CN1936361A

CN1936361A - Automatic speed changing device

Info

Publication number: CN1936361A
Application number: CNA2006100732842A
Authority: CN
Inventors: 北原铁郎; 土屋恒平
Original assignee: JATCO Ltd
Current assignee: Nissan Motor Co Ltd; JATCO Ltd
Priority date: 2005-09-21
Filing date: 2006-04-07
Publication date: 2007-03-28
Anticipated expiration: 2026-04-07
Also published as: JP2007085409A; CN100460711C; JP4350692B2

Abstract

Provided is an automatic speed changing device which makes sufficient lubrication while making the constitution of the transmission compact even when two cylinder rooms are arranged in the radial direction. The automatic speed changing device comprises a first brake, a pump cover; a first cylindrical part; a first cylinder room; a first piston; a lubricating oil supply port; and a connecting groove. The lubricating oil supply port is formed in the position between the first cylinder room and the first cylindrical part in the radial direction. Then the connecting groove connects the lubricating oil supply port to a spline.

Description

Automatic transimission

Technical field

The present invention relates to automatic transimission, particularly the lubricating structure of link component.

Background technique

As the multi-plate brake that disposes two automatic transmission diametrically, with the technology that forms as one with cylinder chamber and pump cover of pushing of these multi-plate brakes, the technology of record in the

patent documentation

1,2 is disclosed.

[patent documentation 1] spy opens flat 2-42239 communique

[patent documentation 2] spy opens flat 2-42240 communique

But, in above-mentioned prior art, owing to dispose two cylinder chamber diametrically side by side, therefore must be from the outer circumferential side that oil circuit extends to pump cover that rushes down of oil pump.Therefore, pump cover maximizes, in order to ensure with the gap of fluid torque converter, axial size may increase.In addition, in said structure, only return food tray, rush down oil and do not used effectively from the oil that rushes down of oil pump.

Summary of the invention

The present invention is conceived to above-mentioned problem and finishes, even its purpose is to provide a kind of also compactness of implementation structure of two cylinder chamber that disposed diametrically, can effectively utilize the automatic transimission that rushes down oil simultaneously.

In order to reach above-mentioned purpose, in automatic transmission of the present invention, comprising: first break, selectively fixing first rotatable member of planetary gear set; Pump cover is divided first accommodating chamber that holds fluid torque converter and second accommodating chamber that holds planetary gear set, becomes the cover of oil pump simultaneously; First cylindrical part is extended to the described second accommodating chamber side vertically from this pump cover, keeps the first clutch sheet of described first break by spline fitted in interior week; Second cylindrical part more is positioned at all sides than this first cylindrical part, extends to the described second accommodating chamber side vertically from described pump cover; First cylinder chamber more forms by internal side diameter ground than this first cylindrical part, produces the pressing force of described first break; First piston, have and common first extension part radially of dividing described first cylinder chamber of the part of the described second cylindrical part periphery, and from second extension part radially that described first cylinder chamber's radius vector extends outside, use this second radially extension part more pushing described first clutch sheet than described first cylindrical part by internal side diameter; The lubricant oil supplying mouth is formed in the radial position between described first cylinder chamber and described second cylindrical part on the position with the skew of described first cylinder chamber, in the described pump cover vertically to the described second accommodating chamber side supplying lubricating oil; And connectivity slot, this lubricant oil supplying mouth and described spline are communicated with.

Thereby, in the automatic transimission of the present application, can lubricate multi-plate brake expeditiously and can not cause radially increase.

Description of drawings

Fig. 1 is the frame diagram of the structure of 7 speed of advancing of FR type that embodiment 1 is reached in the expression automatic transmission that retreats 1 speed.

Fig. 2 is that 7 speed of advancing in expression embodiment's 1 the automatic transmission retreat the figure of the bridging work table of 1 speed.

Fig. 3 is the alignment chart of rotation halted state of the member of each gear that retreats 1 speed of 7 speed of advancing in expression embodiment's 1 the automatic transmission.

Fig. 4 only represents fluid torque converter in embodiment 1 the automatic transmission and near the sectional drawing first planetary pinion.

Fig. 5 is the front view of the pump cover in embodiment 1 the automatic transmission.

Fig. 6 is near the amplification profile of layout first planetary pinion in expression embodiment's 1 the automatic transmission.

Symbol description

GS1 first planetary gear set

GS2 second planetary gear set

G1 first planetary pinion

G2 second planetary pinion

G3 the third line star gear

G4 fourth line star gear

M1 first linking member

M2 second linking member

M3 the 3rd linking member

The C1 first clutch

The C2 second clutch

The C3 three-clutch

The B1 break

The B2 break

The B3 break

The B4 break

The B5 break

F1 first mono-directional overrun clutch

F2 second mono-directional overrun clutch

F3 the 3rd mono-directional overrun clutch

The Input input shaft

The Output output shaft

1 transmission case

2 pump covers

2a lubricant oil supplying mouth

The 2b connectivity slot

3 stator axis

9 oil pumps

21 first cylindrical part

21a, 21b be oil circuit radially

The 21c spline

22 second cylindrical part

The 22a slide part

23 the 3rd cylindrical part

24 end differences

34 oil circuits

41 first pistons

41d first is extension part radially

41e second is extension part radially

41f extends axially portion

43 first clutch sheets

51 second pistons

53 second clutch sheets

90 pump cases

The 91a internal gear

92 oil sealings

93 lubricating oil paties

94 axial lubrication roads

100 rush down the hole

200 oil circuits

410 first cylinder chamber

510 second cylinder chamber

CVU control valve assembly

The TC fluid torque converter

TCH fluid torque converter lid

TCH1 first accommodating chamber

H1 second accommodating chamber

Embodiment

Below, the best mode of realizing automatic transimission of the present invention is described based on embodiment shown in the drawings.

[embodiment 1]

Fig. 1 is the frame diagram of the structure of 7 speed of advancing of FR type that embodiment 1 is reached in the expression automatic transmission that retreats 1 speed.From input shaft Input lateral axis to output shaft Output side, by the arranged in order that the first planetary gear set GS1 (the first planetary pinion G1, the second planetary pinion G2), the second planetary gear set GS2 (the third line star gear G3 and fourth line star gear G4) arranged.In addition, as the friction link component, a plurality of clutch C1, C2, C3 and break B1, B2, B3, B4, B5 have been disposed.In addition, a plurality of mono-directional overrun clutch F1, F2, F3 have been disposed.

The first planetary pinion G1 is the single pinion type planetary pinion with first planetary wheel carrier PC1 of the first small gear P1 that the first sun gear S1, the first internal gear R1, supporting and two gear S1, R1 mesh.

The second planetary pinion G2 is the single pinion type planetary pinion with second planetary wheel carrier PC2 of the second small gear P2 that the second sun gear S2, secondary annulus R2, supporting and two gear S2, R2 mesh.

The third line star gear G3 is the single pinion type planetary pinion with the third line star wheel frame PC3 of the third pinion P3 that the 3rd sun gear S3, the 3rd internal gear R3, supporting and two gear S3, R3 mesh.

Fourth line star gear G4 is the single pinion type planetary pinion with fourth line star wheel frame PC4 of the fourth pinion P4 that the 4th sun gear S4, the 4th internal gear R4, supporting and two gear S4, R4 mesh.

Input shaft Input and secondary annulus R2 link, via inputs such as fluid torque converters from rotary driving force as the outer motor of the figure of driving source.

Output shaft Output and the third line star wheel frame PC3 link, via the outer final gear of figure etc. to driving wheel transmission output rotary driving force.

The first linking member M1 is the member with the first internal gear R1 and the second planetary wheel carrier PC2 and the binding of the 4th internal gear R4 one.

The second linking member M2 is the member with the 3rd internal gear R3 and the binding of fourth line star wheel frame PC4 one.

The 3rd linking member M3 is the member with the first sun gear S1 and the binding of the second sun gear S2 one.

The first planetary gear set GS1 is by constituting the first planetary pinion G1 and the second planetary pinion G2 by the first linking member M1 and the 3rd linking member M3 binding.In addition, the second planetary gear set GS2 is by constituting the third line star gear G3 and fourth line star gear G4 by second linking member M2 binding.

The first planetary gear set GS1 has from the torque input path of input shaft Input input secondary annulus R2.The torque of importing the first planetary gear set GS1 outputs to the second planetary gear set GS2 from the first linking member M1.

The second planetary gear set GS2 has from input shaft Input and imports the torque input path of the second linking member M2 and import the torque input path of the 4th internal gear R4 from the first linking member M1.The torque of importing the second planetary gear set GS2 outputs to output shaft Output from the third line star wheel frame PC3.In addition, three-clutch C3 separates, and the rotating speed of the 4th sun gear S4 is during greater than the 3rd sun gear S3, and independently rotating speed takes place for the 3rd sun gear S3 and the 4th sun gear S4.Thereby the third line star gear G3 and fourth line star gear G3 become the structure that links via the second linking member M2, reach independently gear ratio of each planetary pinion.

First clutch C1 optionally disconnects the clutch that links with the input shaft Input and the second linking member M2.

Second clutch C2 optionally disconnects the clutch that links with the 4th sun gear S4 and fourth line star wheel frame PC4.

Three-clutch C3 optionally disconnects the clutch that links with the 3rd sun gear S3 and the 4th sun gear S4.In addition, dispose the second mono-directional overrun clutch F2 between the 3rd sun gear S3 and the 4th sun gear S4.

Break B1 (second break that is equivalent to put down in writing in the technological scheme scope) is the break that the rotation of the first planetary wheel carrier PC1 is stopped.

The second break B2 is the break that the rotation of the 3rd sun gear S3 is stopped.

Break B3 (first break that is equivalent to put down in writing in the technological scheme scope) is the break that the rotation of the 3rd linking member M3 (the first sun gear S1 and the second sun gear S2) is stopped.

The 4th break B4 is the break that the rotation of fourth line star wheel frame PC4 is stopped.

The 5th break B5 is and the 3rd mono-directional overrun clutch F3 configuration in upright arrangement, disposes side by side with the second break B2 simultaneously, the break that the rotation of the 3rd sun gear S3 is stopped.

Shown in the bridging work table of Fig. 2, described each clutch C1, C2, C3 and each break B1, B2, B3, B4, B5 linked to be had each gear that retreats 1 speed by 7 speed of advancing to produce to link the outer speed change hydraulic pressure control device of figure of pressing (zero mark) or disjoining pressure (unmarked).In addition, as the speed change hydraulic pressure control device, adopt oil pressure control types, electronic control type, oil pressure+electronic control type etc.

Then, illustration.

[chronotropic action]

Fig. 2 is that expression embodiment's 1 automatic transmission retreats the figure of the bridging work table of 1 speed with 7 speed of advancing in the speed change gear, and Fig. 3 is the figure of alignment chart of rotation halted state of the member of the automatic transmission of representing embodiment 1 each gear of retreating 1 speed with 7 speed of advancing in the speed change gear.

＜1 speed 〉

As shown in Figure 2,1 speed obtains by the binding of break B1, the second break B2, the 5th break B5 and three-clutch C3.In addition, the first mono-directional overrun clutch F1 that is set up in parallel with break B1, the second mono-directional overrun clutch F2 that is set up in parallel with the 5th break B5 the 3rd mono-directional overrun clutch F3 that is provided with in upright arrangement, with three-clutch C3 also participate in transmission of torque.

In this 1 speed,, therefore slow down by the first planetary gear set GS1 from the rotation of input shaft Input input secondary annulus R2 owing to linked break B1.The rotation of this deceleration outputs to the 4th internal gear R4 from the first linking member M1.In addition, because the second break B2 and three-clutch C3 are bonded, the rotation of therefore importing the 4th internal gear R4 is slowed down by second planetary gear set, and exports from the third line star wheel frame PC3.

Promptly, shown in the alignment chart of Fig. 3,1 speed is stipulated the tie point of the break B1 of the output rotational delay of motor and the line that will link from the tie point of the second break B2 of the deceleration rotational delay of the first planetary gear set GS1 by linking, will be exported from output gear Output after the rotational delay of input shaft Input input.

The torque flow of this 1 speed (torque flow) is to break B1, the second break B2 (the 5th break B5 and the 3rd mono-directional overrun clutch F3), three-clutch C3, the first linking member M1, the second linking member M2, the 3rd linking member M3 effect torque.In other words, the first planetary gear set GS1 and the second planetary gear set GS2 participate in transmission of torque.

＜2 speed 〉

As shown in Figure 2,2 speed obtain by the binding of the second break B2, break B3, the 5th break B5 and three-clutch C3.In addition, the second mono-directional overrun clutch F2 that is set up in parallel with the 5th clutch B5 the 3rd mono-directional overrun clutch F3 that is provided with in upright arrangement, with three-clutch also participates in transmission of torque.

In this 2 speed,, therefore only slow down by the second planetary pinion G2 from the rotation of input shaft Input input secondary annulus R2 owing to linked break B3.The rotation of this deceleration outputs to the 4th internal gear R4 from the first linking member M1.In addition, because the second break B2 and three-clutch C3 are bonded, the rotation of therefore importing the 4th internal gear R4 is slowed down by second planetary gear set, and exports from the third line star wheel frame PC3.

Promptly, shown in the alignment chart of Fig. 3,2 speed are stipulated the tie point of the break B3 of the output rotational delay of motor and the line that will link from the tie point of the second break B2 of the deceleration rotational delay of the second planetary gear set GS2 by linking, will be exported from output gear Output after the rotational delay of input shaft Input input.

The torque flow of this 2 speed is to break B3, the second break B2 (the 5th break B5 and the 3rd mono-directional overrun clutch F3), three-clutch C3, the first linking member M1, the second linking member M2, the 3rd linking member M3 effect torque.In other words, the second planetary pinion G2 and the second planetary gear set GS2 participate in transmission of torque.

In addition, when the rising of 2 speed changes, break B1 is separated and begin the binding of break B3, thereby in the moment that the binding capacity of having guaranteed break B3 is guaranteed, the first unidirectional breakaway detents F1 separates by elder generation from 1 speed.Thereby, can realize that speed change precision regularly improves.

＜3 speed 〉

As shown in Figure 2,3 speed obtain by the binding of break B3, the second break B2, the 5th break B5 and second clutch C2.In addition, also participate in transmission of torque with the 5th clutch B5 the 3rd mono-directional overrun clutch F3 that is provided with in upright arrangement.

In this 3 speed,, therefore slow down by the second planetary pinion G2 from the rotation of input shaft Input input secondary annulus R2 owing to linked break B3.The rotation of this deceleration outputs to the 4th internal gear R4 from the first linking member M1.In addition, owing to linked second clutch C2, so the fourth line star gear G4 rotation that becomes one.In addition, owing to linked the second break B2, therefore the rotation of importing the 3rd internal gear R3 via the second linking member M2 from the fourth line star wheel frame PC4 with the rotation of the 4th internal gear R4 one is slowed down by the third line star gear G3, and exports from the third line star wheel frame PC3.Like this, fourth line star gear G4 participates in transmission of torque but does not participate in decelerating effect.

Promptly, shown in the alignment chart of Fig. 3,3 speed are stipulated the tie point of the break B3 of the output rotational delay of motor and the line that will link from the tie point of the second break B2 of the deceleration rotational delay of the second planetary pinion G2 by linking, will be exported from output gear Output after the rotational delay of input shaft Input input.

The torque flow of this 3 speed is to break B3, the second break B2 (the 5th break B5 and the 3rd mono-directional overrun clutch F3), second clutch C2, the first linking member M1, the second linking member M2, the 3rd linking member M3 effect torque.In other words, the second planetary pinion G2 and the second planetary gear set GS2 participate in transmission of torque.

In addition, when the rising of 3 speed changes, three-clutch C3 is separated and begin the binding of second clutch C2, thereby in the moment that the binding capacity of having guaranteed second clutch C2 is guaranteed, the second unidirectional breakaway detents F2 separates by elder generation from 1 speed.Thereby, can realize that speed change precision regularly improves.

＜4 speed 〉

As shown in Figure 2,4 speed obtain by the binding of break B3, the second break B2 and three-clutch C3.

In this 4 speed,, therefore only slow down by the second planetary pinion G2 from the rotation of input shaft Input input secondary annulus R2 owing to linked break B3.The rotation of this deceleration outputs to the 4th internal gear R4 from the first linking member M1.In addition, owing to linked second clutch C2 and three-clutch C3, the therefore second planetary gear set GS2 rotation that becomes one.Thereby the rotation former state of input fourth line star wheel frame R4 is exported from the third line star wheel frame PC3.

Promptly, shown in the alignment chart of Fig. 3,4 speed are stipulated the tie point of the break B3 of the output rotational delay of motor and the line that will link from the tie point of the second clutch C2 of the deceleration rotation former state output of the second planetary pinion G2 and three-clutch C3 by linking, will be exported from output gear Output after the rotational delay of input shaft Input input.

The torque flow of this 4 speed is to break B3, the second break B2, three-clutch C3, the first linking member M1, the second linking member M2, the 3rd linking member M3 effect torque.In other words, the second planetary pinion G2 and the second planetary gear set GS2 participate in transmission of torque.

In addition, when the rising of 4 speed changed, by earlier the second break B2 being separated and begin the binding of three-clutch C3, thereby in the moment that the binding capacity of having guaranteed three-clutch C3 is guaranteed, the 3rd mono-directional overrun clutch F3 separated from 3 speed.Thereby, can realize that speed change precision regularly improves.

＜5 speed 〉

As shown in Figure 2,5 speed obtain by the binding of first clutch C1, second clutch C2 and three-clutch C3.

In this 5 speed, owing to linked first clutch C1, so the second connection piece M2 is imported in the rotation of input shaft Input.In addition, owing to linked second clutch C2 and three-clutch C3, so the rotation of the third line star gear G2 one.Thereby the rotation former state of input shaft Input is exported from the third line star wheel frame PC3.

Promptly, shown in the alignment chart of Fig. 3,5 speed are stipulated by the line that the tie point of first clutch C1, the second clutch C2 of the output rotation of former state being exported motor and three-clutch C3 links, will be exported from output gear Output from the rotation former state of input shaft Input input.

The torque flow of this 5 speed is to first clutch C1, second clutch C2, three-clutch C3, the second linking member M2 effect torque.In other words, only the third line star gear G3 participates in transmission of torque.

＜6 speed 〉

As shown in Figure 2,6 speed obtain by the binding of first clutch C1, three-clutch C3 and break B3.

In this 6 speed, owing to linked first clutch C1, so the rotation of input shaft Input input secondary annulus, import the second linking member M2 simultaneously.In addition, owing to linked break B3, therefore the rotation of being slowed down by the second planetary pinion G2 outputs to the 4th internal gear R4 from the first linking member M1.In addition, owing to linked three-clutch C3, therefore the second planetary gear set GS2 is from the rotation of the third line star wheel frame PC3 output by the rotation regulation of the rotation of the 4th internal gear R4 and the second linking member M4.

Promptly, shown in the alignment chart of Fig. 3,6 speed by by the second planetary pinion G2 with the break B3 of the output rotational delay of motor, former state with the output rotation of motor be delivered to the second linking member M2 first clutch, constitute the line that the tie point of the three-clutch C3 of the second planetary gear set GS2 links and stipulate, will quicken the back from the rotation of input shaft Input input and export from output gear Output.

The torque flow of this 6 speed is to first clutch C1, three-clutch C3, break B3, the first linking member M1, the second linking member M2, the 3rd linking member M3 effect torque.In other words, the second planetary pinion G2 and the second planetary gear set GS2 participate in transmission of torque.

＜7 speed 〉

As shown in Figure 2,7 speed obtain by the binding of first clutch C1, three-clutch C3 and break B1 (the first mono-directional overrun clutch F1).

In this 7 speed, owing to linked first clutch C1, so the rotation of input shaft Input input secondary annulus, import the second linking member M2 simultaneously.In addition, owing to linked break B1, therefore the rotation of being slowed down by the first planetary gear set GS1 outputs to the 4th internal gear R4 from the first linking member M1.In addition, owing to linked three-clutch C3, therefore the second planetary gear set GS2 is from the rotation of the third line star wheel frame PC3 output by the rotation regulation of the rotation of the 4th internal gear R4 and the second linking member M4.

Promptly, shown in the alignment chart of Fig. 3,7 speed by by the first planetary gear set GS1 with the break B1 of the output rotational delay of motor, former state with the output rotation of motor be delivered to the second linking member M2 first clutch C1, constitute the line that the tie point of the three-clutch C3 of the second planetary gear set GS2 links and stipulate, will quicken the back from the rotation of input shaft Input input and export from output gear Output.

The torque flow of this 7 speed is to first clutch C1, three-clutch C3, break B1, the first linking member M1, the second linking member M2, the 3rd linking member M3 effect torque.In other words, the first planetary gear set GS1 and the second planetary gear set GS2 participate in transmission of torque.

＜back back speed 〉

As shown in Figure 2, back back speed obtains by the binding of three-clutch C3, break B1 and the 4th break B4.

In this back back speed, owing to linked break B1, the rotation of being slowed down by the first planetary gear set GS1 outputs to the 4th internal gear R4 from the first linking member M1.In addition owing to link three-clutch C3 and link the 4th break B4, therefore the second planetary gear set GS2 is from the rotation of the third line star wheel frame PC3 output by the fixedly regulation of the rotation of the 4th internal gear R4 and the second linking member M4.

Promptly, shown in the alignment chart of Fig. 3, back back speed by by the first planetary gear set GS1 with the break B1 of the output rotational delay of motor, the 4th break B4 that the rotation of the second linking member M2 is fixing, constitute the line that the tie point of the three-clutch C3 of the second planetary gear set GS2 links and stipulate, will export from output gear Output from the rotation of the input shaft Input input back of oppositely slowing down.

The torque flow of this back back speed is to three-clutch C3, break B1, the 4th break B4, the first linking member M1, the second linking member M2, the 3rd linking member M3 effect torque.In other words, the first planetary gear set GS1 and the second planetary gear set GS2 participate in transmission of torque.

Fig. 4 is in the concrete structure based on said frame figure and layout design, has only represented near the sectional drawing that the fluid torque converter TC and the first planetary pinion PG1 are.In addition, Fig. 5 is the front view of pump cover 2.

In fluid torque converter TC, be formed with the first accommodating chamber TCH1 that holds fluid torque converter TC.Fluid torque converter TC is provided with: with the converter cover CC that directly is attached to motor; CC is welded to connect with converter cover, in the inner peripheral surface soldering shell OS of pump impeller PI; Reception is from flowing of the oil of shell OS and turbine (turbine runner) TR of rotation; And the lock-up clutch LUC that turbine TR and converter cover CC one are linked.

On the shell OS, the driving claw OS1 that cooperates with internal gear (inner gear) 91a of oil pump 9 extends to pump cover 2 sides vertically.Turbine TR is provided with turbine hub (turbine hub) TH with input shaft Input spline fitted.In addition, be provided with to fluid torque converter TC side with the stator axis 3 of the interior Zhou Peihe of pump cover 2 and extend and the extension part 33 of the stator of supporting fluid torque converter TC.

Oil pump 9 is the gear pumps that are contained between pump case 90 and the pump cover 2, by meshing under the state of described internal gear 9a and outer gear 91b off-centre, thereby oil pressure takes place.Pump case 90 be provided with carry out and driving claw OS1 between oil sealing 92, lubricating oil path 93 and the axial lubrication road 94 of liquid seal.

Between the radial clearance of driving claw OS1 and extension part 33, be provided with and supply with the oil circuit 34 that torque-converters is pressed in being used for fluid torque converter TC.In addition, shown in pump cover 2 front views of Fig. 5, in control valve assembly CVU, be formed with and pressed the oil circuit 200 that supplies to oil circuit 34 by the torque-converters of pressure regulation.

Fig. 6 is near the enlarged portion sectional drawing the first planetary pinion PG1.Form the spline 1a that cooperates with second clutch sheet 53 and outer ring 61 described later in the opening of the input side end of transmission case 1, insert simultaneously and be fixed with pump cover 2.This pump cover 2 is divided first accommodating chamber TCH1 that holds fluid torque converter TC and the second accommodating chamber H1 that holds planetary gear set.

In the output shaft Output of pump cover 2 side, be provided with the 3rd cylindrical part 23, first cylindrical part 21, second cylindrical part 22 to internal side diameter from outside diameter.On the periphery of second cylindrical part 22, be provided with the end difference 24 of part wall thickness.This end difference 24 for roughly cylindric, is a pedestal shape in the periphery of second cylindrical part 22 from pump cover 2 sides protuberances.In end difference 24 peripheries,, be formed with the slide part 24a that extends axially 41f of portion and slip as described later second week in the extension part 41e radially.In addition, on the interior week of second cylindrical part 22, be provided with bearing hole 25.In addition, as the periphery of second cylindrical part 22, be formed with the described later first radially interior week of extension part 41d and the slide part 22a of slip at boundary vicinity with end difference 24.

Between the 3rd cylindrical part 23 and first cylindrical part 21, hold second piston 51 of break B1, and be formed with second cylinder chamber 510.In addition, the interior all sides in the 3rd cylindrical part 23 are provided with the spring space 51a that second piston 51 is shifted onto the spring 51b of pump cover 2 sides and kept this spring 51b.

Interior all sides in first cylindrical part 21 form spline 21c, this spline 21c are combined with axially being free to slide the first clutch sheet 43 of break B3.This first clutch sheet 43 is inserted into the clutch disk 45 that is engaged on the 3rd break wheel hub 46 described later with overlapping each other, and is fixed on axially by trip ring.In addition, insert belleville spring in the end of pump cover 2 sides of first clutch sheet 43.In addition, dispose radially oil circuit 21a, the 21b that is used for lubricant oil is imported radial outside on first cylindrical part 21 in the axial direction side by side.

As interior all sides of first cylindrical part 21, accommodate the first piston 41 of break B3 at the outer circumferential side of the end difference 24 and second cylindrical part 22.This first piston 41 has by first extension part 41d, second warp architecture that constitute of extension part 41e, the portion 41f of extending axially radially radially, the slide part 24a liquid seal ground that extends axially the 41f of portion and the outer circumferential side that is formed on end difference 24 slides, and is formed on the first radially slide part 22a liquid seal ground slip on week and second cylindrical part, 22 peripheries in the extension part 41d simultaneously.Thus, at the first extension part 41d and extend axially between the 41f of portion and to constitute first cylinder chamber 410 radially of second cylindrical part, 22 peripheries and end difference 24 and first piston 41.Usually, under the situation that constitutes cylinder chamber, how to hold piston, but then become the reason that intensity reduces as forming recess in the recess side, undesirable.Relative therewith, by on end difference 24, being provided with first cylinder chamber 410, can guarantee the intensity of pump cover 2 as protuberance.

The outer circumferential side of second cylindrical part 22 is provided with shifts first piston 41 onto the spring 41b of pump cover 2 sides and the spring fixture 41a of this spring of maintenance 41b.

Interior all sides of second cylindrical part 22 are provided with bearing hole 25, are pressed into fixed stator axle 3 in this bearing hole 25.On the periphery of this stator axis 3, be provided with wide diameter portion 32, with the collision location, end of this wide diameter portion 32 and second cylindrical part 22.In addition, at the sun gear support 31 that is provided with than these wide diameter portion 32 close output shaft sides at rotatably mounted the 3rd rotating member M3 of outer circumferential side.In addition, at rotatably mounted input shaft Input of the interior week of stator axis 3.In addition, support by needle bearing 8 between the interior week of sun gear support 31 and the input shaft Input.

In addition, as than end difference 24 outside diameters, be formed with lubricant oil supplying mouth 2a at the internal side diameter of first cylindrical part 21.In addition, around lubricant oil supplying mouth 2a, be formed with lubricant oil supplying mouth 2a and be formed on the connectivity slot 2b (with reference to Fig. 5) that the spline 21c of interior all sides of first cylindrical part 21 is communicated with.

The first sun gear S1 of the first planetary pinion G1 is linked the rotation that is useful on this first sun gear S1 (the 3rd rotating member M3) be fixed on the 3rd break wheel hub 46 on the pump cover 2.The 3rd break wheel hub 46 constitutes by being configured in the 46c of supporting cylinder portion, the bottom 46b that setting setting extends to radial outside, the spline part 46a that extends to the input shaft side from bottom 46b that dispose between described wide diameter portion 32 and the first planetary wheel carrier PC1 described later.

The first planetary wheel carrier PC1 of the first planetary pinion G1 is provided with the planetary wheel carrier support PC1a that is supported in the periphery of the 46c of supporting cylinder portion via lining with being free to slide, and forms in the axial direction spline part PC1b as the radial outside of the first planetary wheel carrier PC1.The first break wheel hub 56 and spline part PC1b spline fitted.Interior all sides at the first break wheel hub 56 form the interior all side spline 56b that cooperate with spline part PC1b, are formed with the outer circumferential side spline 56a that cooperates with clutch plate 55 at outer circumferential side.In addition, be fixed with the inner ring 62 of the first mono-directional overrun clutch F1 in the axial output shaft side one of the first break wheel hub 56.

Outer circumferential side at the first internal gear R1 of the first planetary pinion G1 forms spline, and cooperates to the binding parts 7 that the input shaft side is extended vertically from the second small gear planetary wheel carrier PC2.For the second small gear planetary wheel carrier PC2, linking at the outer circumferential side of the second planetary pinion G2 has the first linking member M1.

The first mono-directional overrun clutch F1 has the spline 61a that cooperates with spline 1a on the interior week that is formed on transmission case 1, is made of fixing outer race 61, inner race 62, the floor that is arranged between outer race 61 and the inner race 62 in the axial direction of trip ring 54.In addition, as the outer circumferential side of outer race 61, in transmission case 1, be provided be formed with in the food tray OP that holds control valve assembly CUV be used to flow out the oil that gushes rush down hole 100.

Be fixed with the sensor parts 63 of the second turn-sensitive device TS2 in the axial output shaft side of inner race 62.This sensor with parts 63 at the outer circumferential side of the first linking member M1 and the first linking member M1 overlappingly to axially extended extension part 63b.In extension part 63b, equally spaced be provided with a plurality of through hole 63a, detect the travel frequency of through hole 63a by the second turn-sensitive device TS2 according to the variation in magnetic field etc., and detect the rotating speed of the first planetary wheel carrier PC1 to circumferencial direction.

(about the lubricated path of lubricant oil)

Then, lubricated path based on the lubricant oil of said structure is described.In control valve assembly CUV, when pressing by pressure regulation to the torque-converters of supplying with in the fluid torque converter TC, as shown in Figure 5, the torque-converters pressure is fed near the axis central part via oil circuit 200.Be the position that internal gear 91a and driving claw OS1 cooperate near this axis central part, more than half oil is imported into oil circuit 34, but a part flows out by the gap of driving claw OS1 and pump case 90.The slip surface of the oil lubrication oil sealing 92 that flows out by this gap spews out into lubricating oil path 93 simultaneously.The oil that spews out into lubricating oil path 93 is fed into the lubricant oil supplying mouth 2a of pump cover 2 via axial lubrication road 94.

The lubricant oil that gushes from lubricant oil supplying mouth 2a flows through spline 21c via connectivity slot 2b.To on spline 21c via

radially oil circuit

21a, 21b second piston, 51 part supplying lubricating oils to the break B1 of radial outside configuration.And then the lubricant oil on the spline 21c is after having lubricated first clutch sheet 43, clutch plate 45, from the first planetary pinion side end of first cylindrical part 21 second clutch sheet 53,55 supplying lubricating oils to break B1.The lubricant oil that has lubricated break B1 is back to food tray OP side via the hole 100 of rushing down that is formed on the transmission case 1.

Below, enumerate action effect based on said structure.In addition, the record in () is used for and will makes clear with the corresponding of structure that the claim scope is put down in writing.

(1) the break B3 (first break) of the first sun gear S1 (first rotatable member), the second accommodating chamber H1 that holds the first accommodating chamber TCH1 of fluid torque converter TC and hold planetary gear set G1 are selectively fixed in division, have simultaneously: pump cover 2 becomes the cover of oil pump 9; First cylindrical part 21 is extended to the described second accommodating chamber H1 side vertically from pump cover 2, keeps the first clutch sheet 43 of break 3 by spline fitted in interior week; Second cylindrical part 22 is positioned at all sides than first cylindrical part 21, extends to the described second accommodating chamber H1 side vertically from described pump cover 2; First cylinder chamber 410 is formed on internal side diameter than first cylindrical part 21, and the pressing force of break B3 takes place; The first extension part 41d radially is with common first cylinder chamber 410 that divides of the part of second cylindrical part, 22 peripheries; And the second extension part 41e radially, extend outside from described first cylinder chamber 410 radius vectors, comprising: first piston 41, use second radially extension part 41e pushing first clutch sheet 43 than first cylindrical part, 21 internal side diameters; Lubricant oil supplying mouth 2a in the radial position between first cylindrical part 21 and second cylindrical part 22, is formed on the position with the skew of first cylinder chamber 410, in the pump cover 2 vertically to the described second accommodating chamber H1 side supplying lubricating oil; And connectivity slot 2b, lubricant oil supplying mouth 2a and spline 21c are communicated with.

That is, to pump cover 2 arrangement brake devices the time, the clutch plate and first cylinder chamber 410 are departed from configuration diametrically, pushing first clutch dish 43 than first cylindrical part, 21 internal side diameters, thereby can guarantee the gap radially of spline 21c and first piston 41.At this moment, by the lubricant oil supplying mouth being located between first cylinder chamber 410 and first cylindrical part 21, lubricant oil can be supplied to first clutch dish 43.In addition, by connectivity slot 2b is set, can be along spline 21c supplying lubricating oil efficiently.

(2) the break B1 (second break) that selectively fixes the first planetary wheel carrier PC1 (second rotatable member) is set, as than first cylindrical part, 21 outside diameters, than the axial planetary gear set side end of first cylindrical part 21 second clutch sheet 53 near planetary gear set side arrangement brake device B1 (second break).

Thereby, can from radially inner side to second clutch sheet 53 efficiently supply flow cross the lubricant oil of spline 21c.In addition, by on first cylindrical part 21, forming radially

oil circuit

21a, 21b, also can further improve lubricating efficiency from axially second clutch sheet 53 and clutch plate 55 being supplied with.

(3) as than first cylindrical part 21 (first cylindrical part) outside diameter, comprising: the 3rd cylindrical part 23 of extending to the second accommodating chamber side vertically from pump cover 2; Second cylinder chamber 510 that between first cylindrical part 21 and the 3rd cylindrical part 23, forms, the pressing force of break B1 (second break) takes place: be formed on first oil circuit 411 of supplying with oil pressure on the pump cover 2, to first cylinder chamber 410; And second oil circuit 5111 that is formed on the pump cover 2, second cylinder chamber 510 is supplied with oil pressure.

Can be easily the control valve assembly CVU of bottom of transmission case 1 and the oil pressure supply place binding that radially exists will be arranged on as the pump cover 2 of the longitudinal wall in the transmission case 1.Therefore, by only supplied with the oil pressure feed path of first cylinder chamber 410 and second cylinder chamber 510 by pump cover 2, the processing of oil circuit becomes easily, can guarantee property easy to manufacture.

(4) comprise be arranged on the pump cover 2, as from axis central part the fluid torque converter of supplying with oil pressure in the fluid torque converter TC being pressed the gap of the stator axis 3 of feed path and pump case 90 and being formed in the pump case 90 that holds oil pump 9, linking the lubricating

oil path

93,94 that fluid torque converter is pressed feed path and lubricant oil supplying mouth 2a.

As explanation in above-mentioned (3), therefore pump cover 2 constitutes a plurality of oil circuits (with reference to Fig. 5) owing to can easily link with oil pressure supply place that directly upwards exists.Thereby, be difficult to further constitute the oil circuit that lubricates usefulness.At this moment, by lubricating

oil path

93,94 is formed on pump case 90 sides, can utilize leakage that torque-converters presses supplying lubricating oil easily simultaneously.That is, owing to do not need to supply with the oil pressure of lubricated usefulness from other control valve assembly CVU yet, simplification that therefore can implementation structure.

The end difference 24 that (5) second cylindrical part 22 have enlarged-diameter in the axial first accommodating chamber TCH1 side, first piston 41 have from second radially the outer radius portion of extension part 41e extend to the first accommodating chamber TCH1 side vertically, with first 41f of the portion that extends axially that links of extension part 41d inside diameter radially, first cylinder chamber 410 is by the first slide part 22a of week and second cylindrical part, 22 peripheries in the extension part 41d radially, and the second radially interior week of extension part 41e and the slide part 24a division of end difference 24.

Usually, because cylinder chamber is formed in the recess etc., therefore may be because the wall thickness deficiency of recess cause intensity reduces.In addition, in the time of forming recess and guarantee wall thickness simultaneously, may cause axial increase.Especially, via stator axis 3 supporting input shaft Input, be the place of desired strength near the axle center of pump cover 2.For this,, can dispose first cylinder chamber 410 and can not cause that intensity reduces by covering end difference 24 ground configuration first piston 41 as protuberance.

Claims

1. an automatic transmission is characterized in that, comprising:

First break, this first break be fixing first rotatable member of planetary gear set selectively;

Pump cover, this pump cover are divided first accommodating chamber that holds fluid torque converter and second accommodating chamber that holds described planetary gear set, become the cover of oil pump simultaneously;

First cylindrical part, this first cylindrical part is extended to the described second accommodating chamber side vertically from described pump cover, and keeps the first clutch sheet of described first break by spline fitted in interior week;

Second cylindrical part, this second cylindrical part more is positioned at all sides than described first cylindrical part, and extends to the described second accommodating chamber side vertically from described pump cover;

First cylinder chamber, this first cylinder chamber more forms by internal side diameter ground than described first cylindrical part, produces the pressing force of described first break;

First piston, this first piston has and common first extension part radially of dividing described first cylinder chamber of the part of the described second cylindrical part periphery, and from second extension part radially that described first cylinder chamber's radius vector extends outside, use this second radially extension part more pushing described first clutch sheet than described first cylindrical part by internal side diameter;

The lubricant oil supplying mouth, described lubricant oil supplying mouth is formed in the radial position between described first cylinder chamber and described second cylindrical part on the position with the skew of described first cylinder chamber, and in the described pump cover vertically to the described second accommodating chamber side supplying lubricating oil; And

Connectivity slot, this connectivity slot is communicated with this lubricant oil supplying mouth and described spline.

2. automatic transmission as claimed in claim 1 is characterized in that,

Be provided with second break of second rotatable member of selectively fixing described planetary gear set,

As than described first cylindrical part more by outside diameter, compare the more close described planetary gear set side configuration of the second clutch sheet of described second break with the axial described planetary gear set side end of described first cylindrical part.

3. automatic transmission as claimed in claim 2 is characterized in that, comprising:

The 3rd cylindrical part, the 3rd cylindrical part as than described first cylindrical part more by outside diameter, extend to the described second accommodating chamber side vertically from described pump cover;

Second cylinder chamber, this second cylinder chamber are formed between described first cylindrical part and described the 3rd cylindrical part, to produce the pressing force of described second break;

First oil circuit, this first oil circuit is formed on the described pump cover, so that described first cylinder chamber is supplied with oil pressure; And

Second oil circuit, this second oil circuit is formed on the described pump cover, so that described second cylinder chamber is supplied with oil pressure.

4. as each described automatic transmission in the claim 1 to 3, it is characterized in that, comprising:

Fluid torque converter is pressed feed path, and this fluid torque converter presses feed path to be located on the described pump cover, with near the axis central part to supplying with oil pressure in the described fluid torque converter; And

Lubricating oil path, this lubricating oil path are formed on the pump case that holds described oil pump, to press feed path to be connected with described lubricant oil supplying mouth described fluid torque converter.

5. as each described automatic transmission in the claim 1 to 4, it is characterized in that,

Described second cylindrical part has end difference, and the described in the axial direction first accommodating chamber side diameter of this end difference is expanded,

Described first piston has the portion of extending axially, this extend axially portion from described second radially the outer diameter part of extension part extend to the described first accommodating chamber side vertically, and with described first radially the extension part inside diameter be connected,

Described first cylinder chamber is by described second slide part of week and the described second cylindrical part periphery in the extension part radially, and the described second radially interior week of extension part and the slide part division of described end difference periphery.