oil hole 214 h is provided in the oil collecting portion 23 ca (Ravigneaux type planetary gear mechanism 25) of the third carrier 23 c as it goes radially outward from the inner peripheral surface of the protruding portion 214. Tilt to approach.
- the third sun gear 23s which is an element to be connected to the clutch C2 has a center hole portion 23sc that penetrates the gear portion and the shaft portion 23sa in the axial direction.
- the tip portion of the shaft portion 221 of the support member 220 is fitted inward (fitted more loosely than press-fitting) so that the third sun gear 23s can be aligned on the radially inner side of the inner peripheral surface of the protruding portion 214.
- the third sun gear 23s which is a connection target element of the clutch C2 can be aligned with the input shaft 20i by the shaft portion 221 of the clutch hub 200.
- a snap ring 216 that restricts the movement of the hub member 210 in the axial direction with respect to the support member 220 is attached to the distal end portion of the shaft portion 221, and between the snap ring 216 and the inner peripheral portion 213 of the hub member 210. Is provided with a spacer 217 that is an annular plate made of an iron alloy. As shown in the drawing, the outer peripheral surface of the snap ring 216 is supported from the radially outer side by the inner peripheral surface of the third sun gear 23 s, thereby suppressing the snap ring 216 from expanding in the radial direction. .
- the spacer 217 (inner peripheral portion 213) and the end surface of the shaft portion 23sa of the third sun gear 23s are opposed to each other with a space therebetween, and the shaft of the spacer 217 and the third sun gear 23s.
- a space between the end surface of the portion 23sa communicates with each oil hole 214h of the protruding portion 214.
- the shaft portion 23sa of the third sun gear 23s is formed with a plurality of oil grooves 23sg that connect the space between the spacer 217 and the end surface of the shaft portion 23sa of the third sun gear 23s and the inside of the center hole portion 23sc.
- hydraulic oil for example, lubricating / cooling drain oil
- the working oil as a lubricating / cooling medium is supplied to the oil collecting part 23ca of the third carrier 23c by centrifugal force through the oil holes 214h of the projecting part 214.
- the hydraulic oil collected by the oil collecting portion 23ca flows into the axial oil passage 26a of each pinion shaft 26 by centrifugal force, and the radial oil passage (in-shaft oil passage) 26b communicates with the axial oil passage 26a.
- a plurality of friction plates 201 (respective inner peripheral portions) of the clutch C2 are formed on the half of the cylindrical portion 121 of the drum member 120 on the Ravigneaux planetary gear mechanism 25 side (left side in FIGS. 3 and 4). It is fitted to the spline 121b.
- the plurality of friction plates 201 are supported by the drum member 120 that functions as a clutch drum so as to rotate integrally with the cylindrical portion 121 and be movable in the axial direction.
- the plurality of separator plates 202 and the backing plate (the respective outer peripheral portions) of the clutch C2 are fitted to splines 211s (see FIGS. 6 and 8) formed on the outer peripheral surface of the cylindrical portion 211 of the clutch hub 200.
- the plurality of separator plates 202 are supported by the clutch hub 200 so as to rotate integrally with the cylindrical portion 211 and to be movable in the axial direction.
- the piston 240 of the clutch C ⁇ b> 2 extends in the axial direction from the pressure receiving portion 241 that is supported by the shaft portion 221 of the support member 220 so as to be movable in the axial direction, and from the outer periphery of the pressure receiving portion 241.
- the piston 240 is fitted to the shaft portion 221 so as to be movable in the axial direction so that the pressure receiving portion 241 is positioned closer to the engagement oil chamber defining portion 222 than the spline 221s of the shaft portion 221, and the drum member Surrounded by 120 cylindrical portions 121.
- the inner peripheral surface of the extending portion 242 of the piston 240 is in sliding contact with the outer peripheral surface of the engaging oil chamber defining portion 222, and the inner peripheral surface of the extending portion 242 and the outer peripheral surface of the engaging oil chamber defining portion 222 are in contact with each other.
- a seal member 223 is disposed therebetween.
- the engagement oil chamber 250 of the clutch C2 is defined by the pressure receiving portion 241 and the extension portion 242 of the piston 240 and the engagement oil chamber defining portion 222 of the support member 220.
- the engagement oil chamber 250 is supplied with the engagement hydraulic pressure (hydraulic oil) to the clutch C2 regulated by the hydraulic control device via the oil passage formed in the input shaft 20i, the shaft portion 221 and the like.
- the pressure receiving portion 241 receives the engagement hydraulic pressure.
- the pressure receiving portion 241 of the piston 240 has a plurality of protrusions 241p protruding toward the engagement oil chamber defining portion 222 at intervals in the circumferential direction (in this embodiment, two at 180 ° intervals). Is formed. Furthermore, a plurality of concave portions 222r are formed in the engagement oil chamber defining portion 222 at intervals in the circumferential direction (in this embodiment, two at 180 ° intervals). Each protrusion 241p of the piston 240 is loosely fitted in the corresponding recess 222r of the engagement oil chamber defining part 222.
- the piston 240 is prevented from rotating with respect to the engagement oil chamber defining portion 222, that is, the support member 220, and the support member 220 (the shaft portion 221 and the shaft portion 221). It is possible to prevent rotation with respect to the hub member 210 via the engagement oil chamber defining portion 222).
- at least one protrusion 241p and recess 222r may be provided on the piston 240 or the engagement oil chamber defining part 222, and three or more may be provided.
- at least one protrusion may be provided in the engagement oil chamber defining part 222, and a recess that engages with the protrusion may be provided in the piston 240.
- the cancel chamber defining member 270 of the clutch C ⁇ b> 2 is fitted in the cylindrical portion 211 of the hub member 210, and the centrifugal oil pressure cancel chamber 290 for canceling the centrifugal oil pressure generated in the engagement oil chamber 250 is formed together with the piston 240.
- the engagement oil chamber 250 and the centrifugal hydraulic pressure cancellation chamber 290 of the clutch C2 are rotated integrally with the third sun gear 23s (second output element) of the Ravigneaux type planetary gear mechanism 25.
- the piston 240 and the cancel chamber defining member 270 are defined inside the cylindrical portion 211.
- the hydraulic oil pressure canceling chamber 290 is supplied with hydraulic oil (for example, lubricating / cooling drain oil) from an oil pressure control device via an oil passage formed in the input shaft 20i, the shaft portion 221 and the like.
- the cancel chamber defining member 270 includes a cylindrical sleeve portion 271 fitted into the tubular portion 211 of the hub member 210 and one end of the sleeve portion 271 (see FIGS. 4 and 5). 5 and the annular flange portion 272 extending along the surface of the annular wall portion 212 of the hub member 210.
- the inner peripheral surface of the sleeve portion 271 is in sliding contact with the outer peripheral surface of the extending portion 242 of the piston 240, and a seal member 244 is disposed between the inner peripheral surface of the sleeve portion 271 and the outer peripheral surface of the extending portion 242.
- each return spring SP2 is arranged between the flange portion 272 and the pressure receiving portion 241 of the piston 240 so as to be arranged in the circumferential direction.
- One end (the right end in FIGS. 4 and 5) of each return spring SP2 is fitted into one of the corresponding plurality of spring holding recesses formed in the pressure receiving portion 241 of the piston 240, and the other end of each return spring SP2 is The spring seat is supported by the cancel chamber defining member 270.
- the cancel chamber defining member 270 can be pressed against the hub member 210 by the plurality of return springs SP2 and fixed to the clutch hub 200 without using a dedicated fixing component or the like.
- a single leaf spring may be used instead of the plurality of coil springs as the return spring SP2 of the clutch C2.
- the inner peripheral surface of the cylindrical portion 211 of the hub member 210 is formed in a concave cylindrical surface shape, and the inner peripheral surface of the free end portion of the cylindrical portion 211 protrudes radially inward and cancels.
- An annular protrusion 211a that is in contact with the outer peripheral surface of the sleeve portion 271 of the chamber defining member 270 over the entire periphery is formed.
- the annular wall portion 212 of the hub member 210 is spaced apart in the circumferential direction so that a plurality of arc-shaped protrusions 212p that abut against the flange portion 272 of the cancel chamber defining member 270 face the return spring SP2. (In this embodiment, 5 are formed at equal intervals).
- a plurality of contact portions 272c that protrude toward the annular wall portion 212 and contact the surface of the annular wall portion 212 are provided on the inner peripheral portion of the flange portion 272 of the cancel chamber defining member 270. It is formed at intervals in the circumferential direction.
- the cancel chamber defining member 270 is pressed against the hub member 210 by the plurality of return springs SP2, so that the lubricating oil chamber 275 together with the inner peripheral surface of the cylindrical portion 211 and the surface of the annular wall portion 212 on the piston 240 side.
- a plurality of spaces extending between the annular space and the adjacent protrusions 212p are provided between the surface of the flange portion 272 that contacts the protrusion 212p and the surface of the annular wall portion 212.
- the communication path is defined between the surface of the flange portion 272 that contacts the protrusion 212p and the surface of the annular wall portion 212.
- a plurality of communication ports 273 are formed between the adjacent contact portions 272c of the flange portion 272, as shown in FIGS.
- the lubricating oil chamber 275 extends along the inner peripheral surface of the cylindrical portion 211 and the surface of the annular wall portion 212, and at the side of the shaft portion 221 of the support member 220 via the plurality of communication ports 273, that is, the clutch hub.
- the centrifugal hydraulic pressure cancellation chamber 290 communicates with the inner peripheral side of the 200.
- the lubricating oil chamber 275 communicates with the outside of the cylindrical portion 211, that is, the friction plate 201 and the separator plate 202 side through a plurality of oil holes 211 h formed in the cylindrical portion 211.
- the free end portion 271a of the sleeve portion 271 is curved outward in the radial direction over the entire circumference, and the inner peripheral surface of the free end portion 271a has an R shape.
- the protruding portion 214 of the hub member 210 is tightly splined to the shaft portion 23sa so as to rotate integrally with the third sun gear 23s, whereas the inner peripheral portion 213 of the annular wall portion 212. Are loosely splined (freely fitted) to the shaft portion 221 so that the hub member 210 does not rotate with respect to the support member 220.
- the clearance in the circumferential direction of the inner spline fitting portion SLi configured by the spline 213s of the inner peripheral portion 213 and the spline 221s of the shaft portion 221 is configured by the spline 214s of the protruding portion 214 and the spline of the third sun gear 23s. It is larger than the clearance in the circumferential direction of the outer spline fitting portion SLo.
- the support member 220 that is, the shaft portion 221 and the engagement oil chamber defining portion 222 that are integrally formed with each other are prevented from rotating with respect to the hub member 210, and the shaft portion 221 and Torque can be prevented from being transmitted from the hub member 210 to the engagement oil chamber defining portion 222. Accordingly, it is possible to improve durability while reducing the size and weight of the support member 220, that is, the shaft portion 221 and the engagement oil chamber defining portion 222 integrated with each other, and the clutch hub 200 as a whole.
- the outer spline fitting portion SLo is located on the radially outer side than the inner spline fitting portion SLi. Accordingly, the torque radius in the outer spline fitting portion SLo that is the fitting portion between the protruding portion 214 and the third sun gear 23s can be increased, so that the axial length of the protruding portion 214 is shortened and the axial length of the clutch C2 is reduced.
- the inner spline fitting portion SLi which is a fitting portion between the inner peripheral portion 213 of the annular wall portion 212 and the shaft portion 221 of the support member 220
- the inner spline fitting portion SLi that is, the inner spline fitting portion SLi
- the peripheral portion 213 only needs to have an axial length that can prevent the support member 220 (the shaft portion 221 and the engagement oil chamber defining portion 222) from rotating with respect to the hub member 210. Therefore, in the clutch C2, it is possible to further shorten the axial length by making the length of the inner peripheral portion 213 of the annular wall portion 212 in the axial direction shorter than the length of the protruding portion 214 in the axial direction.
- the brake B1 is engaged in addition to the clutch C2, so that the Ravigneaux planetary gear mechanism 25 is
- the fourth sun gear 24s (fixable element) is fixed so as not to rotate (see FIG. 2).
- the third carrier rotates from the input shaft 20i so that the rotational speed of the third sun gear 23s (second output element) is higher than the rotational speed of the third ring gear 23r (first output element) by the Ravigneaux planetary gear mechanism 25.
- the power transmitted to 23c (input element) is increased and transmitted to the third sun gear 23s and the third ring gear 23r (see FIG. 3).
- the third sun gear 23s (and the third ring gear 23r) of the Ravigneaux type planetary gear mechanism 25 is more than the third carrier 23c, that is, the input shaft 20i or more, except when the reverse gear is formed. It rotates at the rotation speed. Therefore, by reducing the size and weight of the clutch hub 200 of the clutch C2 and improving the durability, the third sun gear 23s that rotates at a higher speed than the input shaft 20i and the third ring gear 23r and the clutch hub that rotates integrally therewith. It is possible to reduce the inertia at the time of rotation of the 200 to improve the speed change performance of the automatic transmission 20 and to ensure good durability of the automatic transmission 20.
- the pressure receiving portion 241 of the piston 240 is formed with a plurality of protrusions 241p protruding toward the engagement oil chamber defining portion 222, and each of the engagement oil chamber defining portions 222 has a protrusion.
- a recess 222r that engages with the portion 241p is formed. Accordingly, the piston 240 is prevented from rotating with respect to the hub member 210 by the support member 220, that is, the shaft portion 221 and the engagement oil chamber defining portion 222 that are integrally formed with each other, while suppressing an increase in the size of the clutch C2. Can do.
- the relative rotation between the piston 240 and the engagement oil chamber defining part 222 and the relative rotation between the piston 240 and the hub member 210 are well regulated, and the piston 240 and the engagement oil chamber defining part 222 are worn well. Therefore, the durability of the clutch hub 200 can be improved. Furthermore, by forming the protrusion 241p on the pressure receiving portion 241 of the piston 240, a decrease in the thickness of the pressure receiving portion 241 can be suppressed, and the durability of the piston 240 can be ensured satisfactorily.
- the relative rotation of the constituent members of the third sun gear 23s that rotates at a higher speed than the input shaft 20i and the third ring gear 23r and the clutch hub 200 that rotates together with the third sun gear 23r is well regulated to improve durability.
- the durability of the automatic transmission 20 can be further improved.
- the space defined by the cylindrical portion 211 and the annular wall portion 212 of the hub member 210 and the piston 240 is partitioned into a centrifugal hydraulic pressure cancel chamber 290 and a lubricating oil chamber 275 by the cancel chamber defining member 270.
- the centrifugal oil pressure cancellation chamber 290 and the lubricating oil chamber 275 communicate with each other on the shaft portion 221 side of the support member 220 of the clutch hub 200.
- a part of the hydraulic oil supplied to the centrifugal hydraulic pressure cancel chamber 290 defined inside the cylindrical portion 211 is caused to flow into the lubricating oil chamber 275 and the friction plate 201 disposed around the cylindrical portion 211.
- the cancel chamber defining member 270 has a sleeve portion 271 fitted into the tubular portion 211 of the hub member 210 and a flange portion 272 extending radially inward from one end of the sleeve portion 271.
- a seal member 244 is disposed between the inner peripheral surface of the sleeve portion 271 and the extended portion 242 of the piston 240.
- a plurality of return springs SP2 are arranged between the flange portion 272 and the piston 240 so as to be aligned in the circumferential direction.
- the cancel chamber defining member 270 can be pressed against the hub member 210 by the plurality of return springs SP2 and fixed to the clutch hub 200 without using a dedicated fixing component or the like.
- annular protrusion 211 a that protrudes radially inward and contacts the outer peripheral surface of the sleeve portion 271 is formed.
- a plurality of protrusions 212p that abut on the flange portion 272 are formed on the wall portion 212 at intervals in the circumferential direction so as to face the return spring SP2.
- a plurality of abutting portions 272 c that protrude toward the annular wall portion 212 and abut against the surface of the annular wall portion 212 are formed on the inner circumferential portion of the flange portion 272 at intervals in the circumferential direction.
- a communication port 273 that connects the lubricating oil chamber 275 and the centrifugal hydraulic pressure cancellation chamber 290 is formed between the contact portions 272c.
- the lubricating oil chamber 275 is defined so as to extend along the inner peripheral surface of the cylindrical portion 211 and the surface of the annular wall portion 212, and the outflow of hydraulic oil from the free end portion of the cylindrical portion 211 is restricted.
- the lubricating oil chamber 275 can be communicated with the centrifugal hydraulic pressure cancellation chamber 290 on the shaft portion 221 side of the support member 220.
- the protrusion 214 of the clutch hub 200 (hub member 210) has a plurality of raised portions 214p that protrude to the oil collecting portion 23ca side from the outer peripheral surface of the protrusion 214, respectively, and a third as it goes radially outward.
- the carrier 23c has a plurality of oil holes 214h that incline so as to be close to the oil collecting portion 23ca and pass through the protrusion 214 and open at the top surface 214ps of the raised portion 214p.
- the oil hole 214h is opened at the top surface 214ps of each raised portion 214p formed in the protruding portion 214 in this manner, and the opening on the third carrier 23c side of each oil hole 214h is surrounded by the raised portion 214p.
- the shaft portion 23sa of the third sun gear 23s includes a center hole portion 23sc into which the tip end portion of the shaft portion 221 of the clutch hub 200 is fitted, and each oil hole 214h inside the center hole portion 23sc and the protruding portion 214. And an oil groove 23 sg that communicates with each other.
- the inner peripheral portion 213 of the annular wall portion 212 of the hub member 210 is loosely fitted to the shaft portion 221 of the support member 220 on the radial inner side of the inner peripheral surface (spline 214s) of the protruding portion 214, and the third sun gear 23s. It faces the end face of the shaft portion 23sa with a space.
- the oil groove 23sg of the third sun gear 23s and the oil holes 214h of the protrusion 214 can be communicated with each other while the shaft portion 221 of the support member 220 is prevented from rotating with respect to the hub member 210.
- FIG. 9 is an enlarged cross-sectional view of a main part showing an automatic transmission 20B as another transmission device of the present disclosure.
- the automatic transmission 20B shown in the figure includes a clutch C2 'different from the clutch C2.
- the configuration of the automatic transmission 20B other than the clutch C2 ' is basically the same as that of the automatic transmission 20, and among the components of the automatic transmission 20B, the same elements as those of the automatic transmission 20 are denoted by the same reference numerals. And redundant description is omitted.
- the clutch C2 ′ also includes the drum member 120 described above as a constituent member.
- the clutch C2 ' is a clutch as a power transmission member that transmits power from the third sun gear 23s of the Ravigneaux type planetary gear mechanism 25 to the first and second sun gears 21s, 22s (other rotating elements) that are always connected.
- Hub 200B a plurality of friction plates 201, a plurality of separator plates 202 and a backing plate, a piston 240 that presses and frictionally engages friction plates 201 and separator plate 202, cancel chamber defining member 270, and piston 240 And a cancel chamber defining member 270 (clutch hub 200B), and a plurality of return springs (coil springs) SP2 that urge the piston 240 away from the friction plate 201 and the separator plate 202.
- coil springs coil springs
- the clutch hub 200 ⁇ / b> B includes a hub member (hub portion) 210 ⁇ / b> B into which a plurality of separator plates 202 and a backing plate are fitted, and a support member 220 that supports the piston 240.
- the hub member 210B is also formed of, for example, an aluminum alloy, and the radially inner side from the cylindrical portion 211 having splines 211s formed on the outer peripheral surface and one end of the cylindrical portion 211 (the left end in FIGS. 4 and 5). And an annular wall portion 212B extending in the direction.
- the inner peripheral portion 213 of the annular wall portion 212B has a center hole (circular hole) having a larger diameter than the center hole of the annular wall portion 212 (inner peripheral portion 213) of the hub member 210. Further, the annular wall portion 212B also has a cylindrical shape that protrudes radially inward of the cylindrical portion 211 and radially outward of the inner peripheral portion 213 and opposite to the cylindrical portion 211 (Ravigneaux planetary gear mechanism 25 side). Projecting portion 214. The axial length of the protruding portion 214 is longer than the axial length of the inner peripheral portion 213 of the annular wall portion 212B, and a spline is formed on the inner peripheral surface of the protruding portion 214.
- An annular sleeve member 218 is fitted into the inner peripheral portion 213 (center hole) of the annular wall portion 212B of the hub member 210B from the protruding portion 214 side.
- the sleeve member 218 includes a radial support surface 218a that supports the inner peripheral surface of the inner peripheral portion 213 (hub member 210B), and an axial support portion 218b that protrudes radially outward from the radial support surface 218.
- the axial support portion 218b has an outer diameter smaller than the inner diameter of the protruding portion 214, and supports the end surface of the inner peripheral portion 213 on the protruding portion 214 side in the axial direction.
- the support member 220B is formed of an iron alloy or the like, and includes a cylindrical shaft portion 221B and an annular engagement oil chamber defining portion 222 that extends radially outward from one end of the shaft portion 221B.
- the shaft portion 221B and the engagement oil chamber defining portion 22 are integrally formed. As a result, it is possible to ensure good durability while reducing both size and weight.
- the support member 220B (shaft portion 221B) is supported coaxially and rotatably by the input shaft 20i via a radial bearing.
- a plurality of (for example, 2 to 4) concave portions 221r extending in the axial direction are formed at the distal end portion of the shaft portion 221B at intervals in the circumferential direction.
- the hub member 210B and the sleeve member 218 are assembled to the support member 220B, and the tip of the shaft portion 221B is The sleeve member 218 fitted in the hub member 210B is fitted in the center hole. Further, a snap ring groove is formed in the shaft portion 221B, and a snap ring 219 as a movement restricting member is provided in the snap ring groove so as to abut the end surface of the sleeve member 218 on the axial support portion 218b side. Installed.
- the biasing force of the return spring SP2 is received by the snap ring 219 via the hub member 210B and the axial support portion 218b of the sleeve member 218, whereby the axial direction of the hub member 210B with respect to the shaft portion 221B (support member 220B). Movement in is regulated.
- the outer peripheral surface of the snap ring 219 is supported from the outer side in the radial direction by the inner peripheral surface of the step formed on the sleeve member 218, thereby suppressing the expansion of the snap ring 219.
- the third sun gear 23s is assembled to the support member 220B and the hub member 210B, and the shaft portion 221B has a central hole portion of the third sun gear 23s radially inward from the inner peripheral surface of the protruding portion 214 of the hub member 210B. In-slot fitting at 23 sc.
- the spigot fitting portion Ef between the shaft portion 221B and the third sun gear 23s is formed so as to be adjacent to the snap ring 219 in the axial direction.
- the spline of the protruding portion 214 is fitted to a spline formed on the outer peripheral surface of the shaft portion 23sa of the third sun gear 23s. As shown in FIG.
- the shaft portion 23sa of the third sun gear 23s is formed with a plurality of (for example, 2 to 4) projections 23sp spaced apart in the circumferential direction, and each projection 23sp has a central hole.
- the shaft portion 221B is loosely fitted into the corresponding concave portion 221r of the shaft portion 221B fitted in the portion 23sc. As a result, the shaft portion 221B, that is, the support member 220B can be prevented from rotating with respect to the third sun gear 23s and the hub member 210B.
- the spline of the protruding portion 214 and the spline of the third sun gear 23s constitute the spline fitting portion Esp on the radially outer side of the spigot fitting portion Ef between the shaft portion 221B and the third sun gear 23s.
- the clearance in the circumferential direction of the outer spline fitting portion Esp that is, the clearance in the circumferential direction between the tooth surface of the spline 214s of the protruding portion 214 and the tooth surface of the spline of the shaft portion 23sa is determined to be extremely small. ing.
- the clearance in the radial direction of the outer spline fitting portion Esp that is, the clearance between the tooth bottom of the spline 214s of the protruding portion 214 and the tooth tip of the spline of the shaft portion 23sa is set to be large to some extent.
- a plurality of protrusions 241p protruding toward the engagement oil chamber defining part 222 are also formed at intervals in the circumferential direction on the pressure receiving part 241 of the piston 240 of the clutch C2 ′.
- a plurality of recesses 222r are also formed in the engagement oil chamber defining part 222 at intervals in the circumferential direction.
- Each protrusion 241p of the piston 240 is loosely fitted in the corresponding recess 222r of the engagement oil chamber defining part 222.
- the piston 240 is prevented from rotating with respect to the engagement oil chamber defining portion 222, that is, the support member 220B, and the support member 220B (the shaft portion 221B and It is possible to prevent rotation with respect to the hub member 210 via the engagement oil chamber defining portion 222).
- the clutch hub 200B of the clutch C2 ′ includes the hub member 210B into which the plurality of separator plates 202 are fitted, the cylindrical shaft portion 221B that supports the piston 240 movably, and the engagement oil chamber 250. And an engaging oil chamber defining part 222 that defines the piston 240 together with the piston 240.
- the hub member 210B is spline-fitted so as to rotate integrally with the third sun gear 23s of the Ravigneaux planetary gear mechanism 25, and the shaft portion 221B is rotatably supported by an input shaft 20i as a central axis. Then, the third sun gear 23s is inlay-fitted.
- the hub member 210B of the clutch hub 200B is separated from the third sun gear 23s and is spline-fitted to the third sun gear 23s, so that the processing accuracy of the third sun gear 23s can be secured well and It can be rotated together. Further, the third sun gear 23 s is accurately supported (aligned) by the shaft portion 221 B by fitting the shaft portion 221 B of the clutch hub 200 B rotatably supported by the input shaft 20 i into the third sun gear 23 s. be able to.
- the spline fitting portion Esp between the protruding portion 214 of the hub member 210B and the third sun gear 23s is located on the radially outer side of the spigot fitting portion Ef between the shaft portion 221B and the third sun gear 23s. .
- the torque radius at the spline fitting portion Esp between the projecting portion 214 and the third sun gear 23s can be further increased. Therefore, the length of the spline fitting portion Esp in the axial direction is shortened, and the clutch C2 ' It is possible to suppress an increase in the axial length.
- the hub member 210B is supported in the radial direction by an annular sleeve member 219 fitted in-between the hub member 210B and the shaft portion 221B.
- the sleeve member 218 protrudes radially outward from the radial support surface 218a to support the inner peripheral surface of the hub member 210B, and the hub member 210B (inner peripheral portion 213) in the axial direction. And an axial direction support portion 218b.
- the position at which the hub portion 210B is supported in the axial direction by the sleeve member 218 is compared with that in the clutch C2 (near the inner periphery of the spacer 217). It can be made more radially outward.
- the shaft portion 221B of the support member 220B has a concave portion 221r extending in the axial direction
- the third sun gear 23s has a protrusion 23sp loosely fitted in the concave portion 221r. Accordingly, it is possible to prevent the shaft portion 221B from rotating with respect to the third sun gear 23s and the hub portion 210B while preventing torque from being transmitted from the third sun gear 23s and the hub member 210B to the shaft portion 221B (support member 220B). It becomes.
- the clutch of the present disclosure includes the friction plate (201), the separator plate (202), the clutch hub (200B), and the piston that presses the friction plate (201) and the separator plate (202).
- the clutch hub (200B) includes a hub portion (210B) into which an inner peripheral portion of the friction plate or the separator plate (202) is fitted, and the piston ( 240) a cylindrical shaft portion (221B) that movably supports and an engagement oil chamber defining portion (250) that, together with the piston (240), is provided with an engagement oil chamber (250) to which engagement oil pressure is supplied.
- the hub portion (210B) is spline-fitted so as to rotate integrally with the gear (23s) of the planetary gear (25).
- the shaft portion (221B), along with being rotatably supported by a central shaft (20i), is intended to be fitted spigot to said gear (23s).
- the clutch hub of this clutch defines a hub portion to which a friction plate or a separator plate is fitted, a cylindrical shaft portion that movably supports the piston, and an engagement oil chamber to which engagement hydraulic pressure is supplied together with the piston. And an engaging oil chamber defining part.
- the hub portion is spline-fitted so as to rotate integrally with the planetary gear, and the shaft portion is rotatably supported by the central axis and is inlay-fitted to the gear.
- the gear can be accurately supported (aligned) by the shaft portion.
- the clutch including the clutch hub that rotates integrally with the gear of the planetary gear it is possible to ensure good processing accuracy and support accuracy of the gear.
- the spline fitting portion (Esp) between the hub portion (210B) and the gear (23s) is radially outside the spigot fitting portion (Ef) between the shaft portion (221B) and the gear (23s). May be located.
- the torque radius in the spline fitting portion between the hub portion and the gear can be increased, so that the length of the spline fitting portion in the axial direction can be shortened to suppress an increase in the clutch shaft length. Is possible.
- the clutch (C2 ') is inlay-fitted between the hub portion (210B) and the shaft portion (221B) to support the hub portion (210B) in the radial direction (218). ) May be provided.
- the radial clearance in the spline fitting portion between the hub portion and the gear is reduced by supporting the hub portion in the radial direction by the sleeve member fitted in-between the hub portion and the shaft portion. Therefore, it is possible to further improve the assembling property between the hub portion and the gear.
- the sleeve member (218) protrudes radially outward from the radial support surface (218a) that supports the inner peripheral surface of the hub portion (210B) and the radial support surface (218a). You may have an axial direction support part (218b) which supports a hub part (210B) to an axial direction.
- the position (support point) at which the hub portion is supported in the axial direction by the sleeve member can be more radially outward, so that the moment acting on the hub portion when the clutch is engaged can be reduced, and the shaft of the sleeve member can be reduced. It is possible to further reduce the stress generated around the direction support portion.
- the hub portion (210B) extends inward in the radial direction from a cylindrical portion (211) to which the friction plate or the separator plate (220) is fitted, and one end of the cylindrical portion (211).
- the cylindrical wall portion (211) and the annular wall portion (212B) formed integrally may have an inner peripheral surface of the annular wall portion (212B) in the radial direction by the sleeve member (218).
- the annular wall portion (212B) may be supported, and has a cylindrical protrusion (214) that protrudes radially outward from the inner peripheral surface and opposite to the cylindrical portion (211).
- the inner peripheral portion of the protrusion (214) may be splined to the gear (23s).
- the shaft portion (221B) has a concave portion (221r) extending in the axial direction, and the gear (23s) is a protrusion (23sp) loosely fitted in the concave portion (221r) of the shaft portion (221B). You may have. Accordingly, it is possible to prevent the shaft portion from rotating with respect to the gear and the hub portion while preventing torque from being transmitted to the shaft portion from the gear and the hub portion.
- the shaft part (221B) and the engagement oil chamber defining part (222) may be integrally formed. That is, since the torque from the gear is not substantially transmitted to the shaft portion that is inlay-fitted to the gear of the planetary gear, if the shaft portion and the engagement oil chamber defining portion are formed integrally, the shaft portion is integrated. The durability of the shaft portion and the engagement oil chamber defining portion can be ensured satisfactorily while reducing the size and weight.
- one of the piston (240) and the engagement oil chamber defining part (222) may have at least one protrusion (241P) protruding toward the other, the piston (240) and The other of the engagement oil chamber defining part (222) may have a recess (222r) that engages with the protrusion (241p). Accordingly, the piston can be prevented from rotating with respect to the hub portion by the shaft portion and the engagement oil chamber defining portion that are integrally formed with each other.
- the clutch (C2 ′) is interposed between the piston (240) and the hub portion (210B), and the piston (240) is separated from the friction plate (201) and the separator plate (202).
- a return spring (SP2) that urges away from each other and an inlay fitting portion (Ef) between the shaft portion (221B) and the gear (23s) are arranged adjacent to each other in the axial direction, and the hub portion ( 210B) may be provided with a movement restricting member (219) for restricting movement relative to the shaft portion (221B) so as to be separated from the engagement oil chamber defining portion (222).
- the gear (23s) may be a sun gear of the planetary gear (25), and the hub portion (210B) may be spline-fitted to a shaft portion (23sa) of the sun gear.
- the portion (23sa) may have a center hole portion (23sc) into which the tip portion of the shaft portion (221B) of the clutch hub (200B) is fitted.
- the transmission of the present disclosure includes the clutch, and is a transmission (20B) that shifts the power transmitted to the input member (20i) and transmits the power to the output member (20o), the input element (23c), A Ravigneaux planetary gear mechanism (25) having a fixable element (24s), a first output element (23r) and a second output element (23s), and a first having a plurality of rotating elements (21s, 21c, 21r).
- a first planetary gear (21) and a plurality of rotating elements (22s, 22c, 22r) are arranged closer to the Ravigneaux type planetary gear mechanism (25) than the first planetary gear (21).
- a first planetary gear (22) and the Ravigneaux type planetary gear mechanism (25) are connected to the stationary member (11) to fix the non-rotatable element (24s) and the first is released from the connection.
- Brake (B1 The first output element (23r) of the Ravigneaux type planetary gear mechanism (25) and at least one of the rotating elements (21s, 22s) of the first and second planetary gears (21, 22).
- the first clutch (C1) for releasing the connection between them, the second output element (23s) of the Ravigneaux type planetary gear mechanism (25), and the first and second planetary gears (21 , 22) and a second clutch (C2 ′) for releasing at least one of the rotating elements (21s, 22s) from each other, and the Ravigneaux planetary gear mechanism (25).
- the fixable element (24s) is fixed non-rotatably by the first brake (B1)
- the rotation speed of the second output element (23s) is the rotation speed of the first output element (23r).
- the power transmitted to the input element (20i) is increased so as to increase, and is transmitted to the first and second output elements (23r, 23s), and the clutch is the second clutch (C2 ').
- the gear is the second output element (23s) of the Ravigneaux type planetary gear mechanism (25).
- the rotation speed of the second output element which is the connection target element of the clutch (second clutch)
- the power transmitted to the input element is increased so as to be higher than the rotational speed of the element, and is transmitted to the first and second output elements. Therefore, by improving the machining accuracy and support accuracy of the gear that is the second output element, it is possible to satisfactorily suppress the occurrence of noise and vibration during the operation of the transmission.
- the transmission (20B) may further include a third clutch (C3), a fourth clutch (C4), and a second brake (B2), and the first planetary gear (21) is a first sun gear. (21s), a first carrier (21c) and a first ring gear (21r), and the second planetary gear (22) includes a second sun gear (22s), a second carrier (22c) and a second A ring gear (22r) may be provided, and the first sun gear (21s) of the first planetary gear (21) and the second sun gear (22s) of the second planetary gear (22) are always connected.
- C3 third clutch
- C4 fourth clutch
- B2 second brake
- the first carrier (21c) of the first planetary gear (21) is always connected to the input member (20i) and the input element (23c) of the Ravigneaux type planetary gear mechanism (25).
- said The second carrier (22c) of the two planetary gears (22) may be always connected to the output member (20o), and the first clutch (C1) is connected to the Ravigneaux type planetary gear mechanism (25).
- the first output element (23r) and the first and second sun gears (21s, 22s) that are always connected may be connected to each other, and the connection between them may be released.
- the second clutch (C2 ') Connects the second output element (23s) of the Ravigneaux planetary gear mechanism (25) and the first and second sun gears (21s, 22s) that are always connected to each other and releases the connection between them.
- the third clutch (C3) may include the first output element (23r) of the Ravigneaux planetary gear mechanism (25) and the second ring gear (22r) of the second planetary gear (22). And each other
- the fourth clutch (C4) may be connected to the first ring gear (21r) of the first planetary gear (21) and the second planetary gear (22).
- the second carrier (22c) may be connected to each other and the connection between them may be released.
- the second brake (B2) is configured to connect the second ring gear (22r) of the second planetary gear (22). While connecting to the said stationary member (11) and fixing it to non-rotatable, you may cancel
- the invention of the present disclosure can be used in the manufacturing industry of clutches and transmissions.
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Abstract
Description
Claims (12)
- 摩擦プレートと、セパレータプレートと、クラッチハブと、前記摩擦プレートおよび前記セパレータプレートを押圧するピストンとを備えるクラッチにおいて、
前記クラッチハブは、前記摩擦プレートまたは前記セパレータプレートの内周部が嵌合されるハブ部と、前記ピストンを移動自在に支持する筒状のシャフト部と、係合油圧が供給される係合油室を前記ピストンと共に画成する係合油室画成部とを含み、
前記ハブ部は、遊星歯車のギヤに一体に回転するようにスプライン嵌合され、
前記シャフト部は、中心軸により回転自在に支持されると共に、前記ギヤにインロー嵌合されるクラッチ。 - 請求項1に記載のクラッチにおいて、
前記ハブ部と前記ギヤとのスプライン嵌合部は、前記シャフト部と前記ギヤとのインロー嵌合部の径方向外側に位置するクラッチ。 - 請求項1または2に記載のクラッチにおいて、
前記ハブ部と前記シャフト部との間にインロー嵌合されて該ハブ部を径方向に支持する環状のスリーブ部材を更に備えるクラッチ。 - 請求項3に記載のクラッチにおいて、
前記スリーブ部材は、前記ハブ部の内周面を支持する径方向支持面と、前記径方向支持面よりも径方向外側に突出すると共に前記ハブ部を軸方向に支持する軸方向支持部とを有するクラッチ。 - 請求項3または4に記載のクラッチにおいて、
前記ハブ部は、前記摩擦プレートまたは前記セパレータプレートが嵌合される筒状部と、前記筒状部の一端から径方向内側に延びるように該筒状部と一体に成形された環状壁部とを有し、
前記環状壁部の内周面は、前記スリーブ部材により径方向に支持され、
前記環状壁部は、前記内周面よりも径方向外側で前記筒状部とは反対側に突出する筒状の突出部を有し、
前記突出部の内周部は、前記ギヤにスプライン嵌合されることを特徴とするクラッチ。 - 請求項1から5の何れか一項に記載のクラッチにおいて、
前記シャフト部は、軸方向に延びる凹部を有し、前記ギヤは、前記シャフト部の前記凹部に遊嵌される突起を有するクラッチ。 - 請求項1から6の何れか一項に記載のクラッチにおいて、前記シャフト部と前記係合油室画成部とは一体に成形されているクラッチ。
- 請求項7に記載のクラッチにおいて、
前記ピストンおよび前記係合油室画成部の一方は、他方に向けて突出する少なくとも1つの突部を有し、前記ピストンおよび前記係合油室画成部の他方は、前記突部と係合する凹部を有することを特徴とするクラッチ。 - 請求項1から8の何れか一項に記載のクラッチにおいて、
前記ピストンと前記ハブ部との間に介設されて該ピストンを前記摩擦プレートおよび前記セパレータプレートから離間するように付勢するリターンスプリングと、
前記シャフト部と前記ギヤとのインロー嵌合部と軸方向に隣り合うように配置され、前記ハブ部が前記係合油室画成部から離間するように前記シャフト部に対して移動するのを規制する移動規制部材とを更に備えるクラッチ。 - 請求項1から9の何れか一項に記載のクラッチにおいて、
前記ギヤは、前記遊星歯車のサンギヤであり、
前記ハブ部は、前記サンギヤの軸部にスプライン嵌合され、
前記軸部は、前記クラッチハブの前記シャフト部の先端部がインロー嵌合される中心孔部を有することを特徴とするクラッチ。 - 請求項1から10の何れか一項に記載のクラッチを含み、入力部材に伝達された動力を変速して出力部材に伝達する変速装置であって、
入力要素と、固定可能要素と、第1出力要素および第2出力要素とを有するラビニヨ式遊星歯車機構と、
複数の回転要素を有する第1遊星歯車と、
複数の回転要素を有し、前記第1遊星歯車よりも前記ラビニヨ式遊星歯車機構に近接して配置される第2遊星歯車と、
前記ラビニヨ式遊星歯車機構の前記固定可能要素を静止部材に接続して回転不能に固定すると共に、両者の接続を解除する第1ブレーキと、
前記ラビニヨ式遊星歯車機構の前記第1出力要素と、前記第1および第2遊星歯車の回転要素の少なくとも何れか1つとを互いに接続すると共に、両者の接続を解除する第1クラッチと、
前記ラビニヨ式遊星歯車機構の前記第2出力要素と、前記第1および第2遊星歯車の回転要素の少なくとも何れか1つとを互いに接続すると共に、両者の接続を解除する第2クラッチとを備え、
前記ラビニヨ式遊星歯車機構は、前記固定可能要素が前記第1ブレーキにより回転不能に固定された際に、前記第2出力要素の回転速度が前記第1出力要素の回転速度よりも高くなるように前記入力要素に伝達された動力を増速して前記第1および第2出力要素に伝達し、
前記クラッチは、前記第2クラッチであり、前記ギヤは、前記ラビニヨ式遊星歯車機構の前記第2出力要素であることを特徴とする変速装置。 - 請求項11に記載の変速装置において、
第3クラッチ、第4クラッチおよび第2ブレーキを更に備え、
前記第1遊星歯車は、第1サンギヤ、第1キャリヤおよび第1リングギヤを有し、
前記第2遊星歯車は、第2サンギヤ、第2キャリヤおよび第2リングギヤを有し、
前記第1遊星歯車の前記第1サンギヤと前記第2遊星歯車の前記第2サンギヤとは、常時連結され、
前記第1遊星歯車の前記第1キャリヤは、前記入力部材および前記ラビニヨ式遊星歯車機構の前記入力要素に常時連結され、
前記第2遊星歯車の前記第2キャリヤは、前記出力部材に常時連結され、
前記第1クラッチは、前記ラビニヨ式遊星歯車機構の前記第1出力要素と、常時連結された前記第1および第2サンギヤとを互いに接続すると共に、両者の接続を解除し、
前記第2クラッチは、前記ラビニヨ式遊星歯車機構の前記第2出力要素と、常時連結された前記第1および第2サンギヤとを互いに接続すると共に、両者の接続を解除し、
前記第3クラッチは、前記ラビニヨ式遊星歯車機構の前記第1出力要素と、前記第2遊星歯車の前記第2リングギヤとを互いに接続すると共に、両者の接続を解除し、
前記第4クラッチは、前記第1遊星歯車の前記第1リングギヤと前記第2遊星歯車の前記第2キャリヤとを互いに接続すると共に、両者の接続を解除し、
前記第2ブレーキは、前記第2遊星歯車の前記第2リングギヤを前記静止部材に接続して回転不能に固定すると共に、両者の接続を解除することを特徴とする変速装置。
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CN201580070133.9A CN107110241B (zh) | 2014-12-26 | 2015-11-30 | 离合器及具有该离合器的变速装置 |
US15/529,751 US10378615B2 (en) | 2014-12-26 | 2015-11-30 | Clutch and speed change device including the same |
JP2016566063A JP6332472B2 (ja) | 2014-12-26 | 2015-11-30 | クラッチおよびそれを備えた変速装置 |
DE112015004655.0T DE112015004655B4 (de) | 2014-12-26 | 2015-11-30 | Kupplung und Geschwindigkeitsänderungsvorrichtung mit dieser |
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JP2014265299 | 2014-12-26 | ||
JP2014-265299 | 2014-12-26 |
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PCT/JP2015/083666 WO2016104063A1 (ja) | 2014-12-26 | 2015-11-30 | クラッチおよびそれを備えた変速装置 |
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US (1) | US10378615B2 (ja) |
JP (1) | JP6332472B2 (ja) |
CN (1) | CN107110241B (ja) |
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WO (1) | WO2016104063A1 (ja) |
Families Citing this family (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US9651118B2 (en) * | 2014-03-20 | 2017-05-16 | Gm Global Technology Operations, Llc | Multi-speed transmission |
JP6187352B2 (ja) * | 2014-03-27 | 2017-08-30 | アイシン・エィ・ダブリュ株式会社 | 多段変速機 |
JP6341216B2 (ja) * | 2016-02-09 | 2018-06-13 | トヨタ自動車株式会社 | 車両の動力伝達装置 |
FR3078373A1 (fr) * | 2018-02-27 | 2019-08-30 | Valeo Embrayages | Porte-disques pour un mecanisme d'embrayage |
WO2020084913A1 (ja) * | 2018-10-22 | 2020-04-30 | ジヤトコ株式会社 | 前後進切替機構 |
US11466765B2 (en) * | 2018-11-08 | 2022-10-11 | Valeo Kapec Japan Kk | Lock-up device of torque converter |
WO2020110554A1 (ja) * | 2018-11-27 | 2020-06-04 | ジヤトコ株式会社 | 動力伝達装置及び動力伝達装置の製造方法 |
JP7059922B2 (ja) * | 2018-12-25 | 2022-04-26 | マツダ株式会社 | 自動変速機 |
USD949201S1 (en) * | 2019-12-23 | 2022-04-19 | Frank C. Kuperman | Billet hub |
BE1027954B1 (nl) * | 2019-12-31 | 2021-08-04 | Punch Powertrain Psa E Trans Nv | Dubbelekoppelingtransmissiesysteem, voertuig en werkwijze voor koelen |
CN111810597B (zh) * | 2020-07-24 | 2022-05-27 | 吉林大学 | 一种双态逻辑变速器及其换挡过程控制方法 |
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- 2015-11-30 JP JP2016566063A patent/JP6332472B2/ja not_active Expired - Fee Related
- 2015-11-30 WO PCT/JP2015/083666 patent/WO2016104063A1/ja active Application Filing
- 2015-11-30 CN CN201580070133.9A patent/CN107110241B/zh active Active
- 2015-11-30 DE DE112015004655.0T patent/DE112015004655B4/de active Active
- 2015-11-30 US US15/529,751 patent/US10378615B2/en active Active
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Also Published As
Publication number | Publication date |
---|---|
DE112015004655T5 (de) | 2017-07-20 |
JP6332472B2 (ja) | 2018-05-30 |
US20170314650A1 (en) | 2017-11-02 |
DE112015004655B4 (de) | 2019-09-12 |
CN107110241A (zh) | 2017-08-29 |
US10378615B2 (en) | 2019-08-13 |
CN107110241B (zh) | 2018-12-21 |
JPWO2016104063A1 (ja) | 2017-07-20 |
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