CN104553770B - Hydraulic pressure feeding mechanism - Google Patents

Abstract

A kind of hydraulic pressure feeding mechanism is provided, the hydraulic pressure feeding mechanism can avoid the damaged of the 1st accumulator and being capable of miniaturization of the apparatus.1st accumulator (65) of hydraulic pressure feeding mechanism has：Cylinder body (65a)；Piston (65b), which is slidably disposed in, and cylinder body (65a) is internal, by the 1st pressure accumulating chamber (65d) that cylinder body (65a) inside division is back side room (65e) and accumulation hydraulic pressure；1st forcing unit (65c), its 1 pressure accumulating chamber side of Chao exert a force to piston (65b)；Intercommunicating pore (65g), its are formed in piston (65b), make the 1st pressure accumulating chamber (65d) communicate with each other with back side room (65e)；Valve body (65h), which is arranged on, and cylinder body (65a) is internal, can move between the detent position for closing intercommunicating pore (65g) release position open with intercommunicating pore (65g) is made；And the 2nd forcing unit (65c), it is internal which is arranged on cylinder body (65a), so that the mode that valve body (65h) is maintained at detent position exerts a force, when hydraulic pressure in the 1st pressure accumulating chamber (65d) reaches the higher limit of regulation, it is allowed to which valve body (65h) is from detent position to release position side shifting.

Description

Hydraulic pressure feeding mechanism

Technical field

The present invention relates to supplying the hydraulic pressure feeding mechanism that object supplies hydraulic pressure to hydraulic pressure.

Background technology

In the past, as this hydraulic pressure feeding mechanism, for example known structure having disclosed in patent document 1.The hydraulic pressure supply Device is arranged at the vehicle using engine as power source, and the clutch supply hydraulic pressure that advances to the vehicle.Hydraulic pressure Feeding mechanism has：Hydraulic pump, which is with above-mentioned engine as driving source；And, main line, its are used for from the hydraulic pump Hydraulic pressure is fed to clutch.The main line is connected with accumulator via looped pipeline road.Additionally, being provided with by magnetic valve in looped pipeline road The stop valve of composition, makes looped pipeline road opening and sealing using the opening and closing of the stop valve.

In the hydraulic pressure feeding mechanism of above structure, when engine operates, using hydraulic pump driven by the engine come Via supervisor's road direction clutch supply hydraulic pressure.Additionally, make looped pipeline road keep open state using stop valve, thus will be from hydraulic pressure The hydraulic pressure of pump is fed to accumulator and puts aside via main line and looped pipeline road.Additionally, when engine automatic stop, utilizing Stop valve closes looped pipeline road, thus makes to end between accumulator and main line, so as to keep putting aside in accumulator so far In hydraulic pressure.Additionally, when the engine under automatic stop condition is reset, opening looped pipeline road using stop valve, with this Together, the hydraulic pressure that puts aside in accumulator is supplied to clutch via looped pipeline road and main line.

Patent document 1：Japanese Patent Publication No. 3807145

Content of the invention

As described above, in conventional hydraulic pressure feeding mechanism, when engine operates, from the higher liquid of hydraulic pump Pressure is fed to accumulator via main line and looped pipeline road.Therefore, in being automatically stopped of engine, in order to keep putting aside in storage Hydraulic pressure in depressor and when utilizing stop valve to close the loop including the looped pipeline road and including accumulator, in the closing being closed The hydraulic pressure of high pressure from hydraulic pump is directly put aside in loop.Additionally, the working oil pumped out from hydraulic pump is used for clutch Engagement and lubrication, therefore, its temperature rises with the process of the duration of runs of engine.Thus, in above-mentioned loop, Very high hydraulic pressure is have accumulated, it is possible to it is damaged to occur accumulator and looped pipeline road.

Additionally, in order to avoid the hydraulic pressure in the problems referred to above, release loop, it is considered to further arrange overflow mechanism, but It is in this case, makes device correspondingly become to maximize because of the overflow mechanism.

The present invention is completed to solve above such problem, it is therefore intended that is provided one kind and can be avoided the 1st storage The hydraulic pressure feeding mechanism that is damaged and being capable of miniaturization of the apparatus of depressor.

In order to reach above-mentioned purpose, the hydraulic pressure feeding mechanism of the invention of first aspect is characterized by：Hydraulic pump 31, Which is used for supplying object to hydraulic pressure ((below, in this identical) LU clutch 4c, buncher 6 in embodiment, front Enter the hydraulic pressure that 13) clutch 12, reverse brake supplies work；And the 1st accumulator (auxiliary accumulator 65), itself and hydraulic pressure Supply object and hydraulic pump 31 connect, and for accumulating hydraulic pressure, the 1st accumulator is configured to have：Cylinder body 65a；Piston 65b, its It is slidably disposed in inside cylinder body 65a, is the 1st (pressure accumulating chamber of pressure accumulating chamber for accumulating hydraulic pressure by cylinder body 65a inside divisions 65d) with back side room 65e；1st forcing unit (spring 65c), its 1 pressure accumulating chamber side of Chao exert a force to piston 65b；Intercommunicating pore 65g, Which is formed in piston 65b, makes the 1st pressure accumulating chamber communicate with each other with back side room 65e；Valve body 65h, its are arranged in cylinder body 65a Portion, can move between the detent position for making intercommunicating pore 65g closings and the release position for making intercommunicating pore 65g openings；And the 2nd Forcing unit (spring 65c), which is arranged on inside cylinder body 65a, is exerted a force in the way of making valve body 65h be maintained at detent position, Also, when the hydraulic pressure in the 1st pressure accumulation room reaches the higher limit of regulation, it is allowed to which valve body 65h is from detent position to release position side Mobile.

According to the structure, the hydraulic pressure of object supply work supplied from hydraulic pump to hydraulic pressure, also, for accumulating hydraulic pressure 1st accumulator supplies object with hydraulic pressure and hydraulic pump is connected.Additionally, the 1st accumulator has cylinder body and a piston, piston is with can The mode of slip is arranged on cylinder interior, and cylinder interior is divided into the 1st pressure accumulating chamber and the back side room of accumulation hydraulic pressure by piston.This Outward, piston is by 1 pressure accumulating chamber's side forces of the 1st forcing unit Chao.Additionally, being formed with intercommunicating pore in piston so that the 1st pressure accumulating chamber Communicate with each other with back side room, in cylinder interior, be provided with valve body and the 2nd forcing unit.

The valve body can be moved between the detent position for making intercommunicating pore closing and the release position for making intercommunicating pore opening, the 2 forcing units are exerted a force in the way of making valve body be maintained at detent position, also, the hydraulic pressure in the 1st pressure accumulation room reaches regulation During higher limit, it is allowed to which valve body is from detent position to release position side shifting.Thus, the hydraulic pressure in the 1st pressure accumulation room becomes larger When, open by valve body intercommunicating pore, thus, make to connect between the 1st pressure accumulating chamber and back side room by intercommunicating pore, because This, can make the excess electron excess fraction of the hydraulic pressure in the 1st pressure accumulation room be discharged in the room of the back side and prevent its excessiveization such that it is able to be avoided The breakage of the devices such as the 1st accumulator.

Additionally, as described above, intercommunicating pore, valve body and the 2nd forcing unit play a role as so-called overflow mechanism.Root According to said structure, these intercommunicating pores, valve body and the 2nd forcing unit are not dividually configured with the 1st accumulator, but It is arranged in the cylinder body of the 1st accumulator, therefore, it is possible to miniaturization of the apparatus.

The invention of second aspect is characterised by that, in the hydraulic pressure feeding mechanism described in first aspect, hydraulic pump 31 is with car Power source (engine 3) be driving source, the hydraulic pressure feeding mechanism also has：2nd accumulator (main accumulator 63), its have Have and the 2nd pressure accumulating chamber (pressure accumulating chamber 63d) that object and hydraulic pump 31 are connected is supplied with hydraulic pressure, for by the liquid from hydraulic pump 31 Pressure is accumulated in the 2nd pressure accumulating chamber；Stop valve 64, consisting of to make hydraulic pressure supply object and hydraulic pump 31 and the 2nd pressure accumulating chamber Between connection/cut-off, the 1st pressure accumulating chamber of the 1st accumulator connected with hydraulic pressure supply object and hydraulic pump 31 via stop valve 64, And connect with the 2nd pressure accumulating chamber in the way of not via stop valve 64.

According to the structure, hydraulic pump is with the power source of vehicle as driving source.Additionally, the 2nd pressure accumulating chamber of the 2nd accumulator and liquid Pressure supply object and hydraulic pump connection, can accumulate the hydraulic pressure from hydraulic pump.Additionally, by stop valve, supplying hydraulic pressure Connect/end between object and hydraulic pump and the 2nd pressure accumulating chamber.By the connection of the stop valve, can be by from hydraulic pump Hydraulic pressure is accumulated in the 2nd pressure accumulating chamber, by the cut-off of stop valve, closes can the 2nd pressure accumulating chamber, thereby, it is possible to keep the 2nd pressure accumulation The hydraulic pressure that accumulates in room.Furthermore it is possible to by the connection based on stop valve, supply in the 2nd pressure accumulating chamber to hydraulic pressure supply object and store Long-pending hydraulic pressure.

Additionally, the 1st pressure accumulating chamber of the 1st accumulator described in the explanation of the invention of first aspect is via stop valve and liquid Pressure supply object and hydraulic pump connection, therefore, by the cut-off based on above-mentioned stop valve, except seal can the 2nd pressure accumulating chamber Beyond closing, additionally it is possible to close the 1st pressure accumulating chamber, therefore, it is possible to keep the hydraulic pressure that accumulates in Liang Ge pressure accumulating chamber.Additionally, the 1st pressure accumulation Room is connected with the 2nd pressure accumulating chamber in the way of not via stop valve, therefore, it is possible to pass through to chat in the explanation of the invention of first aspect The overflow mechanism (intercommunicating pore/valve body/the 2nd forcing unit) that states is preventing be closed due to the cut-off based on stop valve to include Excessiveization of the hydraulic pressure (working oil) in the loop of the 1st pressure accumulating chamber and the 2nd pressure accumulating chamber such that it is able to avoid the 1st accumulator With breakages such as the 2nd accumulators.

The invention of the third aspect is characterised by that, in the hydraulic pressure feeding mechanism described in second aspect, stop valve 64 is by electricity Magnet valve is constituted, and the magnetic valve can optionally be controlled to the non-return valve mode that plays a role as check-valves and be forced to beat The valve opening pattern that opens, under non-return valve mode, the hydraulic pressure in the 2nd pressure accumulating chamber side supplies object and hydraulic pump 31 side less than hydraulic pressure Hydraulic pressure when, make hydraulic pressure supply object and hydraulic pump 31 and the 2nd pressure accumulating chamber between connect, the 2nd pressure accumulating chamber side hydraulic pressure height When hydraulic pressure supplies the hydraulic pressure of object and hydraulic pump 31 side, make hydraulic pressure supply object and hydraulic pump 31 and the 2nd pressure accumulating chamber it Between end.

According to the structure, stop valve is made to be configured to optionally be controlled to non-return valve mode and valve opening pattern, in non-return Under valve mode, when the hydraulic pressure of the 2nd pressure accumulating chamber side is less than the hydraulic pressure that hydraulic pressure supplies object and hydraulic pressure pump side, hydraulic pressure is made for reply As and hydraulic pump and the 2nd pressure accumulating chamber between connect, the hydraulic pressure in the 2nd pressure accumulating chamber side supplies object and hydraulic pump higher than hydraulic pressure The hydraulic pressure of side, makes to end between hydraulic pressure supply object and hydraulic pump and the 2nd pressure accumulating chamber.Thereby, it is possible to be effectively based on The effect above of the invention of second aspect, i.e. the hydraulic pressure from hydraulic pump is accumulated in the 2nd pressure accumulating chamber and can keep being stored Effect as long-pending hydraulic pressure.Additionally, under non-return valve mode, it is not necessary to special for switched over to the opening and closing of stop valve Control action, therefore, it is possible to simply carry out the accumulation/holding of hydraulic pressure to the 2nd pressure accumulating chamber.

The invention of fourth aspect is characterised by, in the hydraulic pressure feeding mechanism described in the third aspect, the 1st forcing unit with And the 2nd forcing unit be made up of public single force application part (spring 65c) each other, force application part is towards detent position side to valve Body 65h exerts a force, and piston 65b is exerted a force via 1 pressure accumulating chamber sides of valve body 65h Chao.

According to the structure, the 1st forcing unit and the 2nd forcing unit are made up of public single force application part each other, Therefore, number of components can correspondingly be cut down because of the part.Additionally, being applied to valve body towards detent position side using the force application part Power, and piston is exerted a force via 1 pressure accumulating chamber sides of valve body Chao, thereby, it is possible to suitably carry out valve body towards the holding of detent position Accumulation with the hydraulic pressure based on the 1st accumulator.

Invention in terms of 5th is characterised by that, in the hydraulic pressure feeding mechanism described in fourth aspect, valve body 65h is formed as Spherical, abutted by making valve body 65h and the edge of intercommunicating pore 65g, close intercommunicating pore 65g.

According to the structure, close intercommunicating pore by making valve body abut with the edge of intercommunicating pore.Additionally, valve body is formed as Spherical, therefore, it is possible to suppress the unilateral of the edge towards intercommunicating pore to abut such that it is able to using valve body come suitably closed communication Hole.

Invention in terms of 6th is characterised by, in the hydraulic pressure feeding mechanism described in any one in the second～five, The back side room 65e of the 1st accumulator in the way of not via stop valve 64 supplies object with hydraulic pressure and hydraulic pump 31 is connected.

According to the structure, the back side room of the 1st accumulator supplies object with hydraulic pressure and hydraulic pump is connected, therefore, in hydraulic pressure In pump operating, the hydraulic pressure from hydraulic pump is supplied in the back side room.Back side room be between across the 1st accumulator piston and The side contrary with the 1st pressure accumulating chamber marks off, and therefore, in hydraulic pump operating, is fed to the hydraulic pressure of back side room as back pressure And play a role, thus, 1 pressure accumulating chamber's side pushing pistons of Chao.So, in hydraulic pump operating, piston is single by the above-mentioned 1st force The active force of unit and this both sides of back pressure effect and pushed by 1 pressure accumulating chamber sides of Chao, therefore, single by suitably setting the 1st force The active force of unit, can be such that the hydraulic pressure from hydraulic pump hardly accumulates in the 1st pressure accumulating chamber, and suitably accumulate in above-mentioned the 2nd pressure accumulating chamber of 2 accumulators.

Additionally, when stopping hydraulic pump, no longer effect has above-mentioned back pressure therewith.Additionally, back side room is with not via cut-off The mode of valve and hydraulic pressure supply object and hydraulic pump is connected, therefore, be closed because of the cut-off based on stop valve comprising the 2nd Hydraulic pressure in the loop of pressure accumulating chamber is no longer supplied to back side room.Additionally, as described above, the 1st pressure accumulating chamber of the 1st accumulator with Mode not via stop valve is connected with the 2nd pressure accumulating chamber of the 2nd accumulator.From the description above, for example, because being based on above-mentioned section Only the connection of valve and the hydraulic pressure from hydraulic pump is accumulated in the 2nd pressure accumulating chamber, and hydraulic pump stop in using be based on stop valve Cut-off, in the case of keeping the hydraulic pressure being accumulated in the 2nd pressure accumulating chamber so far, following effect can be obtained.

That is, according to said structure, as hydraulic pump stops, only the active force of the 1st forcing unit is used as towards the 1st pressure accumulation Room side pushes the pushing force of the piston of the 1st accumulator playing a role.Therefore, it is possible to pass through suitably to set the 1st forcing unit Active force, using the hydraulic pressure accumulate in the loop of valve closure is cut off, make piston resist the active force of the 1st forcing unit And towards back side room side shifting, a part for the hydraulic pressure (working oil) in the loop can be fed to the 1st pressure accumulating chamber, and store Product is wherein.Therefore, in hydraulic pump stopping, the hydraulic pressure in loop can be made to reduce its redundance.Thus, as Stop valve, the small-sized stop valve that resistance to pressure can be adopted relatively low, therefore, it is possible to realize the manufacturing cost of hydraulic pressure feeding mechanism Cut down.

Additionally, for example, when the operating of hydraulic pump is started again at, in the case where the connection based on stop valve has been carried out, As the hydraulic pressure that accumulates in the 2nd pressure accumulating chamber is supplied to hydraulic pressure supply object, by this pair of the active force of back pressure and the 1st forcing unit The pushing force that side is constituted pushes the pushing force of the piston of the 1st accumulator to play a role again as 1 pressure accumulating chamber sides of Chao.By This, when the operating of hydraulic pump is started again at, economically can will be accumulated in the 1st pressure accumulating chamber in the stopping of above-mentioned hydraulic pump Hydraulic pressure (working oil) be fed to together with the hydraulic pressure from the 2nd pressure accumulating chamber hydraulic pressure supply object.

Additionally, as described above, when the operating of hydraulic pump is started again at, the work being accumulated in the 1st pressure accumulating chamber can be discharged Make oil, therefore, when hydraulic pump stops again, suitably a part for the hydraulic pressure in loop can be accumulated and store in the 1st Pressure chamber.Therefore, even if in the case where the operating/stopping of hydraulic pump is repeated, it is also possible to effectively obtain the effect above.

Additionally, back side room and hydraulic pressure supply object and hydraulic pump is connected, therefore, by above-mentioned overflow mechanism (intercommunicating pore/ 2 forcing unit of valve body/the) and the hydraulic pressure that is discharged in the room of the back side can further be discharged into hydraulic pressure supply object and hydraulic pump Side, thereby, it is possible to effectively obtain the effect above of the invention of second aspect, i.e., can avoid the 1st accumulator and the 2nd accumulator Effect as damaged.

Description of the drawings

Fig. 1 is the skeleton drawing of the vehicle for roughly illustrating the hydraulic pressure feeding mechanism for applying present embodiment.

Fig. 2 is the hydraulic circuit diagram for illustrating hydraulic pressure feeding mechanism etc..

Fig. 3 is the block diagram for illustrating the ECU of hydraulic pressure feeding mechanism etc..

Fig. 4 is the figure for roughly illustrating pressure accumulater in internal combustion engine operation etc..

Fig. 5 is to illustrate ECU execution, the place of action that is being used for the various valves for controlling hydraulic pressure feeding mechanism as shown in Figure 3 The flow chart of reason.

Fig. 6 is to be less than the situation of the higher limit for specifying for the hydraulic pressure in loop and roughly illustrate oneself of internal combustion engine The figure of the pressure accumulater in dynamic stopping etc..

Fig. 7 is to reach the situation of higher limit for the hydraulic pressure in loop and roughly illustrate being automatically stopped for internal combustion engine In pressure accumulater etc. figure.

Fig. 8 be roughly illustrate internal combustion engine from automatic stop condition reset when pressure accumulater etc. figure.

Fig. 9 is the sequential chart of the action example for illustrating hydraulic pressure feeding mechanism.

Label declaration

3 engines (power source of vehicle)

4c LU clutches (hydraulic pressure supply object)

6 bunchers (hydraulic pressure supply object)

12 forward clutch (hydraulic pressure supply object)

13 reverse brakes (hydraulic pressure supply object)

31 hydraulic pumps

63 main accumulator (the 2nd accumulators)

63d pressure accumulating chamber (the 2nd pressure accumulating chamber)

64 stop valves

65 auxiliary accumulator (the 1st accumulator)

65a cylinder bodies

65b pistons

65c springs (the 1st forcing unit, the 2nd forcing unit, force application part)

65d pressure accumulating chamber (the 1st pressure accumulating chamber)

65e back sides room

65g intercommunicating pores

65h valve bodies

Specific embodiment

Hereinafter, referring to the drawings, the preferred embodiment of the present invention is described in detail.The driving of the vehicle shown in Fig. 1 System has：Internal combustion engine (hereinafter referred to as " engine ") 3, which is the power source of vehicle；And power transmission T, which is used for The left and right sidesing driving wheel DW (illustrate only right driving wheel) that the driving force of the engine 3 is delivered to vehicle.Engine 3 is sent out for gasoline Motivation, its have the bent axle 3a for output driving power.Additionally, power transmission T has torque-converters 4, forward/backward switching Mechanism 5 and buncher 6.

Torque-converters 4 is made up of pump impeller 4a, turbine 4b and lock-up clutch (hereinafter referred to as " LU clutches ") 4c etc..Pump Wheel 4a is coupled with bent axle 3a, and turbine 4b is coupled with input shaft described later 14, is filled with working oil between both 4a, 4b.Substantially On, the driving force (hereinafter referred to as " engine drive power ") of engine 3 is transferred to be input into via pump impeller 4a, working oil and turbine 4b Axle 14.

LU clutches 4c is hydraulic clutch, and LU clutch 4c are provided with 1LU grease chamber 4d and 2LU grease chamber 4e (with reference to Fig. 2).1LU grease chamber 4d are supplied the hydraulic pressure to, and hydraulic pressure (working oil) is discharged from 2LU grease chambers 4e, thus LU Clutch 4c becomes engagement state, in contrast, supplies the hydraulic pressure to 2LU grease chamber 4e, and from 1LU grease chambers 4d by work Oil is discharged, and thus LU clutches 4c becomes release conditions.By the engagement of the LU clutch 4c, make engine 3 bent axle 3a and Become the state of direct connection between input shaft 14.Additionally, the degree of engagement of LU clutch 4c be fed to 1LU grease chambers 4d or The hydraulic pressure (amount of working oil) of 2LU grease chamber 4e and change.

Forward/backward switching mechanism 5 has epicyclic gearing 11, forward clutch 12 and reverse brake 13.Planet Epicyclic gearing of the geared system 11 for single pinion type, which is made up of following part：Central gear 11a；Gear ring 11b；With Multiple planetary gear 11c (only illustrating 2) of central gear 11a and gear ring 11b engagements；And planet carrier 11d, its by these Planetary gear 11c supportings are to rotate.Central gear 11a is arranged with input shaft 14 and is integrated.

Forward clutch 12 is hydraulic clutch, installs with input shaft 14 and be integrated on the inside of which, forward clutch 12 Install with gear ring 11b and main shaft 21 and be integrated in outside.The main shaft 21 is formed as hollow form, on the inside of which in the way of it can rotate It is configured with input shaft 14.Input shaft 14 is made directly to be coupled with main shaft 21 by the engagement of forward clutch 12, by advance clutch The release of device 12 is allowing the differential speed rotation between input shaft 14 and main shaft 21.Additionally, reverse brake 13 by fluid pressure type from Clutch etc. is constituted, and which is installed in planet carrier 11d, and when in engagement state, planet carrier 11d is kept into by reverse brake 13 Cannot rotate, when in release conditions, reverse brake 13 allows the rotation of planet carrier 11d.

Additionally, forward clutch 12 has FWD grease chamber 12a (with reference to Fig. 2), by supplying hydraulic pressure to FWD grease chambers 12a, make Forward clutch 12 becomes engagement state, by stopping the supply of the hydraulic pressure, makes forward clutch 12 become release conditions.This Outward, reverse brake 13 has RVS grease chamber 13a (with reference to Fig. 2), by supplying hydraulic pressure to RVS grease chambers 13a, makes reverse brake 13 become engagement state, by stopping the supply of the hydraulic pressure, make reverse brake 13 become release conditions.12 He of forward clutch The degree of engagement of reverse brake 13 is respectively with the hydraulic pressure (amount of working oil) that supplies to FWD grease chamber 12a and RVS grease chambers 13a And change.

In the forward/backward switching mechanism 5 of above structure, when vehicle advances, forward clutch 12 is engaged, and is discharged Reverse brake 13.Thus, main shaft 21 is rotated with same rotational speed to equidirectional with input shaft 14.On the other hand, after vehicle When moving back, forward clutch 12 is discharged, and engages reverse brake 13.Thus, main shaft 21 is revolved to the direction contrary with input shaft 14 Turn.

Buncher 6 is belt-type transmission, and which possesses the main shaft 21, driving pulley 22, driven pulley 23, transmission belt 24 and countershaft 25.Driving pulley 22 has mutually opposing movable part 22a and fixed part 22b.Movable part 22a is installed on main shaft 21, which can be moved along the axis direction of main shaft 21, and cannot be rotated against, and fixed part 22b is fixed on main shaft 21.At both The trough of belt of V shape is formed between 22a, 22b, and the trough of belt is used for winding transmission belt 24.Additionally, being provided with DR in movable part 22a Grease chamber 22c (with reference to Fig. 2), makes movable part 22a move in the axial direction by supplying hydraulic pressure to DR grease chambers 22c, thus, drives The belt wheel width of movable belt pulley 22 is changed, and its effective diameter changes.

Driven pulley 23 is constituted in the way of same with the driving pulley 22, and its movable part 23a is installed in countershaft 25, Movable part 23a can be moved along the axis direction of countershaft 25 and cannot be rotated, and fixed part 23b is fixed on countershaft 25.At both The trough of belt of V shape is formed between 23a, 23b.Additionally, being provided with DN grease chamber 23c (with reference to Fig. 2) and return bullet in movable part 23a Spring 23d.Movable part 23a is made to move in the axial direction by supplying hydraulic pressure to DN grease chambers 23c, thus the band of driven pulley 23 Wheel width is changed, and its effective diameter changes.Additionally, return spring 23d exerts a force to fixed part 23b sides to movable part 23a. Transmission belt 24 hangs around two belt wheels 22,23 with the state for being embedded in the trough of belt of two belt wheels 22,23.

More than, in buncher 6, by the DN grease chambers of DR grease chambers 22c and driven pulley 23 to driving pulley 22 23c supplies hydraulic pressure, infinitely to change the effective diameter of two belt wheels 22,23, thus carrys out infinitely to control its gear ratio.The speed change Than be driving pulley 22 rotating speed and driven pulley 23 rotating speed ratio.

Additionally, being fixed with gear 25a in countershaft 25, gear 25a is via idler gear IG1, IG2 and differential gear train The gear G engagements of DF, idler gear IG1, IG2 and pony axle IS are arranged and are integrated, and the idler gear IG1, IG2 are one big one Little.Differential gear train DF is coupled with the driving wheel DW of left and right.

In the drive system of above structure, engine drive power is via torque-converters 4, forward/backward switching mechanism 5, nothing Level speed changer 6 and differential gear train DF are transferred to the driving wheel DW of left and right.Now, using forward/backward switching mechanism 5, make The direction of rotation of the driving force of transmission switches between forward direction and reverse directions, thus carries out the forward/backward of vehicle.This Outward, engine drive power is passed to driving wheel DW in the state of variable speed is carried out by buncher 6.

Next, with reference to Fig. 2, illustrate to hydraulic pressure feeding mechanism, the hydraulic pressure feeding mechanism is to above-mentioned LU clutches 4c The the 1st and 2LU grease chamber 4d, 4e, the FWD grease chamber 12a of forward clutch 12, the RVS grease chambers 13a of reverse brake 13 and The hydraulic pressure of work is supplied to the DR grease chamber 22c and DN grease chambers 23c of buncher 6.Hereinafter, suitably by LU clutches 4c, forward clutch 12, reverse brake 13 and buncher 6 are referred to as " hydraulic pressure supply object ".

Hydraulic pressure feeding mechanism possesses：Hydraulic pump 31；LU fluid pressure line LUL, its are used for 1LU grease chambers 4d and 2LU oil Room 4e supplies hydraulic pressure；Clutch hydraulic pressure pipeline CLL, its are used for supplying hydraulic pressure to FWD grease chamber 12a and RVS grease chambers 13a；And band Wheel fluid pressure line PUL, its are used for supplying hydraulic pressure to DR grease chamber 22c and DN grease chambers 23c.

Hydraulic pump 31 is the gear pump with engine 3 as driving source, and is coupled with bent axle 3a.Hydraulic pump 31 via oil circuit with PH pressure regulator valves (PH REG VLV) 32 connect, and the working oil being accumulated in oil storage pool R is pumped into PH pressure regulator valves 32.PH pressure regulator valves 32 are made up of mechanical guiding valve, in hydraulic pump 31 operates, the hydraulic pressure from hydraulic pump 31 are supplied in the state of being adjusted Above-mentioned LU fluid pressure lines LUL, clutch hydraulic pressure pipeline CLL and belt wheel fluid pressure line PUL should be arrived.

LU fluid pressure lines LUL is made up of following part etc.：TC pressure regulator valves (TC REG VLV) 33, which is via oil circuit and PH Pressure regulator valve 32 is connected；LU controls valve (LU CTL VLV) 34, which is connected with TC pressure regulator valves 33 via oil circuit；And LU switchings Valve (LU SFT VLV) 35, its control the 1LU grease chambers 4d and 2LU grease chambers of valve 34 and LU clutch 4c via oil circuit and LU 4e is connected.TC pressure regulator valves 33, the LU control valve 34 and LU switching valves 35 are made up of guiding valve.In oil pump 31 operates, from PH The hydraulic pressure of pressure regulator valve 32 controls the 1LU that valve 34 and LU switching valves 35 etc. are fed to LU clutch 4c via TC pressure regulator valves 33, LU Grease chamber 4d or 2LU grease chamber 4e.

Additionally, by the hydraulic pressure from aftermentioned pressure-reducing valve (CR VLV) 42 being carried out using the 1st magnetic valve (LS-LCC) SV1 State after pressure regulation is fed to LU control valves 34.Thus, control valve 34 by driving LU, make to be fed to 1LU grease chambers 4d or Hydraulic pressure (amount of the working oil) change of 2LU grease chamber 4e, and then change the degree of engagement of LU clutch 4c.So, by making the 1st The aperture change of magnetic valve SV1, changes the degree of engagement of LU clutch 4c.The aperture of the 1st magnetic valve SV1 is by ECU described later (Electronic Control Unit：Electronic control unit) 2 controls (with reference to Fig. 3).

Additionally, being connected with the 2nd magnetic valve (SOL-A) SV2 in LU switching valves 35.By the excitation of the 2nd magnetic valve SV2/non- Thus the supply destination for controlling the hydraulic pressure of valve 34 from LU, is switched to 1LU grease chamber 4d driving LU switching valves 35 by excitation Or 2LU grease chamber 4e.Thus, 1LU grease chamber 4d are supplied the hydraulic pressure to as described above, and from 2LU grease chambers 4e by work Oil is discharged, and thus becomes engagement state, in contrast, supplies the hydraulic pressure to 2LU grease chamber 4e, and will from 1LU grease chambers 4d Working oil is discharged, and thus becomes release conditions.The excitation of the 2nd magnetic valve SV2/non-excitation is controlled (with reference to Fig. 3) by ECU2.

The clutch hydraulic pressure pipeline CLL is by branch's oil circuit 41, pressure-reducing valve 42, CL working connections 43, the 3rd magnetic valve (LS- CPC) SV3 and hand-operated valve (MAN VLV) 44 etc. are constituted.The one end of branch's oil circuit 41 is connected with PU working connections 51 described later, separately One end is connected with pressure-reducing valve 42.PU working connections 51 are connected with PH pressure regulator valves 32, in the operating of hydraulic pump 31, from PH pressure regulation The hydraulic pressure of valve 32 is fed to pressure-reducing valve 42 via PU working connections 51 and branch's oil circuit 41.

Pressure-reducing valve 42 is made up of mechanical guiding valve, and which is connected with hand-operated valve 44 via CL working connections 43, in CL working connections 43 Midway, be provided with the 3rd magnetic valve SV3 for being opened and closed which.In the operating of hydraulic pump 31, supplied by PH pressure regulator valves 32 The hydraulic pressure that pressure-reducing valve 42 should be arrived is depressurized valve 42 and reduces pressure, and further with by the state after the 3rd magnetic valve SV3 pressure regulation via CL master Oil circuit 43 is fed to hand-operated valve 44.

Hand-operated valve 44 is made up of guiding valve, and which is connected with FWD grease chamber 12a and RVS grease chamber 13a via oil circuit.Additionally, vehicle Driver operation gear lever (not shown) gear be in activation point, movement position or low gear position when, hand-operated valve 44 Select FWD grease chamber 12a to be used as the supply destination of the hydraulic pressure from the 3rd magnetic valve SV3, when in car backing position, select Supply destinations of the RVS grease chambers 13a as the hydraulic pressure from the 3rd magnetic valve SV3.Thus, using aforesaid forward/backward switching Mechanism 5 is driven the switching of the direction of rotation of power.Now, the aperture by making the 3rd magnetic valve SV3 changes, and adjusts supply To the hydraulic pressure of FWD grease chamber 12a or RVS grease chamber 13a, so as to change the degree of engagement of forward clutch 12 or reverse brake 13. The aperture of the 3rd magnetic valve SV3 is controlled (with reference to Fig. 3) by ECU2.

The belt wheel fluid pressure line PUL is by PU working connections 51, DR pressure regulator valves (DR REG VLV) 52 and DN pressure regulator valve (DN REG VLV) 53 grades composition.The one end of PU working connections 51 is connected with PH pressure regulator valves 32, and the branch 51c on way is branched off into wherein 1PU working connections 51a and two strands of 2PU working connections 51b.Additionally, DR pressure regulator valves 52 and DN pressure regulator valves 53 are constituted by guiding valve, And it is respectively set at the midway of 1PU working connection 51a and 2PU working connection 51b.Aforesaid clutch hydraulic pressure pipeline CLL Tributary circuit 41 from PU working connections 51 than branch 51c by PH pressure regulator valves 32 sides element branches out.In hydraulic pump 31 Operating in, from PH pressure regulator valves 32 hydraulic pressure via PU working connections 51,1PU working connection 5a and 2PU working connections 51b and DR pressure regulator valves 52 and DN pressure regulator valves 53 are respectively supplied to DR grease chamber 22c and DN grease chamber 23c.

Additionally, by the hydraulic pressure from pressure-reducing valve 42 being fed to using the state after the 4th magnetic valve (LS-DR) SV4 pressure regulation DR pressure regulator valves 52.Thus, by driving DR pressure regulator valves 52, hydraulic pressure (amount of the working oil) change for being fed to DR grease chamber 22c is made, And then change the effective diameter of driving pulley 22.So, the aperture by making the 4th magnetic valve SV4 changes, and changes driving pulley 22 effective diameter.The aperture of the 4th magnetic valve SV4 is controlled (with reference to Fig. 3) by ECU2.

By the hydraulic pressure from pressure-reducing valve 42 being fed to DN pressure regulation using the state after the 5th magnetic valve (LS-DN) SV5 pressure regulation Valve 53.Thus, by driving DN pressure regulator valves 53, hydraulic pressure (amount of the working oil) change for being fed to DN grease chamber 23c, Jin Erbian are made The effective diameter of more driven pulley 23.So, the aperture by making the 5th magnetic valve SV5 changes, and changes having for driven pulley 23 Effect diameter.The aperture of the 5th magnetic valve SV5 is controlled (with reference to Fig. 3) by ECU2.

Additionally, in the part than 53 downstream of DN pressure regulator valve of 2PU working connection 51b, being connected with hydraulic pressure via oil circuit Sensor 71.Hydrostatic sensor 71 is the strain gage sensing for carrying out action by the supply of electric power from aftermentioned power supply 2a Device, its detect the hydraulic pressure (hereinafter referred to as " PU hydraulic pressure ") of the part than 53 downstream of DN pressure regulator valve of 2PU working connection 51b, And ECU2 is arrived in its detection signal output.Hereinafter, the PU hydraulic pressure detected by hydrostatic sensor 71 is referred to as " detection PU hydraulic pressure POD”.

Additionally, being provided with standby valve (B/U VLV) BV in hydraulic pressure feeding mechanism, standby valve BV is used in the 3rd magnetic valve The supply of the hydraulic pressure to forward clutch 12 and reverse brake 13 is guaranteed during SV3 failures.Standby valve BV is arranged on aforesaid Parts of the 3rd magnetic valve SV3 of ratio of CL working connections 43 by 44 side of hand-operated valve, which is via the oil circuit being set up in parallel with CL working connections 43 OL is connected with pressure-reducing valve 42.Oil circuit OL is connected to 42 downstream of ratio pressure-reducing valve and the 3rd magnetic valve SV3 of ratio in CL working connections 43 Part by upstream side.Additionally, backup valve BV is connected with LU switching valves 35 and DR pressure regulator valves 52 via oil circuit.

When the 3rd magnetic valve SV3 breaks down, the hydraulic pressure from pressure-reducing valve 42 is by aforesaid 4th magnetic valve SV4 Standby valve BV is supplied in the state of being adjusted to higher pressure.Thus, by driving standby valve BV, in the following manner will be from Pressure-reducing valve 42 is fed to various key elements via the hydraulic pressure that above-mentioned oil circuit OL is fed to standby valve BV.That is, it is fed to standby valve BV's A part for hydraulic pressure is fed to FWD grease chambers via part and the hand-operated valve 44 of the ratio standby valve BV downstreams of CL working connections 43 12a or RVS grease chamber 13a, thus engage forward clutch 12 or reverse brake 13.Additionally, being supplied to standby valve BV's A part in the remainder of hydraulic pressure is supplied to LU switching valves 35, also, the remainder is supplied via DR pressure regulator valves 52 DR grease chamber 22c should be arrived.Thus, LU clutches 4c is controlled in release conditions, and the effective diameter of fixed drive belt wheel 22.

Additionally, from explanation so far, the 4th magnetic valve SV4 is also used as the drive of DR pressure regulator valves 52 and standby valve BV Magnetic valve is employed, therefore, when the 3rd magnetic valve SV3 is normal, the hydraulic pressure from the 4th magnetic valve SV4 is supplied to DR pressure regulator valves 52 With this both sides of standby valve BV.Standby valve BV is provided with return spring (not shown), using the active force of the return spring, after making The relatively low hydraulic-driven not supplied when normal by the 3rd magnetic valve SV3 by standby valve BV, and only by the 3rd magnetic valve SV3 failures when institute The higher hydraulic-driven of supply.Thus, when the 3rd magnetic valve SV3 is normal, action during above-mentioned failure will not be carried out.

Additionally, being provided with pressure accumulater 61 in hydraulic pressure feeding mechanism.As shown in figure 4, pressure accumulater 61 has looped pipeline road 62nd, main accumulator 63, stop valve 64 and auxiliary accumulator 65.The one end on looped pipeline road 62 is connected in above-mentioned CL working connections 43 42 downstream of ratio pressure-reducing valve and than with the coupling part of oil circuit OL by upstream side part, the other end and main accumulator 63 Connection.

Main accumulator 63 has cylinder body 63a, the piston 63b that is slidably disposed in cylinder body 63a and by pressing The spring 63c that shrunk-on ring spring is constituted.Delimit out pressure accumulating chamber 63d between cylinder body 63a and piston 63b, piston 63b by spring 63c to Pressure accumulating chamber 63d sides exert a force.Above-mentioned looped pipeline road 62 is connected with pressure accumulating chamber 63d.As described above, pressure accumulating chamber 63d and above-mentioned advance clutch 12 grade hydraulic pressure of device supply object and hydraulic pump 31 are connected.The active force (spring constant) of spring 63c is set to：Savings is made to exist The hydraulic pressure of pressure accumulating chamber 63d is such as 0.3～0.5MPa.

Stop valve 64 is by can optionally be controlled to the valve opening pattern that is forced open and play work as check-valves The magnetic valve of non-return valve mode is constituted, and which is arranged on the midway on looped pipeline road 62.Specifically, stop valve 64 is by with bottom Divide and constitute：Valve body 64a, its can be moved between the valve opening position shown in Fig. 4 and the valve closing position shown in aftermentioned Fig. 6；Reset Spring 64b, its are exerted a force in the way of making valve body 64a be maintained at valve closing position；And for driving the magnetic valve of valve body 64a 64c etc..Magnetic valve 64c has plunger 64d, and is connected (with reference to Fig. 3) with ECU2.Stop valve 64 is being controlled with valve opening pattern In the case of, from ECU2 to magnetic valve 64c input drive signal ASO.Under the valve opening pattern, plunger 64d resists back-moving spring 64b Active force and push valve body 64a, thus, valve body 64a is maintained at valve opening position.That is, under valve opening pattern, 64 quilt of stop valve Force to keep valve opening state.

On the other hand, in the case where stop valve 64 is controlled with non-return valve mode, stop defeated to magnetic valve 64c from ECU2 Enter drive signal ASO.Under non-return valve mode, make plunger 64d keep the state that leaves from valve body 64a, thus, make stop valve 64 Play a role as check-valves.Additionally, under non-return valve mode, the ratio stop valve 64 in looped pipeline road 62 leans on main accumulator 63 When the hydraulic pressure of the part of side is less than the hydraulic pressure of part for leaning on 43 side of CL working connections than stop valve 64, due to the effect of the hydraulic pressure, valve Body 64a resists the active force of back-moving spring 64b and is automatically moved to valve opening position, thus, it is allowed to which working oil is from CL working connections 43 The part of side flows into the part of main 63 side of accumulator.

Additionally, under non-return valve mode, contrary to the above, the ratio stop valve 64 in looped pipeline road 62 leans on 63 side of main accumulator Part hydraulic pressure higher than than stop valve 64 by 43 side of CL working connections part hydraulic pressure when, due to the effect and reset of the hydraulic pressure The force of spring 64b, valve body 64a are automatically moved to valve closing position, thus, prevent working oil from flowing from the part of 63 side of main accumulator Enter the part of 43 side of CL working connections.

Auxiliary accumulator 65 is the accumulator more small-sized than main accumulator 63, with cylinder body 65a, slidably arranges Piston 65b in the cylinder body 65a and spring 65c being made up of compression coil spring.Storage is divided into by piston 65b in cylinder body 65a Pressure chamber 65d and back side room 65e.Additionally, in the part of the back side room 65e sides of piston 65b, recess 65f is formed with, recess 65f The space of inner side constitute a part of above-mentioned back side room 65e.Spring 65c is arranged in the 65e of back side room, and one part is received It is contained in recess 65f.Piston 65b is exerted a force to pressure accumulating chamber 65d sides via aftermentioned valve body 65h by spring 65c.Work for spring 65c Firmly the setting of (spring constant) is as described later.Additionally, stroke of the maximum of the amount of contraction of spring 65c more than piston 65b.

Additionally, in the part of the pressure accumulating chamber 65d sides of piston 65b, it is circular intercommunicating pore 65g to be formed with section so that store Pressure chamber 65d is communicated with each other with back side room 65e.Additionally, between piston 65b and spring 65c, it is provided with for making intercommunicating pore 65g The valve body 65h being opened and closed.Valve body 65h is formed as spherical, with the diameter bigger than intercommunicating pore 65g, and is incorporated in recess 65f.Valve body 65h, intercommunicating pore 65g and spring 65c are arranged to same heart shaped.

Additionally, valve body 65h can be moved between the release position shown in the detent position shown in Fig. 4 and aftermentioned Fig. 7, quilt Spring 65c is exerted a force in the way of keeping detent position.When valve body 65h is located at detent position, valve body 65h and intercommunicating pore 65g's The edge of back side room 65e sides abuts, and thus closes intercommunicating pore 65g, on the other hand, when valve body 65h is located at release position, valve Body 65h is left from the edge of the back side room 65e sides of intercommunicating pore 65g, thus opens intercommunicating pore 65g.The back side in intercommunicating pore 65g The edge of room 65e sides, is concentrically provided with the valve seating (not shown) of the ring-type being made up of elastomer.

Additionally, auxiliary accumulator 65 is in the way of bypassing stop valve 64 via the 1st oil circuit 66 and the 2nd oil circuit 67 and secondary Pipeline 62 connects.Thus, the back side room 65e of auxiliary accumulator 65 is connected with looped pipeline road 62 via the 1st oil circuit 66, pressure accumulating chamber 65d Connect with looped pipeline road 62 via the 2nd oil circuit 67.As described above, pressure accumulating chamber 65d is via stop valve 64, (front with hydraulic pressure supply object Enter clutch 12 etc.) and hydraulic pump 31 connect, back side room 65e supplies object and hydraulic pressure not via stop valve 64 with hydraulic pressure Pump 31 is connected.Therefore, hydraulic pump 31 operating in, the hydraulic pressure from CL working connections 43 via looped pipeline road 62 and the 1st oil circuit 66, The end face of the back side room 65e sides of piston 65b is acted on as back pressure.Additionally, pressure accumulating chamber 65d is not via stop valve 64, but Connect with the pressure accumulating chamber 63d of main accumulator 63 via the 2nd oil circuit 67 and looped pipeline road 62.

Furthermore, it is possible to make pressure accumulating chamber 65d via the 2nd oil circuit 67 and the pressure accumulating chamber 63d of looped pipeline road 62 and the 1st accumulator 63 Connection, but it is also possible to only connect with pressure accumulating chamber 63d via the 2nd oil circuit 67.Furthermore, it is possible to make back side room 65e via the 1st oil circuit 66 And looped pipeline road 62 is connected with CL working connections 43, but it is also possible to only connect with CL working connections 43 via the 1st oil circuit 66.

Additionally, as shown in figure 3, exporting the rotating speed of expression engine 3 from engine speed sensor 72 to ECU2 (below, Referred to as " the engine speed ") detection signal of NE.Additionally, output represents the throttle of vehicle from accelerator open degree sensor 73 to ECU2 The detection signal of operational ton (hereinafter referred to as " the accelerator open degree ") AP of pedal (not shown), defeated to ECU2 from vehicle speed sensor 74 Go out to represent the detection signal of vehicle velocity V P of vehicle.

Additionally, the ignition switch (hereinafter referred to as " IG/SW ") 75 and brake switch of ECU2 and vehicle are (hereinafter referred to as " BR/SW ") 76 connections.IG/SW75 is turned on/off because of the operation of the firing key of driver (not shown), and this is connect ECU2 is arrived in the output of on/off ON signal.In this case, in the stopping of engine 3, when IG/SW75 is connected, starter (is not schemed Show) carry out action etc. therefrom, so as to start engine 3.Additionally, in engine 3 operates, when IG/SW75 is closed, starting Machine 3 stops (stopping manually) therefrom.Additionally, BR/SW76 is when the brake pedal (not shown) of vehicle is operated, defeated to ECU2 Go out to connect signal, when not being operated, cut-off signal is exported to ECU2.

ECU2 is made up of microcomputer, and the microcomputer is made up of I/O interfaces, CPU, RAM and ROM etc..CPU according to Detection signal from above-mentioned various sensors 71～74 and the on/off signal from IG/SW75 and BR/SW76, According to the control program stored in ROM, to the dynamic of engine 3, the 1st magnetic valve SV1～the 5th magnetic valve SV5 and stop valve 64 It is controlled.Additionally, in ECU2, being provided with the power supply 2a of its supply of electric power, its on/off is controlled by CPU.As above Described, power supply 2a is shared as the power supply of ECU2 and above-mentioned hydrostatic sensor 71.

Next, with reference to Fig. 5, illustrating to the process executed by CPU.Fig. 5 is shown for controlling above-mentioned stop valve The process of the action of the various valves such as 64, present treatment are performed repeatedly by the controlling cycle (for example, 100msec) of regulation.First, exist In the step of Fig. 51 (being illustrated as " S1 ", same as below), discriminate whether to output connection signal from IG/SW75.In its answer it is "Yes" and from IG/SW75 output connect signal when, differentiate idle stop flag F_IDLESTP whether be " 1 " (step 2).

Idle stop flag F_IDLESTP represents engine 3 in being automatically stopped, for example with " 1 ", comprising such as Condition A～the D of lower regulation executes being automatically stopped for engine 3 when multiple stop conditions of interior regulation are set up.Engine 3 be automatically stopped is executed by stopping fuel supply to engine 3 etc..

A：Signal is connected from IG/SW75 outputs；

B：Vehicle velocity V P for detecting is below setting VPREF；

C：The accelerator open degree AP for detecting is below setting APREF；

D：Signal is connected from BR/SW76 outputs.

Additionally, in being automatically stopped of engine 3, such as in many of the regulation comprising condition E and F being specified below When individual at least one that resets in condition is set up, reset engine 3 automatically.Resetting for engine 3 is to pass through Control fuel supply to starter and engine 3 etc. to execute.

E：Accelerator open degree AP has exceeded setting APREF because stepping on the throttle pedal；

F：Trampling for brake pedal is released, and cut-off signal is exported from BR/SW76.

When the answer of the step 2 is "No" (F_IDLESTP=0), i.e., in being automatically stopped of engine 3 is not at When, differentiate whether previous value F_IDLESTPZ of idle stop flag is " 1 " (step 3).The answer is "No" (F_IDLESTPZ =0) when, i.e. engine 3 in operation when, in order to according to operating when control the various valves such as stop valve 64 with control model, In step 4, will be set as " 1 " with control mark F_OPECO during operating, also, with control mark F_ when will reset RESCO, indicate that F_MSTCO is set as " 0 " with control mark F_ASTCO and when stopping manually with control when being automatically stopped, Terminate present treatment.

Operating condition, car in the operating under control model, according to the engines such as engine speed NE for detecting 3 Fast VP and accelerator open degree AP, control the 1st magnetic valve SV1～the 5th magnetic valve SV5 aperture, thus to LU clutch 4c, advance from Clutch 12, buncher 6 etc. are controlled.Additionally, controlling the 5th magnetic valve always according to the detection PU hydraulic pressure POD for detecting The aperture of SV5, thus, is carried out to the effective diameter and side pressure (driven pulley 23 clamps the pressure of transfer tape 24) of driven pulley 23 Control.Additionally, stopping being input into above-mentioned drive signal ASO to stop valve 64, thus, controlled with non-return valve mode as described above Stop valve 64, so which plays a role as check-valves.

On the other hand, the answer in the step 2 is in being automatically stopped for engine 3 for "Yes" (F_IDLESTP=1) When middle, in order to according to various valves are controlled when being automatically stopped with control model, in steps of 5, with control mark when will be automatically stopped Will F_ASTCO is set as " 1 ", also, will use control mark F_RESCO when being indicated F_OPECO, reset with control during operating And be set as " 0 " with control mark F_MSTCO when stopping manually, terminate present treatment.When this is automatically stopped with control mould Under formula, the 1st magnetic valve SV1～the 5th magnetic valve SV5 is controlled to state when engine 3 will be automatically stopped.Additionally, with Being automatically stopped and stopping hydraulic pump 31 for engine 3, thus, stops to each grease chambers such as above-mentioned FWD grease chambers 12a and DR grease chamber 22c Hydraulic pressure supply.Additionally, identically with the situation of control model during above-mentioned operating, believed by stopping the driving to stop valve 64 The input of number ASO, thus, controls stop valve 64 with non-return valve mode.

Additionally, key element, the i.e. 1LU in being automatically stopped of engine 3, beyond the pressure accumulater 61 of hydraulic pressure feeding mechanism Grease chamber 4d and 2LU grease chamber 4e, FWD grease chamber 12a, RVS grease chamber 13a, DR grease chamber 22c, DN grease chamber 23c, LU fluid pressure line LUL, Working oil in clutch hydraulic pressure pipeline CLL and belt wheel fluid pressure line PUL is discharged (row via discharge pipe (not shown) Put) in oil storage pool R.

On the other hand, when the answer of the step 3 is "Yes" (F_IDLESTPZ=1), i.e., from the automatic of engine 3 When halted state is reset, in order to according to various valves are controlled when resetting with control model, in step 6, will again It is set as " 1 " with control mark F_RESCO during starting, and will be controlled when being indicated F_OPECO, be automatically stopped with control during operating It is set as " 0 " with control mark F_MSTCO when mark F_ASTCO and manually stopping, terminating present treatment.Reset at this When control model under, identical with the situation of control model during operating, according to operating condition of engine 3 etc., control the 1st The aperture of magnetic valve SV1～the 5th magnetic valve SV5.Additionally, pass through to 64 input drive signal ASO of stop valve, with above-mentioned valve opening mould Thus formula, forcibly keeps valve opening state controlling stop valve 64.Additionally, when resetting in control model, from which Started, according to engine speed NE, persistently carry out the judgement, till the hydraulic pressure until determining hydraulic pump 31 fully rises.

On the other hand, the step 1 answer for "No" from IG/SW75 export cut-off signal when, in send out When in the manual stopping of motivation 3, differentiate whether engine speed NE is 0 value (step 7).In the answer, for "No", engine turns When fast NE is more than 0 value, directly terminate present treatment.

On the other hand, when for "Yes", engine speed NE is 0 value for the answer of above-mentioned steps 7, it is judged to：In engine In 3 manual stopping, the hydraulic pump 31 with engine 3 as power source stops.Additionally, controlling mould to use during according to stopping manually With control, formula in step 8, will indicate that F_MSTCO be set as " 1 " when will stop manually controlling various valves, also, when will operate With control mark F_OPECO, control mark F_ASTCO when resetting, is used with control mark F_RESCO and when being automatically stopped It is set as " 0 ", terminates present treatment.

In the manual stopping under control model, the 1st magnetic valve SV1 and the 4th magnetic valve SV4 is controlled respectively so that the 3rd Magnetic valve SV3 is controlled as full-shut position, and LU control valves 34 and DR pressure regulator valves 52 are full-shut position, also, controls the 5th electricity Magnet valve SV5 so that DN pressure regulator valves 53 are full-gear.Additionally, identical with control model with when resetting, by cut-off 64 input drive signal ASO of valve, thus, with valve opening Schema control stop valve 64 so as to keep valve opening state.

In addition, in the manual stopping of engine 3, identically with the situation in being automatically stopped of engine 3, supply hydraulic pressure The working oil in the key element beyond the pressure accumulater 61 of device is answered to discharge (discharge) in oil storage pool R.Additionally, using when stopping manually Control model lasted till till have passed through the stipulated time from which starts, therebetween, remains turned on power supply 2a, with setting about Terminated with control model during dynamic stopping, power supply 2a is controlled to off-state.

Additionally, as described above, from IG/SW75 is closed, waiting engine speed NE to be changed into the (answer of waiting step 7 of 0 value It is changed into "Yes"), control model when starting to stop manually, but step 7 can also be omitted, at the IG/SW75 pent moment Control model when starting to stop manually.In this case, when stopping manually with control model from which starts, last till and start Till machine rotating speed NE is changed into 0 value, that is, till lasting till that hydraulic pump 31 stops completely.

Next, with reference to Fig. 4, Fig. 6～Fig. 8, (Fig. 4) in operating to engine 3, be automatically stopped in (Fig. 6, Fig. 7) and When resetting from automatic stop condition, the action of the pressure accumulater 61 of (Fig. 8) is illustrated successively.

[during engine 3 operates]

As with reference to illustrated by Fig. 5, (the step of Fig. 51 in engine 3 operates：It is, step 2：No), i.e. hydraulic pressure During pump 31 operates, execute when operating with control model (step 4).In the running with the execution of control model, with check-valves mould Formula controls stop valve 64, and thus, stop valve 64 becomes owner of 63 side of accumulator as only permission working oil from 43 effluent of CL working connections Check-valves and play a role.In this case, the hydraulic pressure due to supplying from hydraulic pump 31 to CL working connections 43 is higher than main accumulator 63 hydraulic pressure, therefore, thus the automatic valve opening because of the effect of the hydraulic pressure of stop valve 64, makes main accumulator 63 and CL working connections 43 Between connect.

Thus, as shown in figure 4, the hydraulic pressure from CL working connections 43 is supplied to main accumulator 63 via looped pipeline road 62 Pressure accumulating chamber 63d, so as to pushing piston 63b, thus, piston 63b resists the active force of spring 63c, and court is contrary with pressure accumulating chamber 63d One side shifting (in the diagram, is illustrated with hollow arrow).As a result, accumulating hydraulic pressure in main accumulator 63.

Additionally, from CL working connections 43 hydraulic pressure via looped pipeline road 62 and the 1st oil circuit 66, act on as back pressure auxiliary Help the end face of the back side room 65e sides of accumulator 65.The active force of spring 65c is set to：In hydraulic pump 31 operates, spring The active force of 65c is more than within the loop comprising looped pipeline road 62, main accumulator 63 and the 2nd oil circuit 67 with above-mentioned back pressure sum Hydraulic pressure.Thus, as shown in figure 4, in the operating of hydraulic pump 31, making the end face of the pressure accumulating chamber 65d sides of piston 65b keep and cylinder body The state that the inwall of 65a is abutted, also, make valve body 64a keep its valve opening position, therefore, it is possible to make the liquid from hydraulic pump 31 Pressure is hardly accumulated in auxiliary accumulator 65, and suitably accumulates in main accumulator 63.

[during engine 3 is automatically stopped]

(the step of Fig. 51 in engine 3 is automatically stopped：It is, step 2：It is), execute control model when being automatically stopped (step 5).When being automatically stopped in the execution of control model, when operating in the same manner as the situation of control model, with non-return Valve mode controls stop valve 64 so as to play a role as check-valves.In this case, as engine 3 is automatically stopped, stop Only the hydraulic pressure of CL working connections 43 is supplied from hydraulic pump 31, and the working oil in CL working connections 43 is made as described above from oil storage Pond R is discharged, and therefore, the ratio stop valve 64 in looped pipeline road 62 is higher than to lean on than stop valve 64 by the hydraulic pressure of the part of 63 side of main accumulator The hydraulic pressure of the part of 43 side of CL working connections, therefore, 64 automatic valve closing of stop valve.Thus, as shown in fig. 6, due to CL working connections 43 It is cut off between main accumulator 63, therefore, keeps the hydraulic pressure being accumulated in main accumulator 63 so far.Further, since cutting Only the valve closing of valve 64, defines the loop comprising looped pipeline road 62, main accumulator 63 and the 2nd oil circuit 67.

Additionally, when stopped hydraulic pump 31, no longer effect has the back pressure from CL working connections 43, and back side room therewith 65e is connected with hydraulic pump 31 not via stop valve 64, and therefore, the only active force of spring 65c is used as pushing away towards pressure accumulating chamber 65d sides Pressure aids in the pushing force of the piston 65b of accumulator 65 and is acted on.Additionally, pressure accumulating chamber 65d is not via stop valve 64, but warp Connected with the pressure accumulating chamber 63d of main accumulator 63 by the 2nd oil circuit 67 and looped pipeline road 62.Thus, with the stopping of hydraulic pump 31, auxiliary Help accumulator 65 piston 65b be accumulated in be cut off valve 64 closing loop in hydraulic pressure pushed, so as to towards the back side Room 65e side shiftings (in figure 6, being illustrated with hollow arrow).The part quilt of hydraulic pressure (working oil) thus, in loop The pressure accumulating chamber 65d of auxiliary accumulator 65 is fed to, and is accumulated wherein.Therefore, it is possible to make the hydraulic pressure in loop reduce Its redundance.

Additionally, in figure 6, for the hydraulic pressure in the loop of 63 grade of main accumulator less than the higher limit for specifying (for example, Situation 2.54MPa) and show engine 3 be automatically stopped in pressure accumulater 61 etc..In this case, as shown in fig. 6, auxiliary The valve body 65h of accumulator 65 is helped to be maintained at detent position due to the force of spring 65c, thus, the intercommunicating pore of piston 65b 65g is closed by valve body 65h.

On the other hand, in the figure 7, the situation of above-mentioned higher limit is reached for the hydraulic pressure in loop and show and start Machine 3 be automatically stopped in pressure accumulater 61 etc..As shown in the drawing, the end face of the back side room 65e sides of piston 65b is with cylinder body 65a's Inwall is abutted, it is impossible to which further the hydraulic pressure towards back side room 65e side shiftings and in loop is pushing valve body towards back side room 65e sides The mode of 65h is acted on, and therefore, valve body 65h resists the active force of spring 65c, move from detent position to release position ( In Fig. 7, illustrated with hollow arrow).Thus, open intercommunicating pore 65g, so that pressure accumulating chamber 65d and back side room 65e is via even Through hole 65g communicates with each other, thus, the excess electron excess fraction of the hydraulic pressure in loop via back side room 65e be discharged into the 1st oil circuit 66 with And in looped pipeline road 62, CL working connections 43 etc..Therefore, it is possible to prevent excessiveization of the hydraulic pressure in loop, and then, can avoid The breakage of main accumulator 63, auxiliary accumulator 65, looped pipeline road 62, the 2nd oil circuit 67 and stop valve 64.The active force of spring 65c It is set to obtain above-mentioned effect/effect.

[engine 3 reset from automatic stop condition to when]

(the step of Fig. 51 when engine 3 is reset from automatic stop condition：It is, step 2：No, step 3：It is), hold With control model (step 6) when row is reset.When resetting in the execution of control model, cut with valve opening Schema control Only valve 64 so as to keep valve opening state, thus, make to connect between main accumulator 63 and CL working connections 43.Thus, as shown in figure 8, The piston 63b of main accumulator 63 is because of the active force of spring 63c to pressure accumulating chamber's 63d side shiftings (in the figure, with hollow arrow figure Illustrate).Thus, the hydraulic pressure in the loop of 63 grade of above-mentioned main accumulator is accumulated in via looped pipeline road 62 and CL working connections 43, FWD grease chamber 12a are supplied to, and further via branch's oil circuit 41 and PU working connections 51, are supplied to DR grease chamber 22c And DN grease chamber 23c.Also, when the hydraulic pressure of hydraulic pump 31 is fully raised, in addition to from the hydraulic pressure of loop, from The hydraulic pressure of hydraulic pump 31 is also supplied to DR grease chamber 22c, DN grease chamber 23c and FWD grease chamber 12a.Therefore, according to present embodiment, When engine 3 is reset from automatic stop condition, rapidly and sufficiently can supply to buncher 6 and forward clutch 12 Answer hydraulic pressure.

Additionally, Fig. 8 show associated with resetting for engine 3, after operating that is starting again at hydraulic pump 31 State, in this condition, the hydraulic pressure of hydraulic pump 31 does not also fully rise, and the hydraulic pressure in loop is higher, therefore, such as the figure Shown, lean in the part of 31 side of hydraulic pump in the connecting portion than looped pipeline road 62 of CL working connections 43, working oil flows to hydraulic pump 31 Side.

Additionally, with the opening of above-mentioned stop valve 64, the pushing force that is made up of the active force of back pressure and spring 65c this both sides It is used as pushing force from the piston 65b of auxiliary accumulator 65 to pressure accumulating chamber 65d sides that push again to be acted on.Thus, make , to pressure accumulating chamber's 65d side shiftings (in fig. 8, being illustrated with hollow arrow), thus, savings so far is in auxiliary storage for piston 65b The hydraulic pressure (working oil) of depressor 65 is via the 2nd oil circuit 67, looped pipeline road 62 and PU working connections 51 and the hydraulic pressure for carrying out autonomous accumulator 63 DR grease chamber 22c, DN grease chamber 23c and FWD grease chamber 12a is supplied to together.Therefore, according to present embodiment, oil is being started again at During the operating of pump 31, hydraulic pressure (working oil) that can be economically by the savings when which stops in auxiliary accumulator 65 is fed to Buncher 6 and forward clutch 12.

Additionally, Fig. 9 shows that engine 3 is executed from operating and being automatically stopped, executing in this is automatically stopped and reset In the case of hydraulic pressure feeding mechanism action example.In fig .9, represented with " 1 " respectively to 64 input drive signal of stop valve ASO, is represented with " 0 " not to 64 input drive signal ASO of stop valve.Additionally, in the figure, based on PAC in accumulator 63 The hydraulic pressure (hereinafter referred to as " main accumulator hydraulic pressure ") of accumulation, PFWD are hydraulic pressure (hereinafter referred to as " the FWD liquid in FWD grease chamber 12a Pressure ").

As shown in figure 9, engine 3 operate in and vehicle velocity V P more than the setting VPREF, above-mentioned stop condition not into Immediately (before moment t0～t1,1 the step of Fig. 5：It is, step 2,3：No), will be set with control mark F_OPECO during operating respectively It is set to " 1 ", will be set as with control mark F_ASTCO with control mark F_RESCO and when being automatically stopped when will reset " 0 ", (step 4), control model when executing operating.

In the running with the execution of control model, not to 64 input drive signal ASO of stop valve, therefore, with check-valves Pattern is controlling stop valve 64.Thus, it is allowed to which working oil flows into main accumulator 63 from CL working connections 43, working oil is prevented from main storage Depressor 63 flows out to CL working connections 43, and therefore, main accumulator hydraulic pressure PAC is changed with approximately fixed state.Additionally, at this In action example, due to being in the Reduced Speed Now of vehicle, thus the degree of engagement required by forward clutch 12 is less, therefore, FWD hydraulic pressure PFWD is less than main accumulator hydraulic pressure PAC.

Further, become (moment t1) when 0 value, stop condition are set up in vehicle velocity V P, engine 3 is automatically stopped, engine turns Fast NE drastically drops to 0 value therewith.Additionally, hydraulic pressure of the hydraulic pump 31 with engine 3 as driving source and from hydraulic pump 31 is supplied FWD grease chamber 12a should be arrived, therefore, FWD hydraulic pressure PFWD drastically drop to 0 value with the decline of engine speed NE.

Additionally, establishment (the step of Fig. 51,2 with stop condition：It is), with control mark F_ when will be automatically stopped respectively ASTCO is set as " 1 ", will be set as with control mark F_RESCO when being indicated F_OPECO and reset with control during operating " 0 " (step 5), executes control model when being automatically stopped.When being automatically stopped in the execution of control model, with operating when use The situation of control model in the same manner, not to 64 input drive signal ASO of stop valve, controls stop valve 64 with non-return valve mode. Additionally, as described in using Fig. 6, due to 64 automatic valve closing of stop valve, therefore, defining the closing comprising main accumulator 63 and returning A part for hydraulic pressure in road, and loop is supplied to auxiliary accumulator 65, and accumulates wherein.Thus, main accumulator Hydraulic pressure PAC is changed with fixed state after reducing its redundance.

Further, because of pedal of stepping on the throttle etc. so that above-mentioned reset condition set up when (moment t2), 3 weight of engine New starting, engine speed NE rises therewith, and vehicle velocity V P is gradually increasing.Additionally, why engine speed NE is not in weight New starting conditions rise after setting up at once, are due to the operating lag of starter.

Additionally, establishment (the step of Fig. 51 with condition of resetting：It is, step 2：No, step 3：It is), respectively will weight It is set as " 1 " with control mark F_RESCO during new starting, F_OPECO will be indicated with control during operating and used when being automatically stopped Control mark F_ASTCO is set as " 0 " that (step 6) executes control model when resetting.Control when resetting In the execution of pattern, to 64 input drive signal ASO of stop valve, thus, with valve opening Schema control stop valve 64, force to protect which Hold valve opening state.Thus, as described in using Fig. 8, the hydraulic pressure being accumulated in 63 grade loop of main accumulator is supplied to FWD grease chamber 12a etc., therefore, main accumulator hydraulic pressure PAC drastically declines, and FWD hydraulic pressure PFWD steeply rise.

In fig .9, PUP represents the FWD hydraulic pressure PFWD because the hydraulic pressure of FWD grease chamber 12a being supplied and being risen from loop Rising part.In this case, rising part PUP is less than accumulator liquid when resetting during the beginning of control model Pressure PAC, therefore, hydraulic pressure in loop and not all be supplied to FWD grease chamber 12a, but be also supplied to DR grease chamber 22c Deng.

Additionally, when resetting in the execution of control model, engine speed NE because of the starting of engine 3 on Rise, the decline degree of main accumulator hydraulic pressure PAC diminishes therewith, and FWD hydraulic pressure PFWD are gradually increasing.Further, carry out in engine 3 During incipient detonation, main accumulator 63 and FWD grease chamber 12a, therefore, main accumulator hydraulic pressure PAC is supplied to from the hydraulic pressure of hydraulic pump 31 And FWD hydraulic pressure PFWD this both sides rise.In this case, due to being in during vehicle start, thus will to forward clutch 12 The degree of engagement that asks is larger, and therefore, FWD hydraulic pressure PFWD is risen with the size roughly the same with main accumulator hydraulic pressure PAC.

Further, as described above, when having started to reset after control model, being judged according to engine speed NE When fully rising for the hydraulic pressure of hydraulic pump 31 (moment t3), terminate control model when resetting.Therewith, respectively will operating When be set as " 1 " with control mark F_OPECO, the control with control mark F_ASTCO and when resetting when will be automatically stopped System indicates that F_RESCO is set as " 0 ", control model when executing operating.Thus, due to no longer driving letter to the input of stop valve 64 Number ASO, thus stop valve 64 is controlled with non-return valve mode.

Additionally, the corresponding relation between the various key elements of the various key elements and the present invention of present embodiment is as follows.That is, this reality During LU clutch 4c in mode, forward clutch 12, reverse brake 13 and buncher 6 are applied equivalent to the present invention Hydraulic pressure supply object, in present embodiment auxiliary accumulator 65 and pressure accumulating chamber 65d equivalent to the present invention in the 1st accumulator With the 1st pressure accumulating chamber, also, the spring 65c in present embodiment equivalent to the present invention in the 1st forcing unit, the 2nd forcing unit And force application part.Additionally, the engine 3 in present embodiment equivalent to the present invention in vehicle power source, and this enforcement Main accumulator 63 and pressure accumulating chamber 63d in mode equivalent to the present invention in the 2nd accumulator and the 2nd pressure accumulating chamber.

As described above, according to present embodiment, the pressure accumulating chamber 63d of main accumulator 63 and the liquid with engine 3 as driving source The supply object connection of the hydraulic pressure such as press pump 31 and FWD grease chamber 12a, can accumulate the hydraulic pressure from hydraulic pump 31.Additionally, by cutting Only valve 64, make to connect/end between hydraulic pressure supply object and hydraulic pump 31 and pressure accumulating chamber 63d.As with reference to that described in Fig. 4 Sample, by the connection of the stop valve 64, can be accumulated in the hydraulic pressure from hydraulic pump 31 in pressure accumulating chamber 63d.Additionally, such as reference As Fig. 6 explanations, by the cut-off of stop valve 64, pressure accumulating chamber 63d can be closed, so as to keep accumulation in pressure accumulating chamber 63d Hydraulic pressure.Additionally, as illustrated with reference to Fig. 8, by the connection of stop valve 64, the hydraulic pressure that can be accumulated in pressure accumulating chamber 63d It is fed to hydraulic pressure supply object.

Additionally, the pressure accumulating chamber 65d of auxiliary accumulator 65 supplies object and hydraulic pump 31 via stop valve 64 with hydraulic pressure Connection, therefore, by the cut-off of above-mentioned stop valve 64, in addition to the pressure accumulating chamber 63d that can close main accumulator 63, additionally it is possible to Closing pressure accumulating chamber 65d, thereby, it is possible to keep the hydraulic pressure that accumulates in Liang Ge pressure accumulating chamber 63d, 65d.Additionally, pressure accumulating chamber 65d not via Stop valve 64 and connect with pressure accumulating chamber 63d, therefore, as with reference to Fig. 7 explanation as, can pass through by intercommunicating pore 65g, valve body The overflow mechanism that 65h and spring 65c are constituted, prevent from being cut off valve 64 cut-off closing, comprising Liang Ge pressure accumulating chamber 63d, 65d Loop in hydraulic pressure (working oil) excessiveization, thereby, it is possible to avoid the 1st accumulator 63 and the 2nd accumulator 65 etc. break Damage.

Additionally, intercommunicating pore 65g, valve body 65h and spring 65c are not dividually configured with auxiliary accumulator 65, and It is provided in the cylinder body 65a of auxiliary accumulator 65, therefore, it is possible to minimize hydraulic pressure feeding mechanism.

Additionally, stop valve 64 is configured to optionally be controlled to non-return valve mode and valve opening pattern, in check-valves mould Under formula, when the hydraulic pressure in pressure accumulating chamber 63d sides supplies the hydraulic pressure of 31 side of object and hydraulic pump less than hydraulic pressure, hydraulic pressure is made to supply object And connect between hydraulic pump 31 and pressure accumulating chamber 63d, the hydraulic pressure in pressure accumulating chamber 63d sides supplies object and hydraulic pump higher than hydraulic pressure During the hydraulic pressure of 31 sides, make to end between hydraulic pressure supply object and hydraulic pump 31 and pressure accumulating chamber 63d.Thereby, it is possible to effectively obtain To the effect above, i.e., the hydraulic pressure from hydraulic pump 31 can be accumulated in pressure accumulating chamber 63d and can keep accumulated hydraulic pressure this The effect of sample.Additionally, under non-return valve mode, it is not necessary to which the special control for switching over to the opening and closing of stop valve 64 is moved Make, therefore, it is possible to simply carry out the accumulation/holding of hydraulic pressure to pressure accumulating chamber 63d.

Additionally, the 1st forcing unit and the 2nd forcing unit in the present invention is by public single spring 65c each other Constitute, therefore, number of components can be accordingly cut down because of the part.Additionally, valve body 65h by spring 65c towards detent position Side exerts a force, also, piston 65b is exerted a force towards pressure accumulating chamber 65d sides via valve body 65h, therefore, it is possible to suitably carry out valve body 65h The accumulation of the hydraulic pressure towards the holding of detent position and based on auxiliary accumulator 65.

Additionally, abutting by making valve body 65h and the edge of intercommunicating pore 65g, close intercommunicating pore 65g.Additionally, valve body 65h is formed as spherical, therefore, it is possible to suppress the unilateral of the edge towards intercommunicating pore 65g to abut, valve body 65h can be utilized appropriate Ground closed communication hole 65g.

Additionally, back side room 65e is connected with hydraulic pump 31 and hydraulic pressure supply object not via stop valve 64, therefore, such as With reference to as Fig. 4 explanations, in hydraulic pump 31 operates, the hydraulic pressure from hydraulic pump 31 can be made hardly to accumulate in pressure accumulating chamber 65d, but suitably accumulate the pressure accumulating chamber 63d in main accumulator 63.Additionally, as illustrated with reference to Fig. 6, in hydraulic pump 31 In stopping, the hydraulic pressure in the loop comprising main accumulator 63 can be made to reduce its redundance.Resistance to thereby, it is possible to adopt The relatively low small scaled stop valve of pressure property is used as stop valve 64, therefore, it is possible to realize the reduction of the manufacturing cost of hydraulic pressure feeding mechanism. Additionally, as illustrated with reference to Fig. 8, when the operating of hydraulic pump 31 is started again at, can economically by hydraulic pump 31 The hydraulic pressure (working oil) being accumulated in stopping in pressure accumulating chamber 65d is supplied together with the hydraulic pressure of the pressure accumulating chamber 63d for carrying out autonomous accumulator 63 Hydraulic pressure supply object should be arrived.

Additionally, when the operating of hydraulic pump 31 is started again at, the working oil that accumulates in pressure accumulating chamber 65d can be discharged, therefore, When hydraulic pump 31 is stopped again, suitably a part for the hydraulic pressure in loop can be accumulated in pressure accumulating chamber 65d.Cause This, even if in the case where the operating/stopping of hydraulic pump 31 is repeated, it is also possible to effectively obtain the effect above.

Further, since back side room 65e supplies object with hydraulic pressure and hydraulic pump 31 is connected, therefore, it is possible to make by overflow Mechanism (intercommunicating pore 65g/ valve body 65h/ spring 65c) and the hydraulic pressure that is discharged in the 65e of back side room is further discharged into hydraulic pressure supply 31 side of object and hydraulic pump, thereby, it is possible to effectively obtaining the effect above, can avoiding main accumulator 63 and auxiliary storage pressure Effect as 65 grade of device is damaged.

Additionally, the present invention is not limited to illustrated embodiment, and can be implemented with various forms.For example, in reality Apply in mode, hydraulic pump 31 is gear pump, but can also be Gerotor pump, vane pump etc..Additionally, in embodiments, with pressure Shrunk-on ring spring is constituting spring 65c, and is disposed in the 65c of back side room, but it is also possible to spring 65c is constituted with extension spring, and It is disposed in pressure accumulating chamber 65d.Additionally, in embodiments, the 1st forcing unit that spring 65c is also used as in the present invention And the 2nd forcing unit, but two forcing units can also be respectively provided with.In such a case it is possible to use beyond spring Other appropriate forcing units, the 1st forcing unit and the 2nd forcing unit is for example constituted with rubber etc..

Additionally, in embodiments, make intercommunicating pore 65g be formed as section circle, but can for example be formed as section square Other appropriate shapes such as shape.Additionally, in embodiments, valve body 65h is made to be formed as spherical, but for example can be according to connection The shape in hole, forms coniform other appropriate shapes of grade.In such a case it is possible to make valve body 65h be configured to so-called butterfly Valve, in this case, makes valve body be formed as tabular, and is arranged at intercommunicating pore in a rotatable manner, the 1st that valve body is exerted a force Forcing unit is for example made up of torsion spring, which is arranged at intercommunicating pore.

Additionally, in embodiments, making the CL of main accumulator 63 and auxiliary accumulator 65 and clutch hydraulic pressure pipeline CLL Working connection 43 connects, but it is also possible to be connected with the PU working connections 51 of other oil circuits such as belt wheel fluid pressure line PUL.Additionally, In embodiment, main accumulator 63 is piston type accumulator, but can be bellows accumulator etc..Additionally, in embodiments, The back side room 65e and hydraulic pressure that auxiliary accumulator 65 can be made supplies object and hydraulic pump 31 is connected, it is also possible to do not connect, at this In the case of, auxiliary accumulator is different from the embodiment described above, but in the same manner as main accumulator 63, as the liquid from hydraulic pump The accumulation of pressure with accumulator using.Additionally, in such a case it is possible to omitting in main accumulator 63 and stop valve 64 extremely A few side.Additionally, the quantity of main accumulator 63 and auxiliary accumulator 65 can be multiple.

Additionally, in embodiments, using the magnetic valve that can be controlled under non-return valve mode and valve opening pattern To constitute stop valve 64, but it is also possible to by controlling valve closing/valve opening (or valve opening/valve closing) by excitation/non-excitation respectively , common magnetic valve constituting, or by fluid pressure type valve constituting.Additionally, in embodiments, as the present invention in The power source of vehicle, has used as petrolic engine 3, but can also be started using Diesel engine or LPG Machine etc..

Additionally, in embodiments, the hydraulic pressure supply object in the present invention is LU clutch 4c, buncher 6, advances Clutch 12 and reverse brake 13, however, it can be other the appropriate mechanisms for the hydraulic pressure for being supplied work, for example Can be lift variable mechanism and cam phase variable mechanism etc., wherein, the lift variable mechanism can make entering for internal combustion engine The lift of at least one party in air valve and air bleeding valve is changed, and the cam phase variable mechanism can enter to cam phase Row change, the cam phase are relative to being driven in the admission cam and exhaust cam of intake valve and air bleeding valve respectively The phase place of the bent axle of at least one party.Or, can be that the hydraulic pressure used in ship and airborne vehicle beyond vehicle etc. supplies reply As.Furthermore, it is possible to suitably change the structure of detail section in the range of present subject matter.

Claims (5)

1. a kind of hydraulic pressure feeding mechanism, it is characterised in that the hydraulic pressure feeding mechanism has：

Hydraulic pump, its are used for the hydraulic pressure for supplying object supply work to hydraulic pressure；

1st accumulator, which supplies object with the hydraulic pressure and the hydraulic pump is connected, for accumulating hydraulic pressure；

2nd accumulator, which has supplies the 2nd pressure accumulating chamber that object and the hydraulic pump are connected, the 2nd storage pressure with the hydraulic pressure Device is used for accumulating the hydraulic pressure from the hydraulic pump in the 2nd pressure accumulating chamber；And

Stop valve, consisting of can make to connect between the hydraulic pressure supply object and the hydraulic pump and the 2nd pressure accumulating chamber Logical/cut-off,

1st accumulator has：

Cylinder body；

Piston, its are slidably disposed in the cylinder interior, and the cylinder interior is divided into back side room and fluid accumulation 1st pressure accumulating chamber of pressure；

1st forcing unit, which is towards the 1st pressure accumulating chamber side to the piston force；

Intercommunicating pore, its are formed in the piston in the way of making the 1st pressure accumulating chamber be communicated with each other with the back side room；

Valve body, its are arranged on the cylinder interior, the detent position of the intercommunicating pore closing is made and can make the intercommunicating pore Move between open release position；And

2nd forcing unit, its are arranged on the cylinder interior, are configured to：So that the valve body is maintained at the detent position Mode exert a force, also, the hydraulic pressure in the 1st pressure accumulation room reach regulation higher limit when, it is allowed to the valve body is from described Detent position to the release position side shifting,

The hydraulic pump with the power source of vehicle as driving source,

1st pressure accumulating chamber of the 1st accumulator supplies object and the liquid via the stop valve with the hydraulic pressure Press pump is connected, and is connected with the 2nd pressure accumulating chamber in the way of not via the stop valve.

2. hydraulic pressure feeding mechanism according to claim 1, it is characterised in that

The stop valve is made up of magnetic valve, the magnetic valve optionally can be controlled to play a role as check-valves only Valve mode and the valve opening pattern being forced open is returned, under the non-return valve mode, the hydraulic pressure in the 2nd pressure accumulating chamber side is less than During the hydraulic pressure of the hydraulic pressure supply object and the hydraulic pressure pump side, the hydraulic pressure supply object and the hydraulic pump and institute is made State, the hydraulic pressure in the 2nd pressure accumulating chamber side supplies object and the hydraulic pump higher than the hydraulic pressure During the hydraulic pressure of side, make to end between the hydraulic pressure supply object and the hydraulic pump and the 2nd pressure accumulating chamber.

3. hydraulic pressure feeding mechanism according to claim 2, it is characterised in that

1st forcing unit and the 2nd forcing unit are made up of public single force application part each other, the force application part The valve body is exerted a force towards the detent position side, and the piston is exerted a force towards the 1st pressure accumulating chamber side via the valve body.

4. hydraulic pressure feeding mechanism according to claim 3, it is characterised in that

The valve body is formed as spherical, closes the intercommunicating pore with the edge of the intercommunicating pore by abutting.

5. the hydraulic pressure feeding mechanism according to any one in Claims 1 to 4, it is characterised in that

Object and institute are supplied with the hydraulic pressure in the way of not via the stop valve in the back side room of the 1st accumulator State hydraulic pump connection.