CN101248294B - Hydraulic servo for a brake in an automatic transmission - Google Patents
Hydraulic servo for a brake in an automatic transmission Download PDFInfo
- Publication number
- CN101248294B CN101248294B CN200680031224.2A CN200680031224A CN101248294B CN 101248294 B CN101248294 B CN 101248294B CN 200680031224 A CN200680031224 A CN 200680031224A CN 101248294 B CN101248294 B CN 101248294B
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- drum
- hub portion
- working oil
- gear
- automatic transmission
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- 230000005540 biological transmission Effects 0.000 title claims abstract description 35
- 230000004323 axial length Effects 0.000 claims abstract description 15
- 230000008093 supporting effect Effects 0.000 claims abstract description 15
- 238000009434 installation Methods 0.000 claims description 16
- 230000002093 peripheral effect Effects 0.000 claims description 15
- 239000002184 metal Substances 0.000 claims description 8
- 239000003921 oil Substances 0.000 description 90
- 238000005202 decontamination Methods 0.000 description 5
- 230000003588 decontaminative effect Effects 0.000 description 5
- 239000012530 fluid Substances 0.000 description 5
- 230000008030 elimination Effects 0.000 description 3
- 238000003379 elimination reaction Methods 0.000 description 3
- 239000007788 liquid Substances 0.000 description 3
- 239000000314 lubricant Substances 0.000 description 3
- 238000010586 diagram Methods 0.000 description 2
- 239000004519 grease Substances 0.000 description 2
- 239000000178 monomer Substances 0.000 description 2
- 241000239290 Araneae Species 0.000 description 1
- 230000002159 abnormal effect Effects 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 230000003292 diminished effect Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 239000010687 lubricating oil Substances 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
- 239000007921 spray Substances 0.000 description 1
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Classifications
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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
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
- F16H2200/006—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising eight 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
- F16H2200/0082—Transmissions for multiple ratios characterised by the number of reverse speeds
- F16H2200/0086—Transmissions for multiple ratios characterised by the number of reverse speeds the gear ratios comprising two reverse 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
- F16H2200/2007—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with two 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
- F16H2200/2048—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with seven engaging means
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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
- F16H2200/2097—Transmissions using gears with orbital motion comprising an orbital gear set member permanently connected to the housing, e.g. a sun wheel permanently connected to the housing
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
- F16H3/62—Gearings having three or more central gears
- F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
- F16H3/666—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another with compound planetary gear units, e.g. two intermeshing orbital gears
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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
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H57/021—Shaft support structures, e.g. partition walls, bearing eyes, casing walls or covers with bearings
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structure Of Transmissions (AREA)
- General Details Of Gearings (AREA)
- Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
Abstract
The invention provides an automatic transmission which materializes lightweight and compactization by minimizing the axial length of an auxiliary bearing. The automatic transmission is provided with a main bearing 36 which is arranged in the inner periphery of a boss part 31a in a first drum 31 and the outer periphery of a cylinder supporting part 27a and which freely rotatably supports the firstdrum, and with an auxiliary bearing which is pressed in one end of the inner periphery of the boss part in the first drum, loosely fitted to the cylinder supporting part, abutted on the cylinder supporting part only when the first drum is inclined in a traveling direction of a vehicle and made the axial length shorter in comparison with the main bearing.
Description
Technical field
The present invention relates to automatic transmission, relate in particular to usually only and support bulging with a bearing, only masterpiece time spent another one bearing also has the automatic transmission of this function outside.
Background technique
Speed change becomes in the automatic transmission of multistage gear in conjunction with disengagement with clutch and break having, and clutch is made of drum, piston, cancellation element etc.And automatic transmission generally has 2 above clutches.
Patent documentation: the flat 9-210088 of TOHKEMY
Summary of the invention
The problem that invention will solve
In this automatic transmission, the swivel bearing of the drum of clutch, be to use bearing on one point or 2 of two ends support in revolvable mode.Under Zhi Cheng the situation, the axial length of bearing must be very big on one point, so that first drum can over-tilting not take place because of external force.On the other hand, under the situation of 2 supportings,, the axial length that can guarantee durability at least must be arranged for two bearings need the conduct durability of bearing separately.
Therefore, in existing automatic transmission, no matter some supporting and 2 supportings, because the end at the path of supply pressure oil disposes the big bearing of axial dimension, thereby make bulging axial length become big, thereby become stop drum and then, stop the light weight of automatic transmission, the main cause of miniaturization.
The present invention develops in view of above-mentioned existing issue, its objective is that providing a kind of becomes minimal axial length by the axial length with auxiliary bearing and can realize the automatic transmission of lightweight and miniaturization.
The means that are used to deal with problems
In order to address the above problem, the invention of technological scheme 1 record is the automatic transmission that the direction of travel of relative vehicle is provided in the motor rear, it is characterized in that this gear has: the cylinder support; The first oil pressure servomechanism installation, it has first drum and forms the first piston of the first cylinder chamber with this first drum, and can operate in described a plurality of clutch one; Main bearing, it is provided in the interior week of described first hub portion of rousing and is configured on the periphery of described cylinder support, and is supporting described first drum and described first drum can be rotated freely; Auxiliary bearing, its be pressed in described first the drum hub portion interior week an end and with described cylinder support Spielpassung, only under the situation of the direction of travel inclination of vehicle, connect, and axial length is shorter than described main bearing with described cylinder support at described first drum.
The invention of technological scheme 2 records, it is characterized in that, in technological scheme 1, described cylinder support is to extend the shaft sleeve part that is provided with from mission case, described gear has the first working oil supply hole of supplying with oil circuit and forming in first working oil that forms on the shaft sleeve part of described mission case on the hub portion of described first drum, by supplying with between oil circuit and the described first working oil supply hole between described first working oil, supply with working oil to the described first cylinder chamber at a pair of seal ring that sets on the shaft sleeve part of described mission case.
The invention of technological scheme 3 records, it is characterized in that, in technological scheme 2, described gear has: have second drum and second piston, this second piston forms the second cylinder chamber being provided on this second hub portion of rousing and with this second drum in the mode of sliding on the hub portion of this second drum; Second working oil is supplied with oil circuit, and it is formed on the shaft sleeve part of described mission case; The second working oil supply hole, it is formed on the hub portion of described first drum; The 3rd working oil supply hole, it is formed on the hub portion of described second drum, and, described first drum is to the direction of travel rear of vehicle opening, described first drum matches in the mode of energy one rotation by spline fitted portion with described second drum, this spline fitted portion is made of second spline tooth that forms on first spline tooth that forms on the outer circumferential face of direction of travel rear side end of the vehicle of the hub portion of described first drum and the inner peripheral surface in the hub portion of described second drum, described main bearing is provided on interior all sides of direction of travel rear side end of vehicle of hub portion of described first drum, supply with between oil circuit and the described second working oil supply hole between described second working oil by making at a pair of seal ring that sets on the shaft sleeve part of described mission case, and make a pair of seal ring that between the hub portion of described first hub portion of rousing and described second drum, sets between described second working oil supply hole and described the 3rd working oil supply hole, thereby supply with working oil to the described second cylinder chamber.
The invention of technological scheme 4 record is characterized in that, to each of technological scheme 3, described main bearing is made of metal lining in technological scheme 1.
The effect of invention
If according to the invention of technological scheme 1, owing to have: main bearing, it is provided on the periphery of interior week of hub portion of described first drum and described cylinder support, and is supporting described first drum and described first drum can be rotated freely; Auxiliary bearing, its be pressed in described first the drum hub portion interior week an end and with described cylinder support Spielpassung, only under the situation of the direction of travel inclination of vehicle, connect with described cylinder support at described first drum, and axial length is shorter than described main bearing, auxiliary bearing only carries out the supporting of first drum in case of necessity to vehicle heading inclination etc. at first drum, so do not need durability, minimal axle direction length can be become, first drum can be suppressed in axial maximization.
If invention according to technological scheme 2, has the first working oil supply hole that first working oil that forms is supplied with oil circuit and formed at gear on described gear has shaft sleeve part at described mission case on the hub portion of described first drum, by supplying with between oil circuit and the described first working oil supply hole between described first working oil at a pair of seal ring that sets on the shaft sleeve part of described mission case, supply with in the structure of working oil to the described first cylinder chamber, tilt to support first drum owing to accept first drum to vehicle heading, can prevent to supply with to the working oil of the first cylinder chamber the levering up of seal ring of oil circuit by first drum forming of tilting to cause with auxiliary bearing.So can prevent to prevent the controlled reduction of the first oil pressure servomechanism installation from the leakage of the pressure oil of the portion that levers up of seal ring.
If invention according to technological scheme 3, described first drum is to the direction of travel rear of vehicle opening, described first drum matches in the mode of energy one rotation by spline fitted portion with described second drum, this spline fitted portion is made of second spline tooth that forms on first spline tooth that forms on the outer circumferential face of direction of travel rear side end of the vehicle of the hub portion of described first drum and the inner peripheral surface in the hub portion of described second drum, described main bearing is provided on interior all sides of direction of travel rear side end of vehicle of hub portion of described first drum, supply with between oil circuit and the described second working oil supply hole between described second working oil by making at a pair of seal ring that sets on the shaft sleeve part of described mission case, and make a pair of seal ring that between the hub portion of described first hub portion of rousing and described second drum, sets between described second working oil supply hole and described the 3rd working oil supply hole, thereby supply with to the described second cylinder chamber under the situation of structure of working oil, supply with working oil by first drum to the second cylinder chamber for needs, first drum has the tendency of maximization.So, like this under the situation of the tendency that first drum maximizes, carry out first auxiliary bearing of supporting that rouses also carries out the supporting of first drum at first drum simultaneously under the situation of the direction of travel inclination of vehicle structure owing to become one side with main bearing, can better finish miniaturization.
If according to the invention of technological scheme 4,, can realize enough axial lengths easily for the swivel bearing drum because described main bearing is made of metal lining.
Description of drawings
Fig. 1 is the profile diagram of expression automatic transmission of the present invention.
Fig. 2 is the figure of the mated condition of the break of each gear train of automatic transmission of presentation graphs 1 and clutch.
Fig. 3 is the sectional view of the automatic transmission of the expression embodiment of the invention.
Fig. 4 is the figure that amplifies a part of having represented Fig. 3.
The explanation of reference character
10 ... automatic transmission, 11 ... mission case, 13 ... gear, 15 ... input shaft, 16 ... output shaft, 20 ... slow down and use planetary pinion, 21 ... planetary gear set, 27 ... oil pump body, 27a ... cylinder support (shaft sleeve part), 31 ... first drum, 32 ... second drum, 33 ... shroud member, 35 ... fixed muffle, 36 ... main bearing, 37 ... auxiliary bearing, 43,53,73 ... the cylinder chamber, 44,54,74 ... piston, 65,66 ... the working oil supply hole, 95 ... spline fitted portion, 99,100 ... seal ring, S1, S2, S3 ... sun gear, C1, C2, C3 ... support, R1, R2 ... gear ring, C-1 ... first clutch, C-2 ... second clutch, C-3 ... three-clutch, C-4 ... four clutches, B-1 ... second break, B-2 ... second break
Embodiment
Below, embodiments of the invention are described with reference to the accompanying drawings.Fig. 1 represents to be suitable for for example automatic transmission 10 of the vehicle of front-mounted engine rear-guard ejector half.This automatic transmission 10 has fluid torque converter 12 and gear 13 in the mission case 11 on being installed on car body.The input shaft 15 that pump impeller and the turbine wheel of the output that comes from motor by fluid torque converter 12 inputs to automatic transmission 10.Speed change is carried out in 13 pairs of rotations from input shaft 15 inputs of gear, and exports to the output shaft 16 that is connected in driving wheel.Fluid torque converter 12 has lock-up clutch 17.The input shaft 15 of automatic transmission 10 is coaxial with the direction of travel of output shaft 16 relative vehicles.The direction of travel of fluid torque converter 12 relative vehicles is provided in front side, and the direction of travel of output shaft 16 relative vehicles is provided in rear side simultaneously.In the present embodiment, axial fluid torque converter 12 sides of automatic transmission 10 (the direction of travel front side of vehicle) are called " the place ahead ", output shaft 16 sides (the direction of travel rear side of vehicle) are called " rear ".
The deceleration that makes the rotational delay of input shaft 15 and pass to the deceleration rotating member with planetary pinion 20 by often being fixed on the mission case 11 and the sun gear S1, the support C1 that is directly connected in described input shaft 15 that are limited to rotate, be bearing in that support C1 goes up and with the first small gear 23A of sun gear S1 engagement, be bearing in that support C1 goes up and constitute with the second small gear 23B of first small gear 23A engagement with the gear ring R1 of second small gear 23B engagement.
The first sun gear S2 of the path of planetary gear set 21, by first clutch C-1 can be connected with this gear ring R1 in conjunction with the mode of disengagement with the gear ring R1 that slows down with planetary pinion 20, the secondary sun wheel S3 in big footpath, being connected with this gear ring R1 in conjunction with the mode of throwing off with the gear ring R1 that slows down with planetary pinion 20, and the support C1 that uses planetary pinion 20 by four clutches C-4 via deceleration is to be connected with this input shaft 15 with the mode of input shaft 15 energy in conjunction with disengagement by three-clutch C-3.Short and small gear 25 and first sun gear S2 engagement.And long small gear 26 meshes with short and small gear 25 when meshing with secondary sun wheel S3.These short and small gears 25 and long small gear 26 are bearing in respectively on support C2, the C3 of direct joint construction revolvably.Gear ring R2 meshes with long small gear 26, and is connected on the output shaft 16 as the output key element.
Secondary sun wheel S2 passes through the first break B-1 can be connected with this mission case 11 in conjunction with the mode of throwing off with mission case 11.Support C2 (C3) passes through second clutch C-2 can be connected with this input shaft 15 in conjunction with the mode of throwing off with input shaft 15.And support C2 (C3) being connected with this mission case 11 in conjunction with the mode of throwing off with mission case 11, and only can use one-way engagement device F-1 card by the second break B-2.
The automatic transmission 10 of Gou Chenging as described above, throw off first to fourth clutch C-1～C-4, the first and second break B-1, B-2 by selective binding, selectivity connect or fixedly input shaft 15, output shaft 16, slow down with planetary pinion 20 and planetary gear set 21 each key element, can make advance 8 grades, laggard 2 grades gear than setting up.In Fig. 2, have under the situation of O in the clutch of corresponding each gear train, the field mark of break, if the mated condition of expression clutch and break blank, is then represented open mode.
Below, the action of each gear train is described.The speed change retaining is under the situation of P (parking) retaining and N (sky) retaining, because whole clutch C-1～C-4 and break B-1, B-2 is in the liberation state, cuts off the transmission of power of input shaft 15 and output shaft 16.
Under the situation of 1 speed of advancing, as shown in Figure 2, in conjunction with first clutch C-1, simultaneously in conjunction with one-way engagement device F-1.Therefore, deceleration inputs to the first sun gear S2 of planetary gear set 21 by first clutch C-1 with the deceleration rotation of the gear ring R1 of planetary pinion 20.And the deceleration rotation of the first sun gear S2 is passed through one-way engagement device F-1 via the further deceleration of support C2 (C3) that limits to the rotation of a direction, and inputs to gear ring R2, and output shaft 16 also just changes than deceleration with the gear of 1 speed.During engine braking, replace one-way engagement device F-1, the rotation of fixed support C2 (C3) in conjunction with the second break B-2.
Under the situation of 2 speed of advancing, in conjunction with first clutch C-1, in conjunction with the first break B-1.Therefore, deceleration inputs to the first sun gear S2 with the deceleration rotation of the gear ring R1 of planetary pinion 20 via first clutch C-1, and secondary sun wheel S3 is fixed by the first break B-1, so gear ring R2 and even output shaft 16 also just change with the gear ratio deceleration of 2 speed.
Under the situation of 3 speed of advancing, in conjunction with first and three-clutch C-1, C-3.Therefore, deceleration inputs to the first sun gear S2 with the deceleration rotation of the gear ring R1 of planetary pinion 20 via first clutch C-1, simultaneously input to secondary sun wheel S3 via three-clutch C-3, so the rotation of planetary gear set 21 one, the gear of 3 speed that gear ring R2 and even output shaft 16 obtain to slow down with the rotation of 20 pairs of input shafts 15 of planetary pinion with deceleration is than slowing down and just changeing.
Under the situation of 4 speed of advancing, in conjunction with first and four clutches C-1, C-4.Therefore, deceleration inputs to the first sun gear S2 with the deceleration rotation of the gear ring R1 of planetary pinion 20 via first clutch C-1, the rotation of slowing down simultaneously with the support C1 of planetary pinion 20 inputs to secondary sun wheel S3 via four clutches C-4, gear ring R2 and even output shaft 16 with the gear of 4 speed than just changeing.
Under the situation of 5 speed of advancing, in conjunction with the first and second clutch C-1, C-2.Therefore, deceleration inputs to the first sun gear S2 with the deceleration rotation of the gear ring R1 of planetary pinion 20 via first clutch C-1, the rotation of input shaft 15 simultaneously inputs to the direct-connected first and second support C2, C3 via second clutch C-2, so gear ring R2 and even output shaft 16 also just change with the gear ratio deceleration of 5 speed.
Under the situation of 6 speed of advancing, in conjunction with second and four clutches C-2, C-4.Therefore, via the support C1 that slows down with planetary pinion 20, the input rotation of input shaft 15 inputs to secondary sun wheel S3 via four clutches C-4, the rotation of input shaft 15 simultaneously inputs to the direct-connected first and second support C2, C3 via second clutch C-2, so the rotation of planetary gear set 21 and input shaft 15 one, gear ring R2 and even output shaft 16 with the gear of 6 speed than just changeing.
Under the situation of 7 speed of advancing, in conjunction with second and three-clutch C-2, C-3.Therefore, the rotation of input shaft 15 inputs to the direct-connected first and second support C2, C3 via second clutch C-2, slowing down simultaneously to rotate with the deceleration of the gear ring R1 of planetary pinion 20 inputs to secondary sun wheel S3 via three-clutch C-3, so gear ring R2 and even output shaft 16 also just change than speedup with the gear of 7 speed.
Under the situation of 8 speed of advancing, in conjunction with second clutch C-2, in conjunction with the first break B-1.Therefore, the rotation of input shaft 15 inputs to the direct-connected first and second support C2, C3 via second clutch C-2, secondary sun wheel S3 is fixed by the first break B-1, so gear ring R2 and even output shaft 16 also just change than speedup with the gear of 8 speed.
Under the situation of laggard 1 speed, in conjunction with the three-clutch C-3 and the second break B-2.Therefore, the rotation of input shaft 15 inputs to secondary sun wheel S3 via three-clutch C-3, the direct-connected first and second support C2, C3 are fixed by the second break B-2 simultaneously, so gear ring R2 and even output shaft 16 are with the deceleration of gear ratio and the counter-rotating of laggard 1 speed.
Under the situation of laggard 2 speed, in conjunction with the four clutches C-4 and the second break B-2.Therefore, via the support C1 that slows down with planetary pinion 20, the rotation of input shaft inputs to secondary sun wheel S3 via four clutches C-4, the direct-connected first and second support C2, C3 are fixed by the second break B-2 simultaneously, so gear ring R2 and even output shaft 16 are with the deceleration of gear ratio and the counter-rotating of laggard 2 speed.
Fig. 3 and Fig. 4 are that expression is slowed down with planetary pinion 20, the 3rd and the mechanism map of the concrete formation of four clutches C-3, C-4, the first break B-1.In with figure, input shaft 15 is supported in mission case 11, is fixed on the oil pump body 27 and stator axis 30 on the mission case 11 in revolvable mode.Stator axis 30 was pressed on the interior week of the shaft sleeve part 27a that is fixed on oil pump body 27.The outer circumferential side of the rear side end of stator axis 30 disposes and slows down with planetary pinion 20, by spline fitted the sun gear S1 that slows down with planetary pinion 20 can not be rotated simultaneously.
Be equipped with in the mission case 11: three-clutch C-3 and four clutches C-4 with second drum 32 that the round-ended cylinder shape is arranged with first drum 31 that the round-ended cylinder shape is arranged.Four clutches C-4 is contained in interior all sides of first drum 31.First drum 31 is bearing on the periphery of shroud member 33 of periphery of the shaft sleeve part 27a that is pressed into oil pump body 27 revolvably.Second drum 32 is bearing in along interior all side of first drum 31 and extends on the hub portion 31a that is provided with, and utilizes spline fitted described later portion 95 to cooperate in mode that can the one rotation simultaneously.
A plurality of sealing components are between the periphery of the interior week of the hub portion 31a of first drum 31 and shroud member 33.One end of the rear side of the hub portion 31a of first drum 31 is supported by metal liner shell-like main bearing 36 in the mode that can rotate, this metal liner shell-like main bearing 36 sets on the fixed muffle 35, and this fixed muffle 35 is entrenched in the periphery of rear side end of the shaft sleeve part 27a of oil pump body 27.It is monomer for a main bearing 36, for swivel bearing first drum 31 enough axial lengths is arranged.
In the other end (the front side end of vehicle heading) of hub portion 31a, be pressed into the auxiliary bearing 37 of axial length week than the metal liner shell-like of main bearing 36 weak points.Auxiliary bearing 37 exists with gap, and Spielpassung does not play a role as bearing on the periphery of shroud member 33 usually.And auxiliary bearing 37 is only in the power of the inclination of giving first drum, 31 additional relative flywheel moments etc., makes under first drum 31 tilts situation more than given along vehicle heading, brings into play the function of bearing with the periphery butt of shroud member 33.Thereby, compare with common the supporting under the situation of rousing with 2, because the capacity of auxiliary bearing 37 is diminished, can become minimal axial length.So, the face that is pressed into of first drum 31 that is pressed into auxiliary bearing 37 usefulness is shortened, suppress first drum 31 in axial maximization.
One end of the opening side of the peripheral part 31b of first drum 31 via three-clutch C-3 can be connected with this gear ring R1 in conjunction with the mode of disengagement with the gear ring R1 that slows down with planetary pinion 20.Three-clutch C-3 comprises: by with the separate plates 41 of peripheral part 31b spline fitted and the frictional fit key element and the first oil pressure servomechanism installation that constitute with the friction plate 42 of gear ring R1 spline fitted.The first oil pressure servomechanism installation comprises: in the first cylinder chamber 43 on the bottom that is formed at first drum 31 with the ccontaining first piston 44 of slidable mode, be provided in the canceller plate 91 on the hub portion 31a of first drum 31 and the return spring 45 that first piston 44 applies power constituted.
The interior perimembranous of ending canceller plate 91 with snap ring 90 restrictions and card in the periphery of the hub portion 31a of first drum 31 is moving of a side axially, the inner peripheral surface liquid seal ground of the peripheral part of canceller plate 91 and first piston 44 is chimeric, forms first decontamination chamber 92 between canceller plate 91 and first piston 44.Configuration applies power and return spring 45 that three-clutch C-3 is axially being opened to first piston 44 between canceller plate 91 and first piston 44.
Supply with elimination oil (lubricant oil) by the elimination oil supply hole 93 that shaft sleeve part 27a, shroud member 33 and first drum, 31 upper edge radial directions at oil pump body 27 form to first decontamination chamber 92.The oil that offers first decontamination chamber 92 is discharged to the outside from the elimination oil drain tank 91a on the interior perimembranous that is formed on canceller plate 91.First decontamination chamber 92 has the function of eliminating the centrifugal hydraulic pressure that produces with the oil in the first cylinder chamber 43.
The end of the opening side (rear side) of the peripheral part 32b of second drum 32 via four clutches C-4 can be connected with this support C1 in conjunction with the mode of disengagement with the support C1 that slows down with planetary pinion 20.Four clutches C-4 comprises: by with the separate plates 51 of interior all spline fitted of peripheral part 32b and the frictional fit key element and the second oil pressure servomechanism installation that constitute with the friction plate 52 of the periphery spline fitted that is incorporated into the clutch spider hub 56 on the support C1.The second oil pressure servomechanism installation comprises: in the second cylinder chamber 53 of the bottom that is formed at second drum 32 with the second ccontaining piston 54 of slidable mode, the canceller plate 97 of hub portion 31a that is provided in first drum 31 and the return spring 55 that second piston 54 is applied power.Interior all spline fitted of the peripheral part 32b of one end of second piston 54 and second drum 32, and be configured in the rear of four clutches C-4 frictional fit key element.Second piston 54 is configured in the outer circumferential side of the hub portion 32a of second drum 32 that has formed spline fitted portion 95.
Periphery in the rear side end of the hub portion 31a of first drum 31 sets canceller plate 97 with snap ring 96 and limits its moving of a side axially, the inner peripheral surface of the outside diameter of canceller plate 97 and second piston 54 is chimeric, forms second decontamination chamber 98 between the canceller plate 97 and second piston 54.Configuration applies power and return spring 55 that four clutches C-4 is opened at axle direction to second piston 54 between the canceller plate 97 and second piston 54.
Three-clutch C-3 comprises: described first drum 31, the frictional fit key element that is made of separate plates 41 and friction plate 42, the first cylinder chamber 43, first piston 44, return spring 45, form the oil pressure servomechanism installation of liquid seal shape with first drum 31 and first piston 44, be equipped with frictional fit key element, first piston 44, return spring 45 in first drum 31.
Equally, four clutches C-4 comprises: second drum 32, the frictional fit key element that is made of separate plates 51 and friction plate 52, second piston 54, return spring 55, form the oil pressure servomechanism installation of liquid seal shape with second drum 32 and second piston 54, be equipped with frictional fit key element, second piston 54, return spring 55 in second drum 32.
Pressure oil supply passage 60 by a plurality of the 3rd working oil supply holes 66 that on a plurality of second working oil supply holes 65 that form along radial direction in the equal angles position on the circumference of the hub portion 31a of first drum 31, circumference, form along radial direction in the equal angles position at the hub portion 32a of second drum 32 and, the ring-type oil circuit 67 that forms between two hub portion 31a, 32a constitutes, the second and the 3rd working oil supply hole 65,66 is interconnected via ring-type oil circuit 67.On shroud member 33, a pair of seal ring 99 is provided in the axle direction both sides of the second working oil supply hole 65.Seal ring on the hub portion 31a of first drum 31 (O type circle) 100 is provided in the axle direction both sides of the second and the 3rd working oil supply hole 65,66 respectively, forms ring-type oil circuit 67.
The periphery of the peripheral part 31b of first drum 31 via the first break B-1 can be connected with this mission case 11 in conjunction with the mode of disengagement with mission case 11.The first break B-1 uses by constituting with the separate plates 71 of interior all spline fitted of mission case 11 with frictional fit key element, oil pressure servomechanism installation that the friction plate 72 of the periphery spline fitted of the peripheral part 31b of first drum 31 constitutes.The oil pressure servomechanism installation be used in the grease chamber 73 that is formed in the mission case 11 with the ccontaining piston 74 of slidable mode and, return spring 75 that piston 74 is applied power constitutes.
The front end of piston 74 extends to the side of the frictional fit key element of the first break B-1.The grease chamber 73 of oil pressure servomechanism installation is connected with hydraulic control device by being formed on the illustrated oil circuit of omission in the mission case 11 etc., by the pressure oil of supplying with from hydraulic control device, piston 74 is revolted the spring force of return springs 75 and is slided the frictional fit key element of the frictional fit first break B-1.When stopping the pressure oil supply, remove the frictional fit of frictional fit key element with the spring force of return spring 75.
Form the supply passage 81 of lubricated usefulness on input shaft 15, the lubricant oil that sprays from diagram abridged oil pump is fed into supply passage 81 via hydraulic control device and supply hole 83.Supply passage 81 is communicated with multiple row supply holes 84,85, each supplying lubricating oil of giving in the mission case 11 via these supply holes 84,85.The lubricant oil that offers in the mission case 11 disperses to diametric foreign side because of action of centrifugal force, offers each position of slowing down with planetary pinion 20, clutch C-3, C-4 and break B-1, bearing etc.
Described first drum 31 passes through the combination of three-clutch C-3, and rotates with the gear ring R1 one of slowing down with planetary pinion 20.First drum 31 is by the combination of four clutches C-4, and together rotates with second drum 32 that slows down with the support C1 one rotation of planetary pinion 20.The 31 common times of first drum only are rotated via fixed muffle 35 on the shaft sleeve part 27a that is bearing in oil pump body 27 by main bearing 36, and auxiliary bearing 37 exists with gap Spielpassung not bring into play the bearing function on the periphery of shroud member 33.
, when first drum 31 rotates, under the situation of left and right vehicle wheel rotation, because first drum 31 phenomenon of (direction of vehicle driving) inclination axially takes place in the generation of flywheel moment.Like this, the external force that the axle direction of flywheel moment etc. tilts acts on first drum 31, under the situation of first drum, 31 inclination given angles, and the periphery of auxiliary bearing 37 butt shroud members 33, performance bearing function.Like this, auxiliary bearing 37 has the function of using under abnormal condition, does not need durability, can become minimal axle direction length.Because accepting the axle direction of first drum 31, auxiliary bearing 37 tilts, lever up the seal ring between oil circuit from working oil to the first cylinder chamber 43 that supply with so can prevent first drum 31, the pressure oil of supplying with to the first cylinder chamber 43 leaks, and the situation of the controlled reduction of the first oil pressure servomechanism installation takes place.
If use described embodiment, the main bearing 36 by the metal liner shell-like is supported in embedding in revolvable mode and on the fixed muffle 35 of the front end periphery of the shaft sleeve part 27a of oil pump body 27 week in the end of the hub portion 31a of first drum 31, it is monomer for a main bearing 36, for swivel bearing first drum 31 enough axle direction length is arranged, so the common time, only can be on the shaft sleeve part 27a of oil pump body 27 first drum, 31 swivel bearings with main bearing 36.The auxiliary bearing 37 of the metal liner shell-like of axle direction length weak point has been installed in the other end of shaft sleeve part 27a in week, auxiliary bearing 37 exists with gap Spielpassung on the periphery of shroud member 33, usually do not bring into play the function of bearing, so do not need durability as auxiliary bearing 37, can become minimal axial length.Therefore, though a plurality of supply passages to the first and second cylinder chambers of each oil pressure servomechanism installation of the third and fourth clutch C-3, C-4,43,53 supply pressures oil usefulness are arranged on the chimeric surface of hub portion 31a and shroud member 33, maximize at axle direction with the bearing device that supports it but can suppress first drum 31, and then can realize lightweight, the miniaturization of automatic transmission.
In described embodiment, illustrated and to have finished advance 8 grades, the automatic transmission of laggard 2 grades gear ratio, but the present invention does not limit such automatic transmission, can be applicable to the automatic transmission widely of the drum of useful bearing supporting.
In described embodiment, though with the La Weilveshi gear train that a small gear planetary pinion and double pinion planetary pinion are combined is that example has illustrated planetary gear set 21, but planetary gear set 21 of the present invention does not limit the La Weilveshi gear train, if a plurality of (more than 2) planetary planetary gear set is arranged, then can adopt all structures.
And then, in described embodiment, the periphery of the shaft sleeve part 27a of oil pump body 27 respectively embedding shroud member 33 and fixed muffle 35, via main bearing 36 an end swivel bearing of first drum 31 on fixed muffle 35, the other end at first drum 31 is provided with the auxiliary bearing 37 of Spielpassung on the periphery of shroud member 33, but shroud member 33 and fixed muffle 35 constitute the part of the cylinder support of claim item.Abolishing shroud member 33 and fixed muffle 35 also can directly be bearing in first drum 31 on the cylinder support (shaft sleeve part 27a).
Equally, the concrete structure of narrating in described embodiment only is an expression example of the present invention, and the present invention does not limit such concrete structure, can adopt all styles of certainly in the scope that does not break away from general idea of the present invention.
Utilizability on the industry
Automatic transmission of the present invention is applicable to that the travel direction to vehicle is provided in the rear of engine and has makes a plurality of clutches and brake in conjunction with breaking away from and speed change becomes the automatic transmission of multistage gear.
Claims (4)
1. automatic transmission, the direction of travel of vehicle is provided in the rear of motor relatively, this automatic transmission have makes a plurality of clutches and break in conjunction with, throw off and realize it is characterized in that the gear of multi-change speed,
This gear has:
The cylinder support;
The first oil pressure servomechanism installation, it has first drum and forms the first piston of first cylinder chamber with this first drum, and can operate in described a plurality of clutch one;
Main bearing, it is provided in the interior week of described first hub portion of rousing and is configured on the periphery of described cylinder support, and is supporting described first drum and described first drum can be rotated freely;
Auxiliary bearing, its be pressed in described first the drum hub portion interior week an end and with described cylinder support Spielpassung, only under the situation of the direction of travel inclination of vehicle, connect, and axial length is shorter than described main bearing with described cylinder support at described first drum.
2. according to the automatic transmission of claim 1 record, it is characterized in that,
Described cylinder support is to extend the shaft sleeve part that is provided with from mission case,
Described gear has the first working oil supply hole of supplying with oil circuit and forming in first working oil that forms on the shaft sleeve part of described mission case on the hub portion of described first drum,
Supply with between oil circuit and the described first working oil supply hole between described first working oil by making, supply with working oil to described first cylinder chamber at a pair of seal ring that sets on the shaft sleeve part of described mission case.
3. according to the automatic transmission of claim 2 record, it is characterized in that,
Described gear has:
The second oil pressure servomechanism installation, it has second drum and second piston, and this second piston forms the second cylinder chamber being provided on this second hub portion of rousing and with this second drum in the mode of sliding on the hub portion of this second drum;
Second working oil is supplied with oil circuit, and it is formed on the shaft sleeve part of described mission case;
The second working oil supply hole, it is formed on the hub portion of described first drum;
The 3rd working oil supply hole, it is formed on the hub portion of described second drum, and,
Described first rouses to the direction of travel rear of vehicle opening,
Described first drum matches in the mode of energy one rotation by spline fitted portion with described second drum, this spline fitted portion is made of second spline tooth that forms on first spline tooth that forms on the outer circumferential face of direction of travel rear side end of the vehicle of the hub portion of described first drum and the inner peripheral surface in the hub portion of described second drum
Described main bearing is provided on interior all sides of direction of travel rear side end of vehicle of hub portion of described first drum,
Supply with between oil circuit and the described second working oil supply hole between described second working oil by making at a pair of seal ring that sets on the shaft sleeve part of described mission case, and make a pair of seal ring that between the hub portion of described first hub portion of rousing and described second drum, sets between described second working oil supply hole and described the 3rd working oil supply hole, thereby supply with working oil to the described second cylinder chamber.
4. according to the automatic transmission of each record in the claim 1 to 3, it is characterized in that described main bearing is made of metal lining.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2005333383A JP4906046B2 (en) | 2005-11-17 | 2005-11-17 | Automatic transmission |
| JP333383/2005 | 2005-11-17 | ||
| PCT/JP2006/320268 WO2007058032A1 (en) | 2005-11-17 | 2006-10-11 | Automatic transmission |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101248294A CN101248294A (en) | 2008-08-20 |
| CN101248294B true CN101248294B (en) | 2011-01-26 |
Family
ID=38048425
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN200680031224.2A Active CN101248294B (en) | 2005-11-17 | 2006-10-11 | Hydraulic servo for a brake in an automatic transmission |
Country Status (4)
| Country | Link |
|---|---|
| JP (1) | JP4906046B2 (en) |
| CN (1) | CN101248294B (en) |
| DE (1) | DE112006002160B4 (en) |
| WO (1) | WO2007058032A1 (en) |
Families Citing this family (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US7862461B2 (en) * | 2007-07-05 | 2011-01-04 | Aisin Aw Co., Ltd. | Automatic transmission |
| JP5031591B2 (en) * | 2008-01-08 | 2012-09-19 | 本田技研工業株式会社 | transmission |
| JP5649173B2 (en) * | 2011-01-27 | 2015-01-07 | ダイハツ工業株式会社 | Planetary carrier |
| KR101610085B1 (en) * | 2011-09-22 | 2016-04-08 | 현대자동차 주식회사 | Hydraulic clutch |
| KR101566725B1 (en) * | 2011-09-27 | 2015-11-09 | 현대자동차 주식회사 | Hydraulic clutch |
| CN111692230B (en) * | 2020-05-25 | 2022-03-25 | 中国北方车辆研究所 | Low drag-torque type clutch suitable for high rotating speed |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2000220705A (en) * | 1998-09-01 | 2000-08-08 | Aisin Aw Co Ltd | Automatic transmission for vehicle |
| CN1502022A (en) * | 2001-12-25 | 2004-06-02 | ���Ű�����ʽ���� | Automatic transmission |
Family Cites Families (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH028540A (en) * | 1988-06-23 | 1990-01-12 | Aisin Aw Co Ltd | Automatic transmission |
| JPH02125131A (en) * | 1988-11-04 | 1990-05-14 | Aisin Aw Co Ltd | Structure for coast clutch and reverse clutch of automatic transmission |
| JPH02129445A (en) * | 1988-11-09 | 1990-05-17 | Aisin Aw Co Ltd | Torque transmission structure of automatic transmission |
| US4945782A (en) * | 1989-04-28 | 1990-08-07 | General Motors Corporation | Mounting device for securing a ring gear to a drive drum |
| JPH02296041A (en) * | 1989-05-10 | 1990-12-06 | Aisin Aw Co Ltd | Clutch device of automatic transmission |
| JPH0539866A (en) * | 1991-08-02 | 1993-02-19 | Toyota Motor Corp | Friction engagement device for automatic transmission |
| JP2003287090A (en) * | 2002-03-28 | 2003-10-10 | Jatco Ltd | Automatic transmission |
| JP2005240826A (en) * | 2004-02-24 | 2005-09-08 | Nsk Warner Kk | Support structure of multiple disk clutch and method for assembling multiple disk clutch and shaft with pump cover |
-
2005
- 2005-11-17 JP JP2005333383A patent/JP4906046B2/en not_active Expired - Fee Related
-
2006
- 2006-10-11 DE DE112006002160.5T patent/DE112006002160B4/en not_active Expired - Fee Related
- 2006-10-11 WO PCT/JP2006/320268 patent/WO2007058032A1/en active Application Filing
- 2006-10-11 CN CN200680031224.2A patent/CN101248294B/en active Active
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2000220705A (en) * | 1998-09-01 | 2000-08-08 | Aisin Aw Co Ltd | Automatic transmission for vehicle |
| CN1502022A (en) * | 2001-12-25 | 2004-06-02 | ���Ű�����ʽ���� | Automatic transmission |
Also Published As
| Publication number | Publication date |
|---|---|
| DE112006002160T5 (en) | 2008-06-05 |
| CN101248294A (en) | 2008-08-20 |
| DE112006002160B4 (en) | 2014-05-22 |
| WO2007058032A1 (en) | 2007-05-24 |
| JP2007139066A (en) | 2007-06-07 |
| JP4906046B2 (en) | 2012-03-28 |
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