CN102135144A

CN102135144A - Oil pressure control device and exhausting method thereof

Info

Publication number: CN102135144A
Application number: CN2011100077885A
Authority: CN
Inventors: 山本英晴; 海津谦一; 庄司准; 谷口正志; 长田浩二; 木岛正道
Original assignee: Nissan Motor Co Ltd; JATCO Ltd
Current assignee: JATCO Ltd
Priority date: 2010-01-21
Filing date: 2011-01-14
Publication date: 2011-07-27
Anticipated expiration: 2031-01-14
Also published as: KR20110085933A; JP5534830B2; KR101778802B1; CN102135144B; JP2011149490A

Abstract

The invention provides an oil pressure control device and an exhausting method thereof, which can lead to no cost increase as well as weight increase and ensure the oil pressure responsiveness. In a clutch oil pressure control device of a first clutch CL 1, the first clutch oil pressure assembly (14) comprises a CSC cylinder (40), a diaphragm spring (43) applying force on a CSC piston (41) from a side where the volume of a CSC cylinder chamber (42) can be reduced, and an oil feed and discharge port (44) for oil feeding and discharging of the CSC cylinder chamber (42). A first clutch control valve (6) comprises a slide valve (60) which discharges the remaining air in the CSC cylinder chamber (42) towards an oil pan (39) when the volume of the CSC cylinder chamber (42) is decreasing. The oil feed and discharge port (44) is equipped above the CSC cylinder (40) where the remaining air in the CSC cylinder chamber (42) is concentrated when oil is supplied to the CSC cylinder chamber (42) through the first clutch control valve (6).

Description

The method for exhausting of hydraulic pressure control device and this hydraulic pressure control device

Technical field

The present invention relates to the hydraulic pressure control device that a kind of air that will be present in the cylinder chamber when assembling in the early stage etc. discharges and the method for exhausting of hydraulic pressure control device.

Background technique

In the clutch oil pressure control device of the cylinder that possesses clutch, makes the connection of carrying out this clutch, the piston of release slides, oil pump, when having air in the loop from oil pump to the cylinder chamber, the oil pressure responsiveness of clutch can worsen.

For fear of the deterioration of the oil pressure responsiveness of this clutch, known have by outlet pipe is set discharge the technology (for example, with reference to patent documentation 1) of the indoor air of cylinder.

Patent documentation 1:(Japan) real fair 7-29313 communique

Yet, in existing technology,, therefore, have cost and weight and increase such problem owing in addition outlet pipe is set.

Summary of the invention

The present invention is conceived to the problems referred to above and proposes, and its purpose is, provides a kind of and can not cause the increase of cost and weight and can realize guaranteeing the hydraulic pressure control device of oil pressure responsiveness and the method for exhausting of this hydraulic pressure control device.

To achieve these goals, hydraulic pressure control device of the present invention possesses the oil pressure assembly, via the control valve that oil circuit is connected with this oil pressure assembly, and described oil pressure assembly possesses: cylinder, and it possesses the cylinder chamber, supplies with oil from oily supply source to this cylinder chamber; Piston, it forms described cylinder chamber with this cylinder, and when supplying with described oil to described cylinder chamber or described oil discharged from described cylinder chamber, the described relatively cylinder of this piston slides; Force application device, it reduces side to the described piston application of force to the volume that makes described cylinder chamber; Oil is supplied with exhaust port, it is arranged at described cylinder, and the described oil that supplies to the described oil of described cylinder chamber and discharge from described cylinder chamber is supplied with the exhaust port circulation at this oil, described control valve possesses valve, at described piston by the described force application device application of force and when the volume of described cylinder chamber is dwindled, described valve is supplied with the air that exhaust port will be present in described cylinder chamber via described oil and is discharged to oily discharge portion, and described oil is supplied with exhaust port and is arranged on via described control valve and supplies with the top position of the described cylinder that described when oily, as to be present in described cylinder chamber air concentrates to described cylinder chamber.

Thus, indoor at cylinder when existing under the air state when cylinder is supplied with oil in that cylinder is indoor in hydraulic pressure control device of the present invention because of proportion relation oil side shifting downwards, the air side shifting that makes progress, air concentrates on the top of cylinder.Under this state, utilize force application device to make piston to the volume shrinking side of cylinder chamber is slided, will be present in the indoor air of cylinder and supply with exhaust port via oil, discharge to oily discharge portion by valve.At this moment, because of oil being supplied with the top position that exhaust port is arranged on the cylinder that air concentrates, so the air ratio of cylinder chamber oil is discharged from the cylinder chamber earlier.Like this,, exhaust is not set in addition,, just the air of cylinder chamber can be discharged as long as follow pressurization, the decompression of the stroke action of piston with pipe because of oil being supplied with the top position that exhaust port is arranged on the cylinder chamber.Its result can not cause the increase of cost and weight and can realize guaranteeing the oil pressure responsiveness.

Description of drawings

Fig. 1 is the overall system view of FR motor vehicle driven by mixed power of rear wheel drive of the clutch oil pressure control device of expression Application Example 1;

Fig. 2 is that the Li Heqi ﹠amp that is controlled the first clutch CL1 (example of clutch) that connects, discharges by embodiment 1 hydraulic pressure control device is disposed in expression; The sectional drawing of the structure of electric motor assembly portion;

Fig. 3 is the External view that expression connects and composes the outer pipe arrangement of embodiment 1 the first clutch oil pressure assembly of hydraulic pressure control device and first clutch control valve;

Fig. 4 is the control system figure that the major component of expression embodiment's 1 clutch oil pressure control device constitutes, oil pressure control constitutes and electronic control constitutes;

Fig. 5 is the flow chart of expression with the exhaust control processing flow process of embodiment 1 integrated controller enforcement;

Fig. 6 is the time diagram of expression with the step response of the oil pressure command value of the exhaust control processing output of embodiment 1 integrated controller enforcement;

Fig. 7 is the figure of expression according to the example of the driving mode selection figure that is determined the EV zone of first clutch release and the HEV zone that first clutch connects by the speed of a motor vehicle and the definite operation point of throttle opening;

Fig. 8 is the air volume of expression when being assembled with the oil hydraulic circuit of the connection that is used to carry out first clutch, release and the figure of the relation property of first clutch oil pressure;

The contrastive feature figure of the contrast of Fig. 9 relation property that to be expression obtain according to the calculating formula of ON/OFF number of the residual air amount of first clutch oil hydraulic circuit and oil pressure command value and experimental value;

Figure 10 is the figure that the scavenging action the when initial stage assembles in embodiment 1 clutch oil pressure control device is described, the PRESSURE-VOLUME RELATION of Figure 10 (a) expression clutch oil hydraulic circuit, assembling A-stage before Figure 10 (b) expression exhaust, the piston stroke state of Figure 10 (c) expression pressurization, the piston return state of Figure 10 (d) expression decompression;

Figure 11 is the flow chart of expression with the flow process of the exhaust control processing of embodiment 2 integrated controller enforcement;

Figure 12 exhaust control that to be expression implement with embodiment 2 integrated controller to the variation of the oil pressure command value of first clutch and the time diagram that piston stroke changes.

Description of reference numerals

The Eng motor

CL1 first clutch (clutch)

MG motor/generator (motor)

RL, RR left and right sides trailing wheel (driving wheel)

S-O/P auxiliary oil pump (oil pump)

6 first clutch for clutch control valves (control valve)

14 first clutch oil pressure assemblies (clutch pressure assembly)

39 food trays (oily discharge portion)

40 CSC cylinders (cylinder)

41 CSC pistons (piston)

CSC cylinder chambers (cylinder chamber) 42

43 diaphragm springs (force application device)

44 oil are supplied with exhaust port

Pipe arrangement (pipe arrangement) in 51

53 outer pipe arrangements (pipe arrangement)

60 guiding valves (switching valve)

The 60f oil drain out

61 solenoid valves (switching valve)

Embodiment

Below, based on the best mode of illustrated embodiment 1 and embodiment's 2 explanations hydraulic pressure control devices of the present invention and the method for exhausting of realizing hydraulic pressure control device.

(embodiment 1)

At first, formation is described.

Fig. 1 is the overall system view of FR motor vehicle driven by mixed power of rear wheel drive of the clutch oil pressure control device (example of hydraulic pressure control device) of expression Application Example 1.Below, illustrate that based on Fig. 1 total system constitutes.

As shown in Figure 1, the driving of embodiment 1 FR motor vehicle driven by mixed power system comprises: motor Eng, flywheel FW, first clutch CL1, motor/generator MG, second clutch CL2, automatic transmission AT, transmission shaft PS, differentiator DF, left driving shaft DSL, right driving axle DSR, left rear wheel RL, off hind wheel RR.In addition, FL is that the near front wheel, FR are that off-front wheel, M-O/P are that main oil pump, S-O/P are auxiliary oil pump.

Above-mentioned motor Eng is petrol engine and diesel engine, based on the engine control instruction from engine controller 1, carries out engine start control and motor and stops control.In addition, engine output shaft is provided with flywheel FW.

Above-mentioned first clutch CL1 is installed between motor Eng and the motor/generator MG, be to be released when EV pattern (electric automobile during traveling pattern) is selected, driving mode coupled when HEV pattern (hybrid vehicle driving mode) is selected is selected clutch.Use normally closed dry type single plate clutch as this first clutch CL1.

Above-mentioned motor/generator MG is installed between first clutch CL1 and the automatic transmission AT, has as the power traction of motor work with as the regeneration function of generator work.What this motor/generator MG used is to be embedded with permanent magnet on the rotor, the synchronized model motor/generator of the three phase current of coiling coil on the stator.

Above-mentioned second clutch CL2 is mounted between motor/generator MG and left and right sides trailing wheel RL, the RR, for example, during by the change of transmitting torque such as engine start the time, becomes the state of being slidingly connected, for absorbing the clutch that cogging is provided with.This second clutch CL2 is not other setting, is chosen in the friction that is present in the transmission of torque path that a plurality of frictions that each speed change level of automatic transmission AT connects connect in the key elements and connects key element.

Above-mentioned automatic transmission AT for example be according to automatic switchovers such as the speed of a motor vehicle and gas pedal aperture advance 7 speed/retreat, 1 speed etc. have level the speed change level step change transmission or infinitely change the stepless speed variator of gear ratio, transmission output shaft connects with left and right sides trailing wheel RL, RR via transmission shaft PS, differentiator DF, left driving shaft DSL, right driving axle DSR.

Above-mentioned main oil pump M-O/P is arranged at the input shaft of automatic transmission AT, is the mechanical oil pump that mechanically makes the pump action.Above-mentioned auxiliary oil pump S-O/P is arranged on package shell etc., is when main oil pump M-O/P does not discharge oil mass or when discharging low on fuel, utilizes motor to make the electric oil pump of pump action.

Below, illustrate that the control of motor vehicle driven by mixed power is.

As shown in Figure 1, the control of embodiment 1 FR motor vehicle driven by mixed power system constitutes and has: engine controller 1, electric motor controller 2, transducer 3, storage battery 4, first clutch control valve 6, AT controller 7, AT control valve 8, brake controller 9, integrated controller 10.In addition, each

controller

1,2,7,9 is connected via the CAN order wire 11 that can carry out information exchange mutually with integrated controller 10.

1 input of above-mentioned engine controller from the engine speed information of engine rotation speed sensor 12, from the target engine torque instruction of integrated controller 10, other needs information.And, control the instruction (engine control) of motor operating point (Ne, Te) to the outputs such as throttler valve actuator of motor Eng.

2 inputs of above-mentioned electric motor controller from the information of the resolver 13 of the rotor rotation position that detects motor/generator MG, from the target MG torque instruction of integrated controller 10 and target MG rotary speed instruction, other needs information.And, control the instruction (motor control) of the motor action point (Nm, Tm) of motor/generator MG to transducer 3 inputs.In addition, this electric motor controller 2 monitors the storage battery SOC of the charging capacity of expression storage battery 4.

Above-mentioned AT controller 7 inputs are from the information of gas pedal jaw opening sensor 16, vehicle speed sensor 17, other sensor class 18 (speed changer input speed sensor, Circuit breaker etc.).And when the D shelves travelled, according to the optimum speed change level of location retrieval that the moving turning point of being determined by gas pedal aperture APO and vehicle velocity V SP exists on speed change figure, the control command of the speed change level of retrieving obtaining was to 8 outputs (speed Control) of AT control valve.

7 inputs of this AT controller from the heat transfer agent of the first clutch stroke sensor 15 of the piston stroke position of detecting first clutch oil pressure assembly 14, from the target CL1 torque instruction of integrated controller 10, other needs information.And, the instruction that control first clutch CL1 connects, is slidingly connected, discharges is exported (first clutch control) to first clutch control valve 6.

This AT controller 7 is during from integrated controller 10 input target CL2 torque instructions, is slidingly connected control command (second clutch control) to AT control valve 8 output second clutch CL2.

9 inputs of above-mentioned brake controller from the heat transfer agent of the vehicle-wheel speed sensor 19 of each wheel velocity that detects four-wheel and break stroke sensor 20, from the regeneration of integrated controller 10 coordinate control command, other needs information.And, when brake service,, when regenerative braking power is not enough, utilize the braking force of machinery to replenish its insufficient section (break control is coordinated in regeneration) when with respect to by the desired braking force that requires of break stroke BS.

The consumed energy of above-mentioned integrated controller 10 management vehicle integral body is taken on the function that vehicle is effectively travelled, and input reaches via CAN order wire 11 input information from the information that needs of motor speed sensor 21 that detects motor speed Nm and air discharge cook 22 etc.And, instruct to engine controller 1 export target engine torque, to electric motor controller 2 export target MG torque instructions and target MG rotary speed instruction, to first clutch controller 5 export target CL1 torque instructions, to AT controller 7 export target CL2 torque instructions, coordinate control command (Comprehensive Control) to brake controller 9 output regeneration.

Fig. 2 is that the Li Heqi ﹠amp that is controlled the first clutch CL1 (example of clutch) that connects, discharges by embodiment 1 hydraulic pressure control device is disposed in expression; The sectional drawing of the structure of electric motor assembly portion.Fig. 3 is the External view that expression connects and composes the outer pipe arrangement of embodiment 1 the first clutch oil pressure control unit of hydraulic pressure control device and first clutch control valve.Fig. 4 is the control system figure that the major component of expression embodiment's 1 clutch oil pressure control device constitutes, oil pressure control constitutes and electronic control constitutes.Below, illustrate that based on Fig. 2～Fig. 4 the oil hydraulic circuit of connection, release first clutch CL1 constitutes.

As shown in Figures 2 and 3, embodiment 1 Li Heqi ﹠amp; Electric motor assembly portion possesses: motor Eng, flywheel FW, first clutch CL1 (clutch), motor/generator MG, main oil pump M-O/P, automatic transmission AT, package shell 30.

The front side of said modules shell 30 is connected with the engine block 31 of motor Eng as shown in Figure 2, and rear side is connected with the transmission case body 32 of automatic transmission AT.And the inside of this package shell 30 is divided into three Room by engine casing (Eng Cas) 33 and stator casing 34 as shown in Figure 2.Dispose flywheel FW and first clutch CL1 in first Room that surrounds by motor Eng and engine casing (Eng Cas) 33.Second Room configuration motor/generator MG that is surrounding by engine casing (Eng Cas) 33 and stator case 34.Dispose main oil pump M-O/P in the 3rd Room that surrounds by stator case 34 and automatic transmission AT.

As shown in Figure 2, above-mentioned first clutch CL1 is installed between the coreless motor axle 35 of flywheel FW and motor/generator MG.Above-mentioned motor/generator MG disposes resolver 13 at the inner side of rotor as shown in Figure 2, connects package shell 30 and is provided with forceful electric power Wiring harness terminal 36 and the cooling water oral pore 37 of coming in and going out.Above-mentioned main oil pump M-O/P drives by the speed changer supply shaft 38 that combines with coreless motor axle 35 as shown in Figure 2.

As Fig. 2～shown in Figure 4, the oil hydraulic circuit that is used to connect, discharge embodiment 1 first clutch CL1 constitutes and possesses: first clutch oil pressure assembly 14 (oil pressure assembly), first clutch control valve 6 (control valve), AT control valve 8, main oil pump M-O/P, auxiliary oil pump S-O/P (oil pump), food tray 39 (oily discharge portion).

Above-mentioned first clutch oil pressure assembly 14 is the connection of control first clutch CL1, the CSC oil pressure actuator of release.As shown in Figure 2, this first clutch oil pressure assembly 14 possess carry out first clutch CL1 connects, relative CSC cylinder 40 (cylinder) slides when discharging CSC piston 41 (piston), to the volume shrinking side that makes CSC cylinder chamber 42 (cylinder chamber) to the diaphragm spring 43 (force application device) of CSC piston 41 application of forces, carry out oil to CSC cylinder chamber 42 and supply with the oil of discharging and supply with exhaust port 44.One of diaphragm spring 43 distolaterally contacts with pressure ring 45, and another of diaphragm spring 43 is distolateral to be contacted with CSC piston 41 via release bearing 46.

That is, when not when CSC cylinder 40 is supplied with oil pressure, the connection fully that keeps first clutch CL1 by the active force of diaphragm spring 35.And, when when CSC cylinder 40 is supplied with oil pressure, the path increment of the CSC piston 41 that the active force by control opposing diaphragm spring 35 slides, thus control discharges from being slidingly connected fully.In addition, CSC is the abbreviation of " Concentric Slave Cylinder ".

As Fig. 2～shown in Figure 4, the oil circuit that connects the CSC cylinder chamber 42 of above-mentioned first clutch oil pressure assembly 14 and first clutch control valve 6 by be connected from oil supply with exhaust port 44 to the interior pipe arrangement 51 of pipe-fitting joint 50, connect outer pipe arrangement 53, make outer pipe arrangement 53 be communicated with in the casing that mission case 32 forms oil circuit 54, the first clutch pressure oil circuit 55 that oil circuit 54 connections are formed in the first clutch control valve 6 in the casing is constituted from pipe-fitting joint 50 to housing assembly department 52.In addition, outer pipe arrangement 53 therein way position relative component shell 30 by clamp 56 intermediate supports.

As shown in Figure 4, above-mentioned first clutch control valve 6 possesses main oil pump M-O/P or auxiliary oil pump S-O/P; As the connection, the unconnected switching valve that switch CSC cylinder chamber 42, pressing Psol with electromagnetism is that the valve work living first clutch of cutting down output is pressed the guiding valve 60 of Pcl; Pressing Pp with control is that the work living electromagnetism of cutting down output is pressed the solenoid valve 61 of Psol.

Above-mentioned guiding valve 60 has: the traveller 60b that can slide at valve opening 60a, to the left of Fig. 4 to the spring 60c of the traveller 60b application of force, the first clutch that is formed at valve opening 60a being pressed hole 60d, mainly pressing hole 60e, oil drainage hole 60f, valve work to press hole 60g.First clutch presses hole 60d and first clutch to press oil circuit 55 to be communicated with.The main hole 60e of pressure is communicated with the main oil circuit 62 of pressing.Oil drainage hole 60f is communicated with oil extraction oil circuit 63.Valve work presses hole 60g and electromagnetism to press oil circuit 64 to be communicated with.

And, the first clutch of guiding valve 60 presses hole 60d and the main hole 60e of pressure when non-connected state (=first clutch is pressed hole 60d and oil drainage hole 60f connected state), when the piston stroke of following the active force of diaphragm spring 35 and producing is dwindled the volume of CSC cylinder chamber 42, will be present in a CSC cylinder chamber 42 and a part and discharge to food tray 39 through oil drainage hole 60f and oil extraction oil circuit 63 from CSC cylinder chamber 42 to the empty G﹠O of the oil circuit of guiding valve 60.

Above-mentioned solenoid valve 61 serves as initial the pressure according to the control command from AT controller 7 with the first pilot Pp that is produced by AT control valve 8, produces electromagnetism and presses Psol.This guiding valve 60 and solenoid valve 61 are valves of control of connection, the release of the first clutch CL1 when travelling usually, in this embodiment 1, still prolong and be used in when travelling usually the control valve that uses, discharge the exhaust control of the air that residues in CSC cylinder chamber 42 and oil circuit when assembling in the early stage and when repairing assembling.

As shown in Figure 4, above-mentioned AT control valve 8 possesses according to the main pressure electromagnetic valve 80 that produces the electromagnetism pressure from the control command of AT controller 7; With the pump pressure is initial the pressure, is that signal pressure is carried out pressure controlled pressure regulator valve 81 to the main PL of pressure with the electromagnetism pressure; With the pump pressure is that initial the pressure carried out pressure controlled pilot valve 82 to certain first pilot Pp.

The main PL of pressure that this AT control valve 8 produces when travelling usually is as the initial pressure of carrying out speed Control with automatic transmission AT, become the pressure of corresponding gas pedal aperture etc. by pressure regulation.Relative with it, the main PL of pressure during exhaust control is adjusted to the authorized pressure PLs that predesignates as the air in the

pipe arrangement

51,53 is sent to CSC cylinder chamber 42 enough pressure when utilizing exhaust control to form the pressurization of piston travel condition.At this moment, the volume of CSC cylinder chamber 42 is also stipulated its volume in the mode that the air in the

pipe arrangement

51,53 is sent to CSC cylinder chamber 42.

Above-mentioned oil is supplied with exhaust port 44 in the piston travel condition of the volume of the supply expansion CSC cylinder chamber 42 of passing through compressed oil, to be present in CSC cylinder chamber 42 and from CSC cylinder chamber 42 to the oil circuit of guiding valve 60 air compression, the air of compression is in compressed oil enters CSC cylinder chamber 42, in CSC cylinder chamber 42, reason owing to proportion, air concentrates on the top, is divided into oil reservoir and air layer.Above-mentioned oil is supplied with exhaust port 44 and is set in the top position of concentrating the CSC cylinder 40 that forms air layer by the air that is present in CSC cylinder chamber 42.Therefore, oil is supplied with the setting permissible range of exhaust port 44 shown in the A-A cross section of Fig. 4, when being divided into oil reservoir and air layer in CSC cylinder chamber 42, is the scope E that air layer exists.That is, oil supply exhaust port 44 is allowed any position that is set in this scope E.

Fig. 5 is the flow process (exhaust control device) of expression by the flow process of the exhaust control processing of embodiment 1 integrated controller 10 enforcements.Below, each step of Fig. 5 is described.

When the initial stage assembled, the controller from equipment side on Assembly line transmitted exhaust control commencing signal to integrated controller 10, beginning exhaust control.In addition, main oil pump M-O/P discharges compressed oil by driven the input shaft of automatic transmission AT by the driving source of equipment side.

In step S1, via 7 couples of solenoid valve 61a of AT controller output oil pressure command value ON, enter step S2 from integrated controller 10.

In step S2, continue the output of the oil pressure command value ON among the step S1, whether judgement is more than the first set time T1 from the ON timing value Ton that oil pressure command value ON output begins to start, and (enter step S4 under the situation of Ton 〉=T1), (situation of Ton＜T1) is returned step S1 at NO at YES.

At this, for " the first set time T1 ", measure in advance from pressurization and instruct (oil pressure command value ON) to begin to reach the time that maximum travel position needs,, be set in the institute that needs the minimum limit zone that has suppressed dead time and want the time (with reference to Fig. 6) based on this determination data to CSC piston 41.

In step S3, the judgement when judgement when continuing the Ton 〉=T1 among the step S2 or the Toff among the step S4＜T2 via 7 couples of solenoid valve 61a of AT controller output oil pressure command value OFF, enters step S4 from integrated controller 10.

In step S4, continue the output of the oil pressure command value OFF among the step S3, whether judgement is more than the second set time T2 from the OFF timing value Toff that the output of oil pressure command value OFF begins to start, (enter step S6 under the situation of Toff 〉=T2), (situation of Toff＜T2) is returned step S3 at NO at YES.

At this, for " the second set time T2 ", measure in advance from decompression and instruct (oil pressure command value OFF) to begin to return the time that primary position needs, and, be set in the institute that needs the minimum limit zone that has suppressed dead time and want the time (with reference to Fig. 6) based on this determination data to CSC piston 41.

In step S5, the judgement when continuing the Toff 〉=T2 among the step S4, with pressurization, decompression unit be the count value n of once counting with the replacement of n=n+1 formula, enter step S6.In addition, the initial value n=0 of count value n.

In step S6, continue the replacement of the count value n of step S7, judge whether count value n is more than the setting count value N, (carry out to end under the situation of n 〉=N), (situation of n＜N) is returned step S1 at NO at YES.

At this, " set count value N " wanted number of times based on the institute that reaches the exhaust condition of guaranteeing the oil pressure responsiveness and set the output for the exhaust control command once counted with the unit that pressurizes, reduce pressure.

Below, illustration.

At first, carry out the explanation of " problem that prior art should solve ", then, with the effect of embodiment 1 clutch oil pressure control device be divided into " mechanism of method for exhausting of the present invention ", " scavenging action during assembling " describes.

(problem that prior art should solve)

Normally closed dry clutch oil pressure assembly connects outside clutch pedal (master cylinder) and oil hydraulic cylinder (CSC) with the loop circuit, utilize the operation of clutch pedal, oil hydraulic cylinder is exerted pressure, make the dry clutch that utilizes elastic force to connect discharge (with reference to the real fair 7-29313 communique of Japan).

When there was air in this loop circuit, the oil pressure response time that the oil pressure of conversion pedal operation power arrives oil hydraulic cylinder produced sluggishness, and action causes obstacle to oil hydraulic cylinder.Therefore, guarantee the initial stage response, need to set exhaust gear and carry out bleeding in order when assembling, to discharge the air of loop circuit.

When setting air-breather (outlet pipe) as this exhaust gear, oil is discharged to the outside from air-breather with air during exhaust.Therefore, need parts such as oil vessel in addition in air-breather, cost and weight increase, and air-breather occupy space enlargement, restricted the layout degrees of freedom of circumferential component.

In addition, the manually-operable that when assembling at initial stage or the bleeding of carrying out when repairing assembling are carried out respectively each oil pressure assembly for the operator, so bleeding extremely bothers, and bleeding quantity in man-hour obviously increases.

On the other hand, known have a following hybrid vehicle, promptly, it is equipped with motor and motor as driving source, driving mode is installed between motor and motor selects clutch (=first clutch CL1).In the situation of this hybrid vehicle, for example shown in Figure 7, having with the throttle opening is that the following zone of a/8 aperture (setting aperture) is the EV zone, and the zone that surpasses the a/8 aperture with throttle opening is the driving mode selection figure in HEV zone.Therefore, when travelling, when being in the EV zone by the speed of a motor vehicle and the definite operation point of throttle opening, first clutch CL1 discharges, and when operation point was in the HEV zone, first clutch CL1 connected.

And, when utilizing the EV pattern to travel, by depressing the operation of gas pedal, operation point from the EV zone when HEV zone is mobile, the first clutch CL1 of release is connected, make engine operation, to being the HEV mode transition of driving source, deal with demanding driving force apace with motor and motor.But when the oil pressure responsiveness of first clutch CL1 was hanged down, engine start was slow and slow to the HEV mode transition, starting property and acceleration deterioration.

In addition, when the HEV pattern is travelled, utilize gas pedal return, operation point from the HEV zone when EV zone is mobile, the first clutch CL1 of connection is discharged, motor is stopped apace to being the EV mode transition of driving source with the motor only, guarantee high fuel consumption performance (promptly, reducing fuel consume).But when the oil pressure responsiveness of first clutch CL1 was hanged down, motor stopped slow and slow to the transition of EV pattern, became the reason that the fuel consumption performance is reduced.

Like this, discharge when the EV model selection, the driving mode that connects when the HEV preference pattern is selected in the situation of clutch, for make drive performance and fuel consumption performance the two and deposit, have and guarantee high and stable this requirement of oil pressure response performance.But,, then can not tackle this requirement as long as carry out bleeding with manually-operable.

(mechanism of method for exhausting of the present invention)

In order to solve above-mentioned problem, motion of the present invention has does not a kind ofly have air-breather (outlet pipe) to carry out venting gas appliance and method for exhausting, promptly, only pressurization, the decompression work (piston stroke) of the control command by coming self-controller, then can discharge when assembling in the early stage or be present in the residual air of loop circuit when repairing assembling.Below, based on Fig. 8～Figure 10, the mechanism of method for exhausting of the present invention is described.

(A-stage)

When assembling in the early stage or when repairing assembling, promptly assemble under the A-stage, shown in Figure 10 (b), be that oil circuit 54, first clutch are pressed the air state that is full of the barometric pressure level in the oil circuit 55 in CSC cylinder chamber 42, the interior pipe arrangement 51 that connects via oil supply exhaust port 44, pipe-fitting joint 50, outer pipe arrangement 53, casing.

(piston stroke state)

Oil under the piston stroke state and air are dynamically narrated.

(a) at first, the oil of the path increment volume of CSC piston 41 is supplied with and is full of in the loop circuit of air.

(b) apply oil pressure, make the air compression in the loop circuit.

At this, the air compression in the loop circuit is certain such relation by PV, that is, oil pressure P is high more, and the more little such relation of the air volume in the loop circuit is compressed.For example, shown in dashed lines arrow C O-C1 among Fig. 8, when the air volume in the loop circuit was B0, when 0 brought up to P1, the air volume in the loop circuit was compressed to B1 from B0 with oil pressure.

(c) supplied with in the loop circuit by the oil of the cubical content of air compression.

For example, when air volume was compressed to B1 from B0, the oil of the cubical content of compression (B0-B1) was supplied with in the loop circuit.

(d) shown in Figure 10 (c), because the proportion difference of empty G﹠O is divided into air on top in the CSC cylinder chamber 42 of CSC cylinder 40, oil is in the bottom.In addition, shown in Figure 10 (c), supplying with oil circuit that exhaust port 44 is connected with CSC cylinder chamber 42 via oil is 51,50,53,54,55 to be the oily state that almost is full of.

(piston return state)

Oil under the piston return state and air are dynamically narrated.

(a) oil of the cubical content that returns of CSC piston 41 is discharged from.

(b) CSC cylinder chamber 42 oil of residual bottom that remains unchanged divides and supplies with exhaust port 44 at the air on top via oil and be discharged from.

(c) along with oil pressure reduces, air is discharged from after expanding as original volume.

(d) after air is discharged, an oil residues in CSC cylinder chamber 42.

(e) shown in Figure 10 (d), form the form that oil and air replace, the A-stage air quantity reduces relatively.

(oil pressure is opened (ON), is closed the repetition of (OFF))

Above-mentioned explanation is when being full of the A-stage of air only carrying out the primary oil pressure open and close in the loop circuit, moves and exhausting air the mechanism that air quantity is reduced to the piston return state from the piston stroke state.But, only carry out oil pressure open and close once, there is not air quantity to be reduced to can to guarantee this reliable guarantee of residual air amount of high clutch pressure responsiveness.Therefore, exhaust control of the present invention repeatedly repeats the oil pressure open and close with the target that is reduced to of reliable residual air amount.

That is, oil pressure is opened (ON) n back residual air and be made as Vair (n), can use calculating formula

Vair (n)=(Vp-Vs)+Vair (n-1) hydraulic pressure control device K (1)

Represent.

But in the formula (1), to be the capacity (with reference to Figure 10 (a)) of pipe arrangement part, stroke capacity (with reference to Figure 10 (a)) that Vs is CSC piston 41, Vair (n-1) open (ON) residual air amount, K after (n-1) inferior for oil pressure to Vp is the compressibility coefficient of oil pressure.

Therefore, when in the coordinate surface that is coordinate axes with residual air amount and ON-OFF number, representing above-mentioned (1) calculating formula with characteristic line, shown in the solid line characteristic of Fig. 9, ON-OFF number about 1 time～3 times, the residual air amount sharply descends, even increase ON-OFF number, be almost the characteristic of plateau thereafter.And, when on the coordinate surface of identical coordinate axes, illustrating the experimental value of residual air amount and ON-OFF number, be ■ mark as shown in Figure 9.The characteristic line of this Fig. 9 of paired observation and experimental value, almost consistent by the characteristic line that calculating formula obtains as can be known with experimental value.Therefore, the reduction for the residual air amount that realizes guaranteeing high clutch pressure responsiveness need not repeat tens oil pressure open and close, just can realize about only repeating for several times.

Consequently, method for exhausting of the present invention is considered as the control of repetition left and right sides oil pressure open and close for several times.And, when being used to guarantee the assembling of high clutch pressure responsiveness behind the oil pressure loop structure of the connection of exhaust by being used to carry out first clutch CL1 in assembling, release from the use initial stage, utilizing for the first time, the oil pressure open and close reduce the air quantity in the loop circuit quickly, utilize for the second time later oil pressure open and close, residual every repetition of residual air amount once realized with regard to reducing such mechanism.

(scavenging action during assembling)

During based on Fig. 4～Fig. 6 explanation initial stage assembling and the scavenging action when repairing assembling.

After assembling is used to carry out the oil pressure loop structure of connection, release of first clutch CL1, when making air discharge cook 22 for ON, in the flow process of Fig. 5, enter step S1 → step S2 → step S3, judge the flow process that enters step S2 → step S3 repeatedly during Ton＜T1 at step S3.

That is, in step S1, motoring auxiliary oil pump S-O/P, and, by the principal pressure PL under the AT control valve 8 generation authorized pressure PLs.And in step S2, from 5 couples of solenoid valve 61a of first clutch controller output oil pressure command value ON, the output of this oil pressure command value ON lasts till through the first set time T1.

And, when judging Ton 〉=T1 among the step S3, in the flow process of Fig. 5, enter step S4 → step S5 from step S3, during step S5 judges Toff＜T2, the flow process that enters step S4 → step S5 repeatedly.That is, in step S4, from 5 couples of solenoid valve 61a of first clutch controller output oil pressure command value OFF, the output of this oil pressure command value OFF lasts till through the second set time T2.

And, when judging Toff 〉=T2 at step S5, in the flow process of Fig. 5, enter step S6 → step S7 from step S5, when judging n＜N at step S7, return step S2 from step S7, begin the exhaust control of oil pressure open and close next time.And, by the exhaust of oil pressure open and close being controlled only repeatedly setting count value N, when step S7 judges n 〉=N, carry out to ends from step S7, finish exhaust and control.

As mentioned above, in embodiment 1 exhaust control, after the preparation that operation produces the principal pressure PL of authorized pressure PLS based on the ON of air discharge cook 22 was handled, output was the exhaust control command of a unit with the decompression of the output of the pressurization of the output of oil pressure command value ON and oil pressure command value OFF.And, as shown in Figure 6, the waveform of this pressurization, decompression is the step-like waveform of oil pressure command value ON/OFF, carries out the output (being 5 times) for the exhaust control command once counted with the unit of pressurization, decompression with the stipulated number that reaches the exhaust condition of guaranteeing the oil pressure responsiveness in the example of Fig. 6.

In the preparation that the ON based on above-mentioned air discharge cook 22 operates is handled, produce the principal pressure PL of authorized pressure PLs.That is, when main pressure electromagnetic valve 80 was exported control commands, main pressure electromagnetic valve 80 produced electromagnetism and presses from AT controller 7, and this electromagnetism is pressed and is applied to pressure regulator valve 81.Pressing with this electromagnetism is to press as initial with the pump pressure from auxiliary oil pump S-O/P in the pressure regulator valve 81 of signal pressure, and pressure regulation is the main pressure PL of the authorized pressure PLs (only the air in the

pipe arrangement

51,53 being delivered to the pressure of CSC cylinder chamber 42) that predesignates.

In the pressurization that the output by above-mentioned oil pressure command value ON produces, enlarge the volume of CSC cylinder chamber 42 by the stroke of CSC piston 41.That is, when solenoid valve 61 output ON instructed, solenoid valve 61 produced the electromagnetism pressure Psol that is communicated with the main PL of pressure (=authorized pressure PLs) by AT controller 7.Therefore, the compressed oil that produces from the authorized pressure PLs of AT control valve 8 is shown in the blacking arrow of Fig. 4, and through the main oil circuit 62 of pressing, hole 60g is pressed in supply valve work.Thus, guiding valve 60 traveller 60b antagonism spring 60c advances to the imaginary line position from the solid line position of Fig. 4, is communicated with first clutch and presses hole 60d and the main hole 60e of pressure.By this valve switch motion, independently press the compressed oil of the authorized pressure PLS generation of oil circuit 62 to press hole 60d to enter first clutch pressure oil circuit 55 through main hole 60e of pressure and first clutch.And, the compressed oil that authorized pressure PLs produces is through oil circuit 54 in the casing → outer pipe arrangement 53 → pipe-fitting joint 50 → interior pipe arrangement 51, supply with exhaust port 44 from oil and import CSC cylinder chamber 42, to the left of Fig. 4 to pushing CSC piston 41, CSC piston 41 to the left of Fig. 4 to stroke, thereby enlarge the volume of CSC cylinder chamber 42.

In the decompression that the output of above-mentioned oil pressure command value OFF produces, return the volume that dwindles CSC cylinder chamber 42 by CSC piston 41.That is, along with after the pressurization of the stroke of CSC piston 41 from first clutch controller 5 when the solenoid valve 61 output OFF instructions, solenoid valve 61 produces the electromagnetism that disconnects principal pressure PL and presses Psol.Therefore, the valve work that supplies to guiding valve 60 presses the valve work of hole 60g to press (=main the PL of pressure) by pressure release, the active force that the traveller 60b of guiding valve 60 utilizes spring 60c to produce is advanced to solid line position from the imaginary line position of Fig. 4, is communicated with first clutch and presses hole 60d and oil drainage hole 60f.By this valve switch motion, the oil pressure in the CSC cylinder chamber 42 reduce, and CSC piston 41 is along with the active force of the diaphragm spring 43 right return stroke to Fig. 4.And during along with the return stroke of CSC piston 41, the volume of CSC cylinder chamber 42 dwindles.

Like this, guiding valve 60 switches to the connection side, when CSC cylinder 40 is supplied with compressed oils, is present in CSC cylinder chamber 42 and supplies with exhaust port 44 to the air of the oil circuit of guiding valve 60 from oil and be compressed, and the air of compression enters CSC cylinder chamber 42.In this CSC cylinder chamber 42, because the proportion relation, oil (than great) is side shifting downwards, and air (proportion is little) is side shifting upwards, thereby is divided into oil reservoir and air layer.

Under this state, when guiding valve 60 being switched to non-connection side, utilize the active force of diaphragm spring 43, CSC piston 41 is to the volume shrinking side return stroke that makes CSC cylinder chamber 42.By this return stroke, a part that is present in the CSC cylinder chamber 42 and the empty G﹠O of the oil circuit that is connected CSC cylinder chamber 42 and guiding valve 60 is shown in the blank arrow of Fig. 4, press oil circuit 55 → first clutch to press hole 60d → oil drainage hole 60f → oil extraction oil circuit 63 through oil circuit 54 → first clutch in CSC cylinder chamber 42 → interior pipe arrangement 51 → pipe-fitting joint 50 → outer pipe arrangement 53 → casing, discharge to food tray 39.

At this moment, the oil of CSC cylinder 40 is supplied with the top position that exhaust port 44 is set in the CSC cylinder 40 of air layer existence, therefore, air ratio oil is 42 interior discharges the from CSC cylinder chamber earlier.Like this, carry out oil from the top position of CSC cylinder chamber 42 and supply with discharge, so, exhaust need not be set in addition with pipe, as long as follow pressurization, the decompression of the stroke action of CSC piston 41, just the air in the CSC cylinder chamber 42 can be discharged without any confusion.

As mentioned above, assembling is used for carrying out the exhaust control carried out behind the oil pressure loop structure of connection, release of first clutch CL1, represented the air quantity in the loop circuit to be reduced quickly by primary oil pressure open and close (pressurization, decompression), by for the second time later oil pressure open and close (pressurization, decompression), make the situation of the every such scavenging action that repeats once just to reduce of residual air amount residual in exhaust last time.This result is, by only beginning operation, the exhaust control of then carrying out automatically, can and not have the deviation of each assembly with operating time of short time, stably carry out bleeding, make the residual air amount of exhausting air to the oil pressure response performance that obtains wishing, and, can guarantee high clutch pressure responsiveness from the use initial stage of first clutch CL1.

Below, description effect.

In the method for exhausting of embodiment 1 clutch oil pressure control device and clutch oil pressure control device, can access the following effect of enumerating.

(1) in the method for exhausting that possesses the oil pressure assembly (first clutch oil pressure assembly 14) and the hydraulic pressure control device (clutch oil pressure control device) of the control valve (first clutch control valve 6) that is connected with this oil pressure assembly (first clutch oil pressure assembly 14) via oil circuit, above-mentioned oil pressure assembly (first clutch oil pressure assembly 14) has: possess the cylinder (CSC cylinder 40) of supplying with the cylinder chamber (CSC cylinder chamber 42) of oil from oily supply source; Form above-mentioned cylinder chamber (CSC cylinder chamber 42) with this cylinder (CSC cylinder 40), the piston (CSC piston 41) that above-mentioned relatively cylinder (CSC cylinder 40) slides when above-mentioned cylinder chamber (CSC cylinder chamber 42) supplies with the above-mentioned oil of discharge; To the force application device (diaphragm spring 43) of the volume shrinking side that makes above-mentioned cylinder chamber (CSC cylinder chamber 42) to above-mentioned piston (the CSC piston 41) application of force; Be arranged on the above-mentioned cylinder (CSC cylinder 40), supply with the oil of the above-mentioned oil circulation of discharging to above-mentioned cylinder chamber (CSC cylinder chamber 42) and supply with exhaust port 44, above-mentioned control valve possesses above-mentioned piston (CSC piston 41) makes above-mentioned cylinder chamber (CSC cylinder chamber 42) when volume dwindles under above-mentioned force application device (diaphragm spring 43) application of force effect, supply with exhaust port 44 via above-mentioned oil and will be present in the valve (guiding valve 60) of the air of above-mentioned cylinder chamber (CSC cylinder chamber 42) to oily discharge portion (food tray 39) discharge, above-mentioned oil supply with exhaust port 44 via above-mentioned control valve (first clutch control valve 6) when above-mentioned cylinder chamber (CSC cylinder chamber 42) supplies with above-mentioned oil, be arranged on the top position of the above-mentioned cylinder (CSC cylinder 40) that the air that is present in above-mentioned cylinder chamber (CSC cylinder chamber 42) concentrates.

Therefore, can provide to cause cost and weight to increase, and can realize guaranteeing the hydraulic pressure control device (clutch oil pressure control device) of the oil pressure responsiveness (clutch pressure responsiveness) of oil pressure assembly (first clutch oil pressure assembly 14).

(2) possesses above-mentioned oily discharge portion (food tray 39) and supply with the oil pump (auxiliary oil pump S-O/P) of oil to above-mentioned cylinder chamber (CSC cylinder chamber 42), above-mentioned oily discharge portion (food tray 39) is stored the above-mentioned oil that discharge (CSC cylinder chamber 42) from above-mentioned cylinder chamber, above-mentioned oil pump (auxiliary oil pump S-O/P) sucks the oil that is stored in above-mentioned oily discharge portion (food tray 39), supplies with oil to above-mentioned cylinder chamber (CSC cylinder chamber 42).

Like this, the oily discharge portion (food tray 39) that makes hydraulic pressure control device (clutch oil pressure control device) is as the air drain position, so, do not need to be provided with in addition the device of the oil that recovery discharges with air.Thus, can make the bleeding high efficiency.

(3) venting gas appliance (Fig. 5) is set and carries out exhaust control, promptly, when above-mentioned clutch pressure assembly (first clutch oil pressure assembly 14) is assembled, make above-mentioned piston (CSC piston 41) slip enlarge the pressurization of the volume of above-mentioned cylinder chamber (CSC cylinder chamber 42), thereafter, carrying out decompression that above-mentioned piston (CSC piston 41) returns the volume that dwindles cylinder chamber (CSC cylinder chamber 42) this is the exhaust control of unit with pressurization, decompression.

Therefore, after the assembling of clutch pressure assembly (first clutch oil pressure assembly 14), can guarantee oil pressure responsiveness (clutch pressure responsiveness) from the initial stage of vehicle driving.

(4) to make the pressurization of the command value of above-mentioned exhaust control, decompression waveform be step-like waveform to above-mentioned exhaust control device (5).(Fig. 6).

Therefore,, suppress dead time and can pressurize fast and reduce pressure, can realize the bleeding shorteningization of time by the exhaust control action.

(5) above-mentioned exhaust control device (Fig. 5) carries out with pressurization, decompression unit to once and the output (Fig. 6) of the above-mentioned exhaust control command value of counting to reach stipulated number before the exhaust condition of guaranteeing regulation oil pressure responsiveness.

Therefore, by only carrying out pressurization, the decompression of the big number of times of exhaust effect, realize high exhaust effect thus, and can realize the bleeding shorteningization of time.That is, be the exhaust control of unit once with pressurization, decompression, when surpassing certain number of times, air displacement suppresses very for a short time, and the residual air amount is almost state stably.

(6) above-mentioned exhaust control device (Fig. 5) is measured in advance and is carried out above-mentioned pressurization command value from output and begin to reach the needed time of maximum travel position to above-mentioned piston (CSC piston 41), the command value of carrying out above-mentioned decompression with output begins to make above-mentioned piston (CSC piston 41) return the needed time of primary position to the active force that utilizes above-mentioned force application device (diaphragm spring 43), sets based on the time data of said determination and pressurizes from finishing once, reduces pressure the time to the beginning of pressurizeing, reduce pressure next time of beginning.

Therefore, the moment according to finishing along with a bleeding of the stroke of piston (CSC piston 41), begin bleeding next time, thereby can not lose air displacement, can realize the bleeding shorteningization of time.

(7) above-mentioned oil circuit is by pipe arrangement (the interior pipe arrangement 51 that connects above-mentioned oil pressure assembly (first clutch oil pressure assembly 14) and above-mentioned control valve (first clutch control valve 6), outer pipe arrangement 53) oil circuit that inwall forms, above-mentioned cylinder (CSC cylinder 40) with when pressurization with above-mentioned pipe arrangement (interior pipe arrangement 51, outer pipe arrangement 53) Nei the air mode that is sent to above-mentioned cylinder chamber (CSC cylinder chamber 42) is stipulated the volume of above-mentioned cylinder chamber (CSC cylinder chamber 42), above-mentioned exhaust control device (Fig. 5) during with pressurization with above-mentioned pipe arrangement (interior pipe arrangement 51, oil pressure size (regulation oil pressure PLs) when outer pipe arrangement 53) Nei the air mode that is sent to above-mentioned cylinder chamber (CSC cylinder chamber 42) is stipulated to pressurize.

Therefore, even oil pressure assembly (first clutch oil pressure assembly 14) and the situation that control valve (first clutch control valve 6) uses pipe arrangement (interior pipe arrangement 51, outer pipe arrangement 53) to be connected also can be discharged residual air reliably with bleeding efficiently.

(8) have by above-mentioned oil pressure assembly (first clutch oil pressure assembly 14) and connect, the clutch (first clutch CL1) that discharges, above-mentioned clutch (first clutch CL1) is mounted in possesses motor Eng and motor (motor/generator MG) and driving wheel (left and right sides trailing wheel RL, RR) between above-mentioned motor Eng in the hybrid drive train and the above-mentioned motor (motor/generator MG), be released when the selection of electric automobile during traveling pattern (EV pattern), driving mode coupled when the selection of hybrid vehicle driving mode (HEV pattern) is selected clutch.

Therefore, use exhaust control of the present invention in the demanding clutch of oil pressure responsiveness (first clutch CL1), thereby can realize that the two gets both as the driving force performance of motor vehicle driven by mixed power and fuel consumption performance (reduction fuel consumption).

(9) in the method for exhausting that possesses the oil pressure assembly (first clutch oil pressure assembly 14) and the hydraulic pressure control device (clutch oil pressure control device) of the control valve (first clutch control valve 6) that is connected with this oil pressure assembly (first clutch oil pressure assembly 14) via oil circuit, above-mentioned oil pressure assembly (first clutch oil pressure assembly 14) has: possess the cylinder (CSC cylinder 40) of supplying with the cylinder chamber (CSC cylinder chamber 42) of oil from oily supply source; Form above-mentioned cylinder chamber (CSC cylinder chamber 42) with this cylinder (CSC cylinder 40), the piston (CSC piston 41) that above-mentioned relatively cylinder (CSC cylinder 40) slides when above-mentioned cylinder chamber (CSC cylinder chamber 42) supplies with the above-mentioned oil of discharge; To the force application device (diaphragm spring 43) of the volume shrinking side that makes above-mentioned cylinder chamber (CSC cylinder chamber 42) to above-mentioned piston (the CSC piston 41) application of force; Be arranged on the above-mentioned cylinder (CSC cylinder 40), supply with the oil of the above-mentioned oil circulation of discharging to above-mentioned cylinder chamber (CSC cylinder chamber 42) and supply with exhaust port 44, above-mentioned control valve possesses above-mentioned piston (CSC piston 41) makes above-mentioned cylinder chamber (CSC cylinder chamber 42) when volume dwindles under above-mentioned force application device (diaphragm spring 43) application of force effect, supply with exhaust port 44 via above-mentioned oil and will be present in the valve (guiding valve 60) of the air of above-mentioned cylinder chamber (CSC cylinder chamber 42) to oily discharge portion (food tray 39) discharge, this method for exhausting has: assembling procedure, assemble above-mentioned oil pressure assembly (first clutch oil pressure assembly 14) and above-mentioned control valve (first clutch control valve 6); Deairing step, after the above-mentioned assembling, above-mentioned piston (CSC piston 41) is slided and enlarge the pressurization of the volume of above-mentioned cylinder chamber (CSC cylinder chamber 42), carry out above-mentioned piston (CSC piston 41) to return and dwindle the decompression of the volume of above-mentioned cylinder chamber (CSC cylinder chamber 42) thereafter, along with the volume of above-mentioned cylinder chamber (CSC cylinder chamber 42) dwindles, the air that will be present in above-mentioned cylinder chamber (CSC cylinder chamber 42) is discharged to above-mentioned oily discharge portion (food tray 39).The method for exhausting of the hydraulic pressure control device (clutch oil pressure control device) of the oil pressure responsiveness (clutch pressure responsiveness) that can not cause the increase of cost and weight and guarantee oil pressure assembly (first clutch oil pressure assembly 14) therefore, can be provided.

(embodiment 2)

Repeat stipulated number ON, OFF with respect to embodiment 1 and carry out exhaust, embodiment 2 observes the responsiveness of piston stroke with respect to the oil pressure instruction, judge whether responsiveness is specified value (responsiveness of the responsiveness when being equivalent to exhaust), be judged as and finish exhaust when reaching specified value, and the example of finishing control.

At first, formation is described.

Figure 11 is the flow process (exhaust control device) of expression with the flow process of the exhaust control processing of embodiment 2 integrated controller 10 execution.Below, each step of Figure 11 is described.

Initial stage, in assembly line, the signal of beginning being controlled in exhaust from the controller of equipment side sent to integrated controller 10 beginning exhausts controls when assembling.In addition, main oil pump M-O/P is driven the input shaft of automatic transmission AT and is driven the discharge compressed oil by the driving source of equipment side.

In step S21, via 7 couples of solenoid valve 61a of AT controller output oil pressure command value ON, enter step S22 from integrated controller 10.

Among the step S22, continue the output of the oil pressure command value ON of step S21, judge whether actual CSC piston stroke amount St is more than the CSC piston stroke amount St_1 (release side) of regulation, at YES (under the situation of St 〉=St_1), enter step S24, (under the situation of St＜St_1), enter step S23 at NO.

At this, " CSC piston stroke amount St_1 " is the release side mark definite value (with reference to Figure 12) of CSC piston stroke amount.

Among the step S23, continue the judgement of St＜St_1 of step S22, whether judgement opens (ON) more than the time T on_1 at the oil pressure of regulation from the ON clocking value Ton that the output of oil pressure command value ON begins to start, (enter step S24 under the situation of Ton 〉=Ton_1), (situation of Ton＜Ton_1) is returned step S21 at NO at YES.

At this, " oil pressure is opened (ON) time T on_1 " is defined as the time of the pressurization instruction (oil pressure command value ON) that is equivalent to embodiment 1.

In step S24, continue the judgement of St 〉=St_1 of step S22, or the judgement of Ton 〉=Ton_1 of step S23, or the judgement of Toff＞Toff_1 of step S26, via 7 couples of solenoid valve 61a of AT controller output oil pressure command value OFF, enter step S25 from integrated controller 10.

In step S25, continue the output of the oil pressure command value OFF of step S24, judge that actual CSC piston stroke amount St is whether below the CSC piston stroke amount St_2 (attachment side) of regulation, (enter step S27 under the situation of St≤St_2), (enter step S26 under the situation of St＞St_2) at YES at NO.

At this, " CSC piston stroke amount St_2 " is the specified value (with reference to Figure 12) that is equivalent to the stroke that the connection of CSC piston stroke amount finishes.

In step S26, continue the judgement of St＞St_2 of step S25, whether the OFF clocking value Toff that judgement begins to start from the output of oil pressure command value OFF closes (OFF) more than the time T off_1 at the oil pressure of regulation, (enter step S27 under the situation of Toff 〉=Toff_1), (situation of Toff＜Toff_1) is returned step S24 at NO at YES.

At this, " oil pressure closes (OFF) time T off_1 " is defined as the time (with reference to Figure 12) of the decompression instruction (oil pressure command value OFF) that is equivalent to embodiment 1.

In step S27, continue the judgement of St≤St_2 of step S25, or the judgement of Ton 〉=Toff_1 of step S26, judge whether actual CSC piston stroke response time T is below the CSC piston stroke response time T_1 of regulation, (carry out to end under the situation of T≤T_1), (situation of T＞T_1) is returned step S21 at NO at YES.

At this, " CSC piston stroke response time T_1 " arrive from the output time of oil pressure command value ON to first clutch CL1 the release travel position the moment, the needed piston stroke time was defined as exhaust the time the institute of responsiveness want the time.

In addition, it is identical with the formation of Fig. 1 of embodiment 1～shown in Figure 4 that embodiment 2 hardware constitutes, and omits to illustrate and explanation.

Below, embodiment 2 exhaust control action is described.

The sign on of controlling to integrated controller 10 output exhausts from the controller of equipment side among the embodiment 2, beginning exhaust control.

Integrated controller 10 is via AT controller 7 output pressurization instruction (oil pressure command value ON) (step S21), and thereafter, whether the piston stroke of judging CSC piston 41 advances to and make first clutch CL1 release (step S22).Piston stroke at CSC piston 41 does not advance under the situation that makes first clutch CL1 release, judge whether transit time behind the output oil pressure command value ON pass through the stipulated time (as long as exhaust, the time longer than the time that can discharge first clutch CL1, even the time that also can pressurize fully of exhaust not, be equivalent to ON time of embodiment 1) (step S23).And, the piston stroke of CSC piston 41 marches to the situation (YES among the step S22) that first clutch CL1 is discharged, or the piston stroke of CSC piston 41 does not march to first clutch CL1 is discharged, through the situation (YES among the step S23) of stipulated time, integrated controller 10 is via the 7 output decompression instructions (oil pressure command value OFF) (step S24) of AT controller.

After the oil pressure command value OFF output, the piston stroke of CSC piston 41 marches to the situation (YES among the step S25) that first clutch CL1 is connected, or CSC piston 41 piston strokes do not march to first clutch CL1 are connected, through stipulated time (even exhaust, time, suitable that can connect first clutch CL1), confirm whether the piston stroke responsiveness is the responsiveness (step S27) of regulation with OFF time of embodiment 1.And, as long as the responsiveness for stipulating is judged as exhaust, and finish exhaust control (carrying out to end) from step S27.

Like this, the responsiveness of the piston stroke of CSC piston 41 according to output oil pressure command value ON after, how long the piston stroke of CSC piston 41 need be judged to discharging first clutch CL1.

In embodiment 2, the actual CSC piston stroke response time T of expression piston stroke responsiveness equals the output time Ton of the later oil pressure command value ON second time respectively.This T (=Ton) as long as, finish exhaust control for below the CSC piston stroke response time T_1 of expression prescribed response (as long as exhaust, be the time that can discharge first clutch CL1, for example, about 0.5 second).

The CSC piston 41 of representing in the time diagram of Figure 12 to pressurize does not for the first time pass through the situation that the stipulated time begins to reduce pressure in fully advancing.But, discharge the air that compresses when representing its decompression, for the second time the situation that CSC piston 41 can be advanced fully in the pressurization.

However, because of air is fully discharged, so when expression is pressurizeed for the second time from CSC piston stroke response time T_1 to the CSC piston 41 of the judging responsiveness established amount needed time of only advancing.

In decompression operation thereafter, exhaust again, so in the pressurization for the third time with the identical time of CSC piston stroke response time T_1 of judging responsiveness, the piston stroke of CSC piston 41 arrives St_1.Judge constantly at this and to guarantee responsiveness, finish the exhaust control processing.

Situation with respect to embodiment's 1 consideration is difficult to exhaust must repeat ON, OFF to certain rich amount, in embodiment 2, as mentioned above, as long as guarantee responsiveness, just can finish exhaust control.Therefore, embodiment 2 compares with embodiment 1, and the short time is finished exhaust control fast.

In addition, ON separately, OFF time, keep a certain amount of surplus relative with necessary among the embodiment 1, when piston stroke reaches established amount among the embodiment 2, can finish ON, OFF respectively, so can shorten ON, OFF time.

In addition, other effect is identical with embodiment 1, omits explanation.

Below, description effect.

Effect below in embodiment 2 clutch oil pressure control device, accessing.

(10) above-mentioned exhaust control device (Figure 11) monitors and stroke responsiveness as the corresponding above-mentioned piston of output (CSC piston 41) of the command value of the above-mentioned exhaust control of pressurization, decompression unit, and the specified value that the value of expression stroke responsiveness reaches when being equivalent to exhaust is finished exhaust control.

Therefore, except that the effect of embodiment 1 (1)～(4), as long as guarantee responsiveness, just can finish exhaust control, also can shorten ON, OFF time, therefore compare with embodiment 1, the short time is finished exhaust control as early as possible.

More than, method for exhausting based on embodiment 1 and embodiment's 2 explanation hydraulic pressure control devices of the present invention and hydraulic pressure control device still, is not limited to these embodiments for concrete formation, only otherwise break away under the aim of request scope of the present invention, permitted to be installed with the meter change and appended etc.

The oil pressure control loop that expression is still prolonged with first clutch CL1 among the

embodiment

1,2 constitutes, and utilizes control automatically to carry out the example of the switching valve of oil pressure open and close.But,, in addition, also can be structure with manually operated switching valve for exhaust control also can design oil hydraulic circuit in addition.

The example of implementing exhaust control when among the

embodiment

1,2 initial stage being assembled is illustrated, still, also can be when repairing assembling and the oil pressure responsiveness implement exhaust control when reducing.When repairing assembling, the exterior terminal of the controller of the equipment side of the commencing signal of output exhaust control is connected with integrated controller 10, by controlling from exterior terminal output exhaust control sign on realization exhaust.In addition, when the oil pressure responsiveness reduces, confirm the clutch pressure responsiveness, judge the situation of the responsiveness that does not obtain wishing, connect igniting next time, drive auxiliary oil pump S-O/P, carry out exhaust control with trigger by integrated controller 10.

Expression is arranged on the application examples of first clutch CL1 of the normally closed dry clutch of hybrid drive train in embodiment 1,2.But, also can adapt to hydraulic pressure control device of the present invention for clutch of often opening that connects, discharges by oil pressure and wet clutch etc.In addition, be not limited to the oil pressure control of the hydraulic pressure control device of clutch, also go for having in the hydraulic pressure control devices such as variable v-belt drive of the movable wheel of utilizing the oil pressure action.Just, just can use the present invention as long as possess the hydraulic pressure control device of oil pressure assembly, oil circuit, control valve, oily supply source, oily discharge portion.

Claims

1. hydraulic pressure control device, it possesses the oil pressure assembly, via oil circuit and the control valve that this oil pressure assembly is connected, it is characterized in that,

Described oil pressure assembly possesses:

Cylinder, it possesses the cylinder chamber, supplies with oil from oily supply source to this cylinder chamber;

Piston, it forms described cylinder chamber with this cylinder, and when supplying with described oil to described cylinder chamber or described oil discharged from described cylinder chamber, the described relatively cylinder of this piston slides;

Force application device, it reduces side to the described piston application of force to the volume that makes described cylinder chamber;

Oil is supplied with exhaust port, and it is arranged at described cylinder, and supplies to the described oil of described cylinder chamber and supply with the exhaust port circulation from the described oil of described cylinder chamber discharge at this oil,

Described control valve possesses valve, and by the described force application device application of force and when the volume of described cylinder chamber is dwindled, described valve is supplied with the air that exhaust port will be present in described cylinder chamber via described oil and discharged to oily discharge portion at described piston,

Described oil supply with exhaust port be arranged on via described control valve when described oil is supplied with in described cylinder chamber, be present in the top position of the described cylinder that the air of described cylinder chamber concentrates.

2. hydraulic pressure control device as claimed in claim 1 is characterized in that,

Possess described oily discharge portion and supply with oily oil pump to described cylinder chamber,

Described oily discharge portion is stored the described oil of discharging from described cylinder chamber,

Described oil pump sucks the described oil that described oily discharge portion is stored, and described oil is supplied to described cylinder chamber.

3. hydraulic pressure control device as claimed in claim 1 or 2 is characterized in that,

Possesses exhaust control device, this exhaust control device is when the described oil pressure assembly of assembling, described piston is slided and enlarge the pressurization of the volume of described cylinder chamber, thereafter, described piston is returned and the decompression of dwindling the volume of cylinder chamber is the exhaust control of unit like this with pressurization, decompression.

4. hydraulic pressure control device as claimed in claim 3 is characterized in that,

It is step-like waveform that described exhaust control device makes the pressurization of the command value of described exhaust control, the waveform of decompression.

5. hydraulic pressure control device as claimed in claim 3 is characterized in that,

Described exhaust control device carries out with pressurization, the decompression unit output for the command value of the described exhaust control once counted with the stipulated number that reaches the exhaust condition of guaranteeing the oil pressure responsiveness stipulated.

6. hydraulic pressure control device as claimed in claim 5 is characterized in that,

Described piston reached the needed time of maximum travel position after described exhaust control device was determined in advance and exports the command value of carrying out described pressurization; And carry out in output utilizing the described piston of active force of described force application device to turn back to the needed time of initial position after the command value of described decompression, and set based on the time data of described mensuration and once to pressurize, to reduce pressure and finish the back and begin the preceding time to pressurize, reduce pressure next time.

7. hydraulic pressure control device as claimed in claim 1 or 2 is characterized in that,

Described oil circuit is the oil circuit that the inwall by the pipe arrangement that connects described oil pressure assembly and described control valve forms,

Described cylinder is stipulated the volume of described cylinder chamber with when pressurization with the mode that the air in the described pipe arrangement is sent to described cylinder chamber,

Oil pressure size when described exhaust control device is sent to the mode regulation pressurization of described cylinder chamber with when pressurization with the air in the described pipe arrangement.

8. hydraulic pressure control device as claimed in claim 1 or 2 is characterized in that,

Have the clutch that connects, discharges by described oil pressure assembly,

Described clutch is to be installed on to possess motor, between the described motor and described motor in the hybrid drive train of motor and driving wheel, be released when the selection of electric automobile during traveling pattern, coupled driving mode is selected clutch during the selection at the hybrid vehicle driving mode.

9. hydraulic pressure control device as claimed in claim 3 is characterized in that,

Described exhaust control device monitors described piston with respect to the stroke responsiveness of output as the described exhaust control command value of pressurization, decompression unit, when the value of expression stroke responsiveness reaches specified value when being equivalent to exhaust and finishing, finishes exhaust control.

10. the method for exhausting of a hydraulic pressure control device, this hydraulic pressure control device possess the oil pressure assembly, via oil circuit and the control valve that this oil pressure assembly is connected, it is characterized in that,

Described oil pressure assembly possesses:

Oil is supplied with exhaust port, and it is arranged at described cylinder chamber, and supplies to the described oil of described cylinder chamber and supply with the exhaust port circulation from the described oil of described cylinder chamber discharge at this oil,

Described control valve possesses valve, at described piston by the described force application device application of force and when the volume of described cylinder chamber is dwindled, and when described oil being supplied to described cylinder chamber via described control valve, described valve is discharged to oily discharge portion via the air that described oil supply exhaust port will be present in described cylinder chamber

The method for exhausting of this hydraulic pressure control device comprises:

Assembling procedure is assembled described oil pressure assembly and described control valve;

Deairing step, after described assembling, described piston is slided and enlarge the pressurization of the volume of described cylinder, thereafter, described piston is returned and dwindle the decompression of the volume of described cylinder chamber, be accompanied by dwindling of described cylinder chamber volume, the air that will be present in described cylinder chamber is discharged to described oily discharge portion.