CN101248293B

CN101248293B - Hydraulic servo for a brake in an automatic transmission

Info

Publication number: CN101248293B
Application number: CN200680031175.2A
Authority: CN
Inventors: 冈田直也; 石井克久; 岩濑干雄; 太田博文; 野崎和俊; 本多敦
Original assignee: Aisin AW Co Ltd; Toyota Motor Corp
Current assignee: Aisin AW Co Ltd; Toyota Motor Corp
Priority date: 2005-11-17
Filing date: 2006-10-06
Publication date: 2010-07-07
Anticipated expiration: 2026-10-06
Also published as: DE112006002240B4; DE112006002240T5; CN101248293A; WO2007058028A1; DE112006002240B8; JP2007139065A; JP4906045B2

Abstract

The invention is capable of minimizing a phase shift of first and second oil holes when optionally installing a second drum in a first drum without indiscriminately increasing the number of oil holes. This pressure oil supply device of an automatic transmission supplies pressure oil to a hydraulic servo of a second clutch C-4 via a pressure oil supply passage 60 to the first drum 31 and the second drum 32. The pressure oil supply passage 60 is composed of a plurality of first oil holes 65 formed at an equal interval in the peripheral direction in the first drum 31, a plurality of second oil holes 66 at an equal angle interval on the circumference formed at an equal interval in the peripheral direction in the second drum 32 and an annular oil passage 67 formed in the first sand second drums and mutually communicating the first oil hole with the second oil hole. The number of other oil holes is increased more than the number of oil holes formed in one.

Description

Pressure oil supplier in the automatic transmission

Technical field

The present invention relates to the pressure oil supplier in a kind of automatic transmission of the oil servomotor that pressure oil is supplied to the clutch that constitutes automatic transmission.

Background technique

There is such clutch that constitutes by drum, piston, canceller etc. shown in patent documentation 1 in the automatic transmission.

And, 2 above clutches are arranged generally in order to realize a plurality of speed change gears.At this moment, as the means that realize the automatic transmission compactness, the multiple structure of considering clutch is as a kind of method that realizes.

In the automatic transmission that has been equipped with a plurality of clutches of forming multiple structure, usually, inboard drum can one be assembled on the drum in the outside rotatably by spline fitted, by two oilholes on the drum of drum outside being formed on and inboard, to the oil servomotor supply pressure oil that is contained in the clutch on the inboard drum.

In addition, generally be arranged on the circumference equally spacedly for the oilhole that is formed on the drum to oil servomotor supply pressure oil.

Patent documentation 1:JP spy opens flat 9-210088 communique (Fig. 2)

Summary of the invention

The problem that invention will solve

In this automatic transmission, in assembling during automatic transmission,, the inboard drum is assembled on the drum of the outside with arbitrarily angled by spline fitted etc.Phase deviation during at this moment because of assembling produces following problems, just on each platform, the feed path (supply length) of the oil servomotor supply pressure oil by the clutch of first and second oilholes in being contained in inboard drum is gone up the generation error, by this error, on the service time of oil servomotor supply pressure oil, producing error, producing error on the time in clutch engagement.For example shown in Figure 10 (A), the angular phase that is provided with 4

first oilholes

65 and 4 second oilhole 66, the first oilholes 65 and second oilhole 66 on circumference produces the phase deviations of maximum 45 degree.Consistent with the phase place of first oilhole 65 and second oilhole 66 (phase deviation is 0) situation is compared, and has increased the feed path (supply length) to oil servomotor supply pressure oil, and the clutch engagement time can produce delay.

In order to reduce the error of this clutch engagement time, in the time of on the inboard drum being assembled in outside drum, on sense of rotation, position, thereby make second oilhole 66 consistent with first oilhole 65, but exist in order to position, must rule on drum, assembling will be carried out chamfering, thus the problem that cost raises.

In view of described problem, the purpose of this invention is to provide the pressure oil supplier in a kind of automatic transmission, can excessively not increase oilhole quantity, the first and second oilhole phase deviations when second drum is assembled in first bulging the going up arbitrarily are contained in minimum degree.

The means that are used to deal with problems

In order to solve described problem, the invention of claim 1 record is the pressure oil supplier in a kind of automatic transmission, be equipped with a plurality of clutches and break in conjunction with or break away from and realize the gear of multi-change speed, this gear has: first oil servomotor and second oil servomotor, and this first oil servomotor has: first drum; Form the first piston of the first cylinder chamber with this first drum, this second oil servomotor has: be arranged on the periphery of hub portion of described first drum and with second drum of the first drum one rotation; With this second bulging second piston that forms the second cylinder chamber, by being arranged on the pressure oil supply passage on described first drum and described second drum, pressure oil is supplied to the described second cylinder chamber, it is characterized in that described pressure oil supply passage comprises: be formed on a plurality of first oilholes on described first drum in the first-class angle intervals of circumference; Be formed on a plurality of second oilholes on described second drum in the first-class angle intervals of circumference; By being arranged on ring-type oil circuit that pair of seal rings between described first and second drums forms and that described first oilhole and second oilhole are interconnected, in described first oilhole and second oilhole, than a kind of quantity of oilhole wherein, the quantity of another kind of oilhole is many.

The invention of claim 2 record is in claim 1, and the number of described first oilhole and second oilhole is non-multiple relation.

The invention of claim 3 record is in claim 2, and the quantity of any in described first oilhole and second oilhole is 4, and alternative quantity is 6.

The effect of invention

Invention according to claim 1 record, the pressure oil supply passage that is arranged on first drum and second drum comprises: be formed on described first and rouse a plurality of first oilholes of going up in the first-class angle intervals of circumference, be formed on described second and rouse a plurality of second oilholes of going up in the first-class angle intervals of circumference, by being arranged on ring-type oil circuit that pair of seal rings between described first and second drums forms and that described first oilhole and second oilhole are interconnected, described first oilhole is different with the second oilhole quantity, any oilhole quantity can be more than another kind of oilhole quantity, therefore, compare with the second oilhole quantity same case with first oilhole, can be reduced in the phase difference that second drum is assembled in first drum first oilhole and second oilhole when going up arbitrarily, supply with the deviation of the oily feed path (supply length) of oil by what phase difference caused to clutch in the time of can being reduced in assembling.

According to claim 2, because with a plurality of outside the multiple relation and relation that number is different, therefore form described first oilhole and second oilhole,, also can be reduced in the phase difference that second drum is assembled in first drum first oilhole and second oilhole when going up arbitrarily even oilhole quantity is few.

According to claim 3, because the quantity of any in described first oilhole and second oilhole is 4, alternative quantity is 6, therefore need not to wear and surpass the oilhole that needs, when being assembled in second drum on first drum arbitrarily, the phase difference of first oilhole and second oilhole can be contained less than 15 degree, be contained in very little numerical value.

Description of drawings

Fig. 1 is the schematic representation that shows automatic transmission of the present invention;

Fig. 2 is the view of the mated condition of break and clutch in each gears of automatic transmission in the displayed map 1;

Fig. 3 is the sectional view of pressure oil supplier that shows the automatic transmission of the invention process form;

Fig. 4 is the view that the part of Fig. 3 is amplified;

Fig. 5 is along the being seen sectional view of A-A line among Fig. 4;

Fig. 6 is the explanatory drawing that shows the relation of first oilhole shown in Figure 5 and second oilhole;

Fig. 7 is the explanatory drawing that shows the relation of first oilhole of other example of the present invention and second oilhole;

Fig. 8 is the explanatory drawing that shows the relation of first oilhole of other example of the present invention and second oilhole;

Fig. 9 is the explanatory drawing that shows the relation of first oilhole of other example of the present invention and second oilhole;

Figure 10 is the explanatory drawing that shows the relation of first oilhole of comparative example and second oilhole.

10 automatic transmission, 11 gearbox casings, 13 gears, 15 input shafts, 16 output shafts 20 slow down with planetary pinion 21 planetary gear set 27 oil pump body 27a hub portion 31 first drum 31a hub portion 32 second drum 32a hub portion

45,

cylinder chambers

53,73 44,54,74 pistons, 60 pressure oil supply passages 61 ring-

type oil circuits

62,63 oilholes 65 first oilholes 66 second oilholes 67 ring-type oil circuits

S1, S2, S3 sun gear C1, C2, C3 gear carrier R1, R2 gear ring

C-1 first clutch C-2 second clutch C-3 three-clutch

The C-4 four clutches B-1 first break B-2 second break

Embodiment

Hereinafter will describe example of the present invention with reference to the accompanying drawings.Fig. 1 shows the automatic transmission of for example using 10 in front engine rear driving type of vehicle.This automatic transmission 10 possesses hydraulic moment variator 12 and the gear 13 in the gearbox casing 11 that is installed on the car body.On the input shaft 15 that the pump impeller and the turbine of the output of motor by hydraulic moment variator 12 is input to automatic transmission 10.Speed change is carried out in 13 pairs of rotations from input shaft 15 inputs of gear, and outputs to the output shaft 16 that links to each other with driving wheel.Lock-up clutch 17 is arranged on the hydraulic moment variator 12.In addition in the present embodiment, with automatic transmission axially on the hydraulic moment variator side be called " the place ahead ", the output shaft side is called " rear ".

Gear 13 is included in input shaft 15 that gearbox casing 11 is supported on inherent coaxial successively, slow down and constitute with planetary pinion 20, by a plurality of planetary pinions planetary gear set 21, output shaft 16, the first～the four clutches C-1～C-4 and first and second break B-1 and the B-2.

To the rotation of input shaft 15 slow down and the deceleration that is sent to deceleration component with planetary pinion 20, comprising: be fixed on the gearbox casing 11 all the time and limited the sun gear S1 of rotation, directly be connected gear carrier C1 on the described input shaft 15, by gear carrier C1 supporting and with the first small gear 23A of sun gear S1 engagement, with by the second small gear 23B of the first small gear 23A engagement of gear carrier C1 supporting, with the gear ring R1 of second small gear 23B engagement.

Planetary gear set 21 is as an example, constitutes the Ravigneaux formula gear train that small gear planetary pinion and double pinion planetary pinion are combined.

The first sun gear S2 of the path of planetary gear set 21 can link to each other with the gear ring R1 that slows down with planetary pinion 20 in the mode that can cooperate or break away from by first clutch C-1.The second sun gear S3 in big footpath can link to each other with the gear ring R1 that slows down with planetary pinion 20 in the mode that can cooperate or break away from by three-clutch C-3, can link to each other with input shaft 15 in the mode that can cooperate or break away from the gear carrier C1 of planetary pinion 20 by four clutches C-4 and via slowing down simultaneously.Short and small gear 25 and first sun gear S2 engagement.Long small gear 26 and second sun gear S3 engagement are simultaneously with short and small gear 25 engagements.Short and small gear 25 and long small gear 26 can be rotated to support on respectively on the gear carrier C2 and C3 of direct connected structure.Gear ring R2 and long small gear 26 engagements link to each other with output shaft 16 as the output key element simultaneously.

The second sun gear S3 links to each other with gearbox casing 11 in the mode that can cooperate or break away from by the first break B-1.Gear carrier C2 (C3) links to each other with input shaft 15 in the mode that can cooperate or break away from by second clutch C-2, and gear carrier C2 (C3) links to each other with gearbox casing 11 in the mode that can cooperate or break away from by the second break B-2, can utilize overrunning clutch F-1 to block simultaneously and end.

The automatic transmission 10 of described mechanism is by cooperating disengaging with the first～the four clutches C-1～C-4, the first and second break B-1, B-2 selectively, selectively to input shaft 15, output shaft 16, slowing down is connected with planetary gear set 21 each key elements or fixes with planetary pinion 20, can realize thus advancing 8 grades, retreat 2 grades gear ratio.In Fig. 2, in the hurdle of the clutch corresponding, break during mark zero with each gear stage, the mated condition of expression clutch and break, blank expression cooperates relieving state.

Hereinafter will the operation of each gears be introduced.When the gearshift scope was P (parking) shelves scope and N (sky) shelves scope, all clutch C-1～C-4 and break B-1, B-2 were in the cooperation relieving state, so the transmission of the power of input shaft 15 and output shaft 16 is cut off.

Under the situation of 1 speed of advancing, as shown in Figure 2, when first clutch C-1 cooperated, overrunning clutch F-1 cooperated.Thereby deceleration is input in 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.The deceleration rotation of the first sun gear S2 further is decelerated via the gear carrier C2 (C3) that is restricted to unidirectional rotation under the effect of overrunning clutch F-1, and is imported into gear ring R2, and output shaft 16 also just changes than slowing down with 1 fast gear.And when engine braking, substitute overrunning clutch F-1, and the second break B-2 cooperates, and the rotation of gear carrier C2 (C3) is fixed.

Under the situation of 2 speed of advancing, first clutch C-1 cooperates, and the first break B-1 cooperates.Thereby deceleration is input to the first sun gear S2 with the deceleration rotation of the gear ring R1 of planetary pinion 20 by first clutch C-1, and the second sun gear S3 is fixed by the first break B-1, thereby gear ring R2 and even output shaft 16 also just change than slowing down with 2 fast gears.

Under the situation of 3 speed of advancing, first and three-clutch C-1, C-3 cooperate, thereby deceleration is input to the first sun gear S2 with the deceleration rotation of the gear ring R1 of planetary pinion 20 by first clutch C-1, be input to the second sun gear S3 by three-clutch C-3 simultaneously, therefore, the rotation of planetary gear set 21 one, gear ring R2 is extended down to output shaft 16, rotation by input shaft 15 is slowed down with planetary pinion 20 by deceleration, also just changes than slowing down with 3 fast gears.

Under the situation of 4 speed of advancing, first and four clutches C-1, C-4 cooperate, thereby deceleration is input to the first sun gear S2 with the deceleration rotation of the gear ring R1 of planetary pinion 20 by first clutch C-1, deceleration simultaneously is input to the second sun gear S3 with the rotation of the gear carrier C1 of planetary pinion 20 by four clutches C-4, gear ring R2 is extended down to output shaft 16, also just changes than slowing down with 4 fast gears.

Under the situation of 5 speed of advancing, the first and second clutch C-1, C-2 cooperate, thereby deceleration is input to the first sun gear S2 with the deceleration rotation of the gear ring R1 of planetary pinion 20 by first clutch C-1, the rotation of input shaft 15 simultaneously is input to the first and second gear carrier C2, the C3 that directly links to each other by second clutch C-2, therefore, gear ring R2 is extended down to output shaft 16, also just changes than slowing down with 5 fast gears.

Under the situation of 6 speed of advancing, second and four clutches C-2, C-4 cooperate, thereby by slowing down with the gear carrier C1 of planetary pinion 20, the input rotation of running shaft 15 is input to the second sun gear S3 by four clutches C-4, the rotation of input shaft 15 simultaneously is input to the first and second gear carrier C2, the C3 that directly links to each other by second clutch C-2, planetary gear set 21 and the rotation of input shaft 15 one, gear ring R2 is extended down to output shaft 16, also just changes than slowing down with 6 fast gears.

Under the situation of 7 speed of advancing, second and three-clutch C-2, C-3 cooperate, thereby the rotation of input shaft 15 is input to the first and second gear carrier C2, the C3 that directly links to each other by second clutch C-2, the deceleration rotation of the gear ring R1 of planetary pinion 20 is input to the second sun gear S3 by three-clutch C-3, thereby, gear ring R2 is extended down to output shaft 16, also just changes than speedup with 7 fast gears.

Under the situation of 8 speed of advancing, second clutch C-2 cooperates, and the first break B-1 cooperates.Thereby the rotation of input shaft 15 is input to the first and second gear carrier C2, the C3 that directly links to each other by second clutch C-2, the second sun gear S3 is fixed by the first break B-1, thereby gear ring R2 is extended down to output shaft 16, also just changes than speedup with 8 fast gears.

Under the situation that retreats 1 speed, the three-clutch C-3 and the second break B-2 cooperate.Thereby the rotation of input shaft 15 is input to the second sun gear S3 by three-clutch C-3, the first and second gear carrier C2, the C3 that directly links to each other is fixed by the second break B-2 simultaneously, thereby gear ring R2 is extended down to output shaft 16 to retreat 1 fast gear than slowing down and counter-rotating.

Under the situation that retreats 2 speed, the four clutches C-4 and the second break B-2 cooperate.Thereby by slowing down with the gear carrier C1 of planetary pinion 20, the rotation of input shaft is input to the second sun gear S3 by four clutches C-4, the first and second gear carrier C2, the C3 that directly links to each other is fixed by the second break B-2 simultaneously, thereby, gear ring R2 is extended down to output shaft 16, to retreat 2 fast gears than slowing down and counter-rotating.

Fig. 3 and 4 shows the view of deceleration with the concrete structure of planetary pinion 20, third and fourth clutch-3, C-4, the first break B-1.In described figure, input shaft 15 can be supported in gearbox 11 with rotating freely, be fixed on the oil pump body 27 and stator axis 30 on the gearbox 11.Stator axis 30 was pressed on the interior week of the hub portion 27a that is fixed on oil pump body 27.Slowing down is arranged on the outer circumferential side of rear side end of stator axis 30 with planetary pinion 20, and simultaneously, deceleration can not be rotated because of spline fitted with the sun gear S1 of planetary pinion 20.

In gearbox 11, be equipped with: have first drum 31 that the round-ended cylinder shape is arranged three-clutch C-3 and, have a four clutches C-4 of second drum 32 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 can be supported on the periphery of the housing part 33 on the hub portion 27a periphery that is pressed into oil pump body 27 with rotating freely.And second drum 32 by along the hub portion 31a supporting that is set to all sides in first drum 31, simultaneously can the one cooperation by aftermentioned spline fitted portion 95.

Between the periphery of the interior week of the hub portion 31a of first drum 31 and housing part 33, be provided with a plurality of sealed members.Rear side one end of the hub portion 31a of first drum 31 can rotate freely by main bearing 36 supportings, this main bearing 36 is arranged on the fixed muffle 35 on the periphery of rear side end of the hub portion 27a that at oil pump body 27 by embedding.Main bearing 36 has enough length in the axial direction, can be rotated supporting to first drum 31 with monomer structure.

In addition, the axial length auxiliary bearings 37 shorter than main bearing 36 were pressed in the front side end of hub portion 31a in week, and auxiliary bearing 37 keeps with gap Spielpassung can not bring into play the function of plain bearing on the periphery of housing part 33.Only when first drum 31 tilted to surpass given degree vertically, auxiliary bearing 37 contacted with the periphery of housing part 33, performance bearing function.

Opening side one end of the peripheral part 31b of first drum 31 can link to each other with the gear ring R1 that slows down with planetary pinion 20 in the mode that can break away from cooperation by three-clutch C-3.Three-clutch C-3 is made of the frictional fit key element and first oil servomotor, and the friction plate 42 on gear ring R1 constitutes this frictional fit key element at demarcation strip on the peripheral part 31b 41 and spline fitted by spline fitted.First oil servomotor comprises: can be contained in first piston 44 in the first cylinder chamber 43 that is formed on first drum, 31 bottoms slidably, be arranged on elimination plate 91 on the hub portion 31a of first drum 31, first piston 44 applied the Returnning spring 45 of elastic force.

Under the effect of stop ring 90, the interior perimembranous of eliminating plate 91 is on an axial direction mobile only blocks periphery at the hub portion 31a of first drum 31 controlledly.The peripheral part liquid of eliminating plate 91 is thickly chimeric with the inner peripheral surface of first piston 44, and is eliminating the formation first releasing chamber 92 between plate 91 and the first piston 44.Returnning spring 45 is arranged between elimination plate 91 and the first piston 44, vertically first piston 44 is applied elastic force, thereby three-clutch C-3 is opened wide.

First removes chamber 92 by separating oil removing supply hole 93 on the hub portion 27a that radially is formed on oil pump body 27, housing part 33 and first drum 31, supplies with and separates oil removing (lubricant oil).Supply to first oil removing of separating of removing chamber 92 and eliminate in the plate 91 separating oil removing drain tank 91a and be discharged to the outside on the perimembranous by being formed on.First removes chamber 92 has the function of elimination by the centrifugal oil pressure that oil produced in the first cylinder chamber 43.

First piston 44 is along the interior Zhou Yanshen of first drum, 31 peripheral part 31b, and its front end is provided with corresponding to the side of the frictional fit key element of three-clutch C-3.The supply passage 47 of the first cylinder chamber 43 by being made up of the oilhole on the hub portion 31a that is respectively formed at first drum 31, the housing part 33 of oil servomotor is communicated with oil circuit on the hub portion 27a that is formed on oil pump body 27.The oil circuit that is formed on the hub portion 27a links to each other with hydraulic pressure control device not shown in the figures, the pressure oil that utilization is supplied with by hydraulic pressure control device, the elastic force that first piston 44 is resisting Returnning spring 45 slides, and carries out frictional fit with the frictional fit key element of three-clutch C-3.If stop supply pressure oil, then under the effect of the elastic force of Returnning spring 45, the frictional fit of frictional fit key element is disengaged.

Second drum 32 is arranged on the inside of the first piston 44 of three-clutch C-3.Be arranged on interior all sides that hub portion 32a on the hub portion 31a of first drum 31 is set at second drum 32, peripheral part 32b is set at outer circumferential side.As shown in Figure 4, on the interior week of the rear side end of the hub portion 32a of second drum 32, be formed with internal spline 32c.External splines 31c spline fitted on the periphery of front side end of this internal spline 32c and the hub portion 31a that is formed on first drum 31.Constitute spline fitted portion 95 by first spline tooth formed by external splines 31c with by second spline tooth that internal spline 32c forms.

Opening side (rear side) end of the peripheral part 32b of second drum 32 is connected with the gear carrier C1 that slows down with planetary pinion 20 in the mode that can engage, break away from by four clutches C-4.Four clutches C-4 comprises the frictional fit key element and second oil servomotor, and this frictional fit key element is made of the spline fitted separating plate on week 51 and spline fitted friction plate 52 on the periphery of the clutch spider hub 56 that combines with gear carrier C1 in peripheral part 32b.Second oil servomotor comprises: be contained in second piston 54 in the second cylinder chamber 53 that is formed on second drum, 32 bottoms slidably, be arranged on elimination plate 97 on the hub portion 31a of first drum 31, second piston 54 applied the Returnning spring 55 of elastic force.One end spline fitted of second piston 54 is arranged on the rear of the frictional fit key element of four clutches C-4 on the interior week of the peripheral part 32b of second drum 32.Second piston 54 is arranged on the outer circumferential side of the hub portion 32a of second drum that is formed with spline fitted portion 95.

Under the effect of stop ring 96, eliminate on plate 97 is arranged on the periphery of hub portion 31a rear side end from first drum 31 to mobile being limited of an axial direction.The outside diameter of elimination plate 97 and the inner peripheral surface of second piston 54 are chimeric, formed second and remove chamber 98 between the elimination plate 97 and second piston 54.Between the elimination plate 97 and second piston 54, be provided with vertically second piston 54 is applied the Returnning spring 55 that makes the open such elastic force of four clutches C-4.

The second cylinder chamber 53 of oil servomotor, by being formed on first and second drums 31, each hub portion 31a of 32, pressure oil supply passage 60 between the 32a and be formed on the fixed muffle 33 ring-type oil circuit 61 and, be respectively formed at the oilhole road 62 on the hub portion 27a of oil pump body 27, link to each other with hydraulic pressure control device not shown in the figures.

Pressure oil supply passage 60 comprises as shown in Figure 5: towards the hub portion 31a that radially is located in first drum 31 go up simultaneously along a plurality of first oilholes 65 that circumferentially form equally spacedly, by go up simultaneously with respect to a plurality of second oilholes 66 that circumferentially form equally spacedly towards the hub portion 32a that radially is located in second drum 32, at two hub portion 31a, ring-type oil circuit 67, the first oilholes 65 and second oilhole 66 that are formed by pair of seal rings between the 32a are interconnected by ring-type oil circuit 67.

The periphery of the peripheral part 31b of first drum 31 is connected with gearbox casing 11 in the mode that can engage, break away from via the first break B-1.The first break B-1 is made of frictional fit key element and oil servomotor, and this frictional fit key element is made up of the spline fitted demarcation strip on week 71 and spline fitted friction plate 72 on the peripheral part 31b of first drum 31 in gearbox casing 11.Oil servomotor by can be contained in slidably in the cylinder chamber that is formed on the gearbox casing 11 73 piston 74 and, Returnning spring 75 that piston 74 is applied elastic force constitutes.

The front end of piston 74 extends to the side of the frictional fit key element of the first break B-1.The cylinder chamber 73 of oil servomotor links to each other with hydraulic pressure control device by being formed on oil circuit not shown in the figures on the gearbox casing 11 etc., under the effect of the pressure oil that hydraulic pressure control device is supplied with, the elastic force that piston 74 is resisting Returnning spring 75 slides, with the frictional fit key element frictional fit of the first break B-1.In case stop supply pressure oil, then under the effect of the elastic force of Returnning spring 75, the frictional fit of frictional fit key element will be disengaged.

Be formed with the lubricated supply passage 81 of using on input shaft 15, the lubricant oil of being discharged by oil pump not shown in the figures supplies in the supply passage 81 by hydraulic pressure control device and supply hole 83.A plurality of supply holes 84,85 are communicated with supply passage 81, by described supply hole 84,85, lubricant oil are supplied to various piece in the gearbox casing 11.The lubricant oil that supplies in the gearbox casing 11 disperses to radius foreign side under centrifugal action, supplies to slow down with each positions such as planetary pinion 20, clutch C-3, C-4 and the first break B-1, bearings.

Fig. 6 is the view of the position relation of a plurality of second oilholes 66 on the circumference on a plurality of first oilholes 65 on the circumference that shows on the hub portion 31a be formed on described first drum 31 and the hub portion 32a that is formed on second drum 32.For the ease of understanding, represent first oilhole 65 by white circle, represent second oilhole 66 by black circles.As shown in Figure 6, the circumference equal intervals formed 6 first oilholes 65, and, the circumference equal intervals formed 4 second oilholes 66

When assembling, second drum 32 with arbitrarily angled phase place spline fitted on first drum 31, but number combination by described first oilhole 65 and second oilhole 65, even under the most abominable combination condition, at least on 2 positions on the circumference, phase difference (phase deviation) θ 1 that can make two

oilholes

65,66 is less than 15 degree.

Thereby by hydraulic pressure control device not shown in the figures, by being formed on supply hole 63 on the input shaft 15, being formed on the oil circuit 62 on the hub portion 27a of oil pump body 27 and being formed on ring-type oil circuit 61 on the retaining ring 33, pressure oil is assigned in 6 first oil circuits 65 on the circumference.The pressure oil that is assigned in first oil circuit 65 is assigned in 4 second oil circuits 66 on the circumference by being formed on the ring-type oil circuit 67 on weeks in second drum 32, supplies in the second cylinder chamber 53 of second oil servomotor.

At this moment, even the pressure oil by first oil circuit 65 just can arrive second oil circuit 66 at the θ 1 (15 degree) that also only flows in a circumferential direction under the maximum case in ring-type oil circuit 67, thereby, can reduce the deviation of the feed path (supply length) of pressure oil.

Because first oilhole 65 in the time of can being assembled in second drum 32 on first drum 31 arbitrarily and the phase deviation of second oilhole 66 are contained in inferior limit, therefore can reduce when assembling by the oil servomotor of the caused four clutches C-4 of phase deviation and supply with the deviation of the oily feed path (supply length) of oil to the second cylinder chamber 53, the caused frictional fit key element of phase deviation cooperates the deviation of time in the time of can reducing by assembling.

And at least on 2 positions on the circumference, the phase place of first oilhole 65 and second oilhole 66 conforms to, if first oilhole 65 that can be by these 2 positions and second oilhole 66 are to second cylinder, the 54 supply pressure oil of oil servomotor, the problems such as response delay that oil servomotor then can not occur, even thereby the phase deviation of first oilhole 65 outside described 2 positions on the circumference and second oilhole 66 is big, also no problem.

Example as a comparison, Figure 10 (A) shows the situation the when quantity of first and second oilholes 65 and 66 all is 4, Figure 10 (B) shows the situation the when quantity of first and second oilholes 65 and 66 all is 6, when being 4, the maximum phase deviation that produces 45 degree, when being 6, the maximum phase deviation that produces 30 degree.Thereby the deviation of the feed path (supply length) of the caused oil of phase deviation during by assembling increases, and the cooperation time of frictional fit key element can produce deviation.

Self-evident, if 4 situations of Figure 10 (A) and 6 situations of Figure 10 (B) are compared, when first oilhole 65 and second oilhole 66 respectively are 6, can reduce phase deviation.But make the undue increase of oilhole quantity will cause that processing cost increases.And because of the oilhole that is worn increases, the reduction in strength of drum is therefore in order to compensate reduction in strength.Must increase the wall thickness of drum, cause that overall weight increases.Thereby importantly can not be only by making the increase of oilhole quantity reduce the phase deviation of first oilhole 65 and second oilhole 66.

Fig. 7～9th, the view of other example of demonstration the present invention, wherein, first oilhole 65 is different with the compound mode of second oilhole 66.

Under combined situation shown in Figure 7, first oilhole 65 and second oilhole 66 are respectively 8 and 4, in the case, the phase difference θ 2 of first oilhole 65 when being assembled in second drum 32 on first drum 31 arbitrarily and second oilhole 66 is being to the maximum on 2 positions on the circumference below 22.5 degree at least.But in this embodiment, because the quantity (8) of first oilhole 65 is multiples of the quantity (4) of second oilhole 66, thereby, when the phase place of second oilhole 66 phase place in the centre of 2 first oilholes 65, the phase place of all second oilholes 66 is all in the middle of the phase place of first oilhole 65, with the quantity of first oilhole 65 shown in Figure 6 and second oilhole 66 is respectively that 6 situations with 4 are compared, though first oilhole increases, it is big that phase difference θ also becomes.Thereby the relation of the quantity of first oilhole 65 and second oilhole, 66 quantity had better not be the relation of multiple.

Under combined situation shown in Figure 8, the quantity of first oilhole 65 is odd numbers, and the quantity of second oilhole 66 is even numbers, specifically, the first-class angular interval of circumference 5 first oilholes 65 are set, the first-class angular interval of circumference 4 second oilholes 66 are set.

Under combined situation shown in Figure 9, the quantity of first oilhole 65 and second oilhole 66 all is odd numbers, the first-class angular interval of circumference 5 first oilholes 65 are set, the first-class angular interval of circumference 3 second oilholes 66 are set.

Under situation shown in Fig. 8 and 9, though the configuration of oilhole is point symmetry not, become uneven point in a circumferential direction, different with Fig. 6 and the situation that respectively is provided with the even number oilhole shown in Figure 7, but aspect the phase difference θ 3, the θ 4 that are reduced in first oilhole 65 when being assembled in second drum 32 on first drum 31 arbitrarily and second oilhole 66, can obtain identical effect.

According to described example, by being formed on first oilhole 65 and second oilhole 66 that is formed on second drum 32 on first drum 31, when pressure oil is supplied to the oil servomotor of four clutches C-4, because the quantity of first oilhole 65 and second oilhole 66 is even number and quantity differs from one another, for example the first-class angular interval of circumference 6 first oilholes 65 are set, the first-class angular interval of circumference 4 second oilholes 66 are set, first oilhole 65 in the time of therefore can being assembled in second drum 32 on first drum 31 arbitrarily and the phase difference of second oilhole 66 are contained in the inferior limit.Thereby can reduce the deviation by the oily feed path (supply length) of the second cylinder chamber 54 of the oil servomotor of the caused four clutches C-4 of phase deviation in when assembling, the caused frictional fit key element of phase deviation cooperates the deviation of time in the time of can reducing by assembling.

In addition, when first oilhole 65 and second oilhole 66 can be with the such multiple numbers combinations of 8 and 4, also can be with 5 and 4 such odd and even number combinations, but also can make up each other with 5 and 3 such odd numbers, compare with the quantity same case of second oilhole 66 with first oilhole 65, can reduce deviation from the oily feed path (supply length) of oil to the second cylinder chamber 54 that when assembling, supply with by the oil servomotor of the caused four clutches C-4 of phase deviation.

And in described example, be introduced though mostly be example with the quantity of first oilhole 65 than the quantity of second oilhole 66, which does not manyly influence design to the quantity of the quantity of first oilhole 65 and second oilhole 66, does not produce difference on effect yet.

In described example, can realize advancing 8 grades, the automatic transmission that retreats 2 grades gear ratio are described, but the present invention is not limited thereto, can be between 2 drums extensive use in the automatic transmission of supply pressure oil.

And in described example, is that example describes with the cured civilian Nao formula gear train by single small gear planetary pinion and the combination of double pinion planetary pinion as planetary gear set 21, but planetary gear set 21 of the present invention is not defined as cured civilian Nao formula gear train, as long as have a plurality of (more than 2) planetary planetary gear set, just can adopt.

And because one such as stator axis 30, oil pump body 27, housing part 33 are combined on the gearbox casing 11, thereby stator axis 30, oil pump body 27, housing part 33 etc. constitute the part of gearbox casing 11.

Concrete structure described in this external described example only is an example of the present invention, and the present invention is not limited to this concrete structure, and is self-evident, in the scope that does not break away from purport of the present invention, can carry out various improvement.

Utilizability on the industry

Pressure oil feedway in the automatic transmission of the present invention be applicable to be equipped with a plurality of clutches and brake cooperate break away from and a plurality of gears can speed change the automatic transmission of gear.

Claims

1. the pressure oil supplier in the automatic transmission,

Be equipped with a plurality of clutches and break in conjunction with or break away from and realize the gear of multi-change speed,

This gear has first oil servomotor and second oil servomotor, and this first oil servomotor has: first drum; Form the first piston of the first cylinder chamber with this first drum, this second oil servomotor has: be arranged on the periphery of hub portion of described first drum and with second drum of the first drum one rotation; With this second bulging second piston that forms the second cylinder chamber,

By being arranged on the pressure oil supply passage on described first drum and described second drum, pressure oil is supplied to the described second cylinder chamber, it is characterized in that,

Described pressure oil supply passage comprises:

Be formed on a plurality of first oilholes on described first drum in the first-class angle intervals of circumference;

Be formed on a plurality of second oilholes on described second drum in the first-class angle intervals of circumference;

By being arranged on ring-type oil circuit that pair of seal rings between described first and second drums forms and that described first oilhole and second oilhole are interconnected,

In described first oilhole and second oilhole, than a kind of quantity of oilhole wherein, the quantity of another kind of oilhole is many.

2. the pressure oil supplier in the automatic transmission according to claim 1 is characterized in that, the number of described first oilhole and second oilhole is non-multiple relation.

3. the pressure oil supplier in the automatic transmission according to claim 2 is characterized in that, the quantity of any in described first oilhole and second oilhole is 4, and alternative quantity is 6.