CN104553770A - Hydraulic supply device - Google Patents

Abstract

Provided is a hydraulic supply device. The hydraulic supply device helps to avoid damage to a first accumulator and makes the device small-sized. The first accumulator (65) of the hydraulic supply device is provided with a cylinder body (65a), a piston (65b), a first force-applying unit (65c), a communicating hole (65g), a valve body (65h) and a second force-applying unit (65c). The piston (65b) can be slidably arranged in the interior of the cylinder body (65a) and enables the interior of the cylinder body (65a) to be segmented to a back-side chamber (65e) and a first pressure accumulation chamber (65d) of accumulated hydraulic pressure. The first force-applying unit applies force towards a piston (65b) of the side of the first pressure accumulation chamber. The communicating hole is formed in the piston (65b) so that the first pressure accumulation chamber (65d) is communicated with the back-side chamber (65e). The valve body is arranged in the interior of the cylinder body (65a) and is enabled to move between the closing position for closing the communicating hole (65c) and an opening position for opening the communicating hole (65g). The second force-applying unit (65c) is arranged in the interior of the cylinder body (65a) such that the valve body (65h) applies force at the closing position. When hydraulic pressure in the first pressure accumulation chamber (65d) reaches the stated upper limit, the valve body (65h) is allowed to move from the closing position to the opening position.

Description

Hydraulic pressure feeding mechanism

Technical field

The present invention relates to the hydraulic pressure feeding mechanism to hydraulic pressure supply object sap pressure supply.

Background technology

In the past, as this hydraulic pressure feeding mechanism, such as, there will be a known the structure disclosed in patent documentation 1.This hydraulic pressure feeding mechanism is arranged at the vehicle using driving engine as propulsion source, and the power-transfer clutch sap pressure supply of advancing to this vehicle.Hydraulic pressure feeding mechanism has: Hydraulic Pump, its with above-mentioned driving engine for drive source; And main line, it is for being fed to power-transfer clutch by the hydraulic pressure from this Hydraulic Pump.This main line is connected with accumulator via looped pipeline road.In addition, in looped pipeline road, be provided with the shutoff valve be made up of electromagnetic valve, utilize the opening and closing of this shutoff valve to make looped pipeline road open and closed.

In the hydraulic pressure feeding mechanism of above structure, when engine running, Hydraulic Pump driven by the engine is utilized to come via main line to power-transfer clutch sap pressure supply.In addition, utilize shutoff valve to make looped pipeline road keep open state, the hydraulic pressure of self-hydraulic pump is fed to accumulator and savings via main line and looped pipeline road in the future thus.In addition, when engine automatic stop, utilize shutoff valve that looped pipeline road is closed, make thus to end between accumulator and main line, thus keep putting aside the hydraulic pressure in accumulator so far.In addition, when the driving engine under automatic stop condition is reset, utilize shutoff valve to make looped pipeline road open, accompany therewith, the hydraulic pressure put aside in accumulator is supplied to power-transfer clutch via looped pipeline road and main line.

Patent documentation 1: No. 3807145th, Japanese Patent

Summary of the invention

As described above, in hydraulic pressure feeding mechanism in the past, when engine running, the higher hydraulic pressure from Hydraulic Pump is fed to accumulator via main line and looped pipeline road.Therefore, in the automatic stopping of driving engine, when utilizing shutoff valve to be closed in the loop comprising this looped pipeline road and accumulator to keep putting aside hydraulic pressure in accumulator, in the closed-loop be closed directly savings from the hydraulic pressure of the high pressure of Hydraulic Pump.In addition, the working oil pumped from Hydraulic Pump is used to joint and the lubrication of power-transfer clutch, and therefore, its temperature rises along with the process of the time of run of driving engine.Thus, in above-mentioned closed-loop, have accumulated very high hydraulic pressure, thus it is damaged likely to make accumulator and looped pipeline road occur.

In addition, the hydraulic pressure in the problems referred to above, release closed-loop, considers to arrange overflow mechanism further, but in this case, makes device correspondingly become maximization because of this overflow mechanism.

The present invention completes to solve above such problem, object be to provide a kind of can avoid the 1st accumulator breakage and can the hydraulic pressure feeding mechanism of miniaturization of the apparatus.

In order to reach above-mentioned purpose, the feature of the hydraulic pressure feeding mechanism of the invention of first aspect is to have: Hydraulic Pump 31, it is for the hydraulic pressure to hydraulic pressure supply object ((following, identical in this) the LU power-transfer clutch 4c in embodiment, toric transmission 6, forward clutch 12, reverse brake 13) supply work; And the 1st accumulator (auxiliary accumulator 65), it supplies object with hydraulic pressure and Hydraulic Pump 31 is connected, and for accumulating hydraulic pressure, the 1st accumulator is configured to be had: cylinder body 65a; Piston 65b, it is inner that it is slidably arranged on cylinder body 65a, is the 1st pressure accumulating chamber (pressure accumulating chamber 65d) and room, the back side 65e of accumulation hydraulic pressure by cylinder body 65a inside division; 1st forcing unit (spring 65c), its Chao 1 pressure accumulating chamber side exerts a force to piston 65b; Intercommunicating pore 65g, it is formed in piston 65b, and the 1st pressure accumulating chamber and room, back side 65e are communicated with each other; Valve body 65h, it is inner that it is arranged on cylinder body 65a, and can make to move between the open release position of intercommunicating pore 65g at the detent position making intercommunicating pore 65g close; And the 2nd forcing unit (spring 65c), it is inner that it is arranged on cylinder body 65a, exerts a force in the mode making valve body 65h remain on detent position, and, when hydraulic pressure in the 1st pressure accumulating chamber reaches set upper limit value, valve body 65h is allowed to move from detent position to side, release position.

According to this structure, supply the hydraulic pressure of object supply work from Hydraulic Pump to hydraulic pressure, and the 1st accumulator for accumulating hydraulic pressure supplies object with hydraulic pressure and Hydraulic Pump is connected.In addition, the 1st accumulator has cylinder body and piston, and piston is slidably arranged on cylinder interior, and cylinder interior is divided into the 1st pressure accumulating chamber and the room, the back side of accumulation hydraulic pressure by piston.In addition, piston is exerted a force by the 1st forcing unit Chao 1 pressure accumulating chamber side.In addition, in piston, be formed with intercommunicating pore, the 1st pressure accumulating chamber and room, the back side are communicated with each other, in cylinder interior, be provided with valve body and the 2nd forcing unit.

This valve body and can make to move between the open release position of intercommunicating pore at the detent position making intercommunicating pore close, 2nd forcing unit exerts a force in the mode making valve body and remain on detent position, and, when hydraulic pressure in the 1st pressure accumulating chamber reaches set upper limit value, valve body is allowed to move from detent position to side, release position.Thus, when hydraulic pressure in the 1st pressure accumulating chamber becomes larger, intercommunicating pore can be made open by valve body, thus, made the 1st pressure accumulating chamber be communicated with between room, the back side by intercommunicating pore, therefore, it is possible to make the excess electron excess fraction of the hydraulic pressure in the 1st pressure accumulating chamber be discharged in room, the back side and prevent its excessiveization, thus the breakage of the devices such as the 1st accumulator can be avoided.

In addition, as mentioned above, intercommunicating pore, valve body and the 2nd forcing unit play a role as so-called overflow mechanism.According to said structure, these intercommunicating pores, valve body and the 2nd forcing unit are all arranged dividually less than with the 1st accumulator, but are arranged in the cylinder body of the 1st accumulator, therefore, it is possible to miniaturization of the apparatus.

The feature of the invention of second aspect is, in the hydraulic pressure feeding mechanism described in first aspect, Hydraulic Pump 31 with the propulsion source of vehicle (driving engine 3) for drive source, described hydraulic pressure feeding mechanism also has: the 2nd accumulator (main accumulator 63), it has the 2nd pressure accumulating chamber (pressure accumulating chamber 63d) supplying object and Hydraulic Pump 31 with hydraulic pressure and be communicated with, and for future, the hydraulic pressure of self-hydraulic pump 31 is accumulated in the 2nd pressure accumulating chamber; Shutoff valve 64, consist of and hydraulic pressure can be made to supply object and be communicated with/end between Hydraulic Pump 31 with the 2nd pressure accumulating chamber, 1st pressure accumulating chamber of the 1st accumulator supplies object via shutoff valve 64 with hydraulic pressure and Hydraulic Pump 31 is communicated with, and is communicated with the 2nd pressure accumulating chamber in the mode not via shutoff valve 64.

According to this structure, Hydraulic Pump with the propulsion source of vehicle for drive source.In addition, the 2nd pressure accumulating chamber of the 2nd accumulator supplies object with hydraulic pressure and Hydraulic Pump is communicated with, and can accumulate the hydraulic pressure from Hydraulic Pump.In addition, by shutoff valve, hydraulic pressure is made to supply object and be communicated with/end between Hydraulic Pump with the 2nd pressure accumulating chamber.By the connection of this shutoff valve, can the hydraulic pressure of in the future self-hydraulic pump accumulate in the 2nd pressure accumulating chamber, by the cut-off of shutoff valve, the 2nd pressure accumulating chamber can be made to close, thereby, it is possible to keep the hydraulic pressure accumulated in the 2nd pressure accumulating chamber.In addition, can by the connection based on shutoff valve, the hydraulic pressure accumulated in hydraulic pressure supply object supply the 2nd pressure accumulating chamber.

In addition, 1st pressure accumulating chamber of the 1st accumulator described in the explanation of the invention of first aspect supplies object via shutoff valve with hydraulic pressure and Hydraulic Pump is communicated with, therefore, by the cut-off based on above-mentioned shutoff valve, except can make the 2nd pressure accumulating chamber close except, the 1st pressure accumulating chamber can also be made to close, therefore, it is possible to keep the hydraulic pressure accumulated in Liang Ge pressure accumulating chamber.In addition, 1st pressure accumulating chamber is communicated with the 2nd pressure accumulating chamber in the mode not via shutoff valve, therefore, excessiveization of the hydraulic pressure (working oil) in the closed-loop comprising the 1st pressure accumulating chamber and the 2nd pressure accumulating chamber that is closed due to the cut-off based on shutoff valve can be prevented by the overflow mechanism (intercommunicating pore/valve body/the 2nd forcing unit) described in the explanation of the invention of first aspect, thus the breakage such as the 1st accumulator and the 2nd accumulator can be avoided.

The feature of the invention of the third aspect is, in the hydraulic pressure feeding mechanism described in second aspect, shutoff valve 64 is made up of electromagnetic valve, the valve opening pattern that this electromagnetic valve optionally can control the boiler check valve pattern for playing a role as boiler check valve and be forced open, under boiler check valve pattern, when hydraulic pressure in the 2nd pressure accumulating chamber side supplies the hydraulic pressure of object and Hydraulic Pump 31 side lower than hydraulic pressure, hydraulic pressure is made to supply object and be communicated with between Hydraulic Pump 31 with the 2nd pressure accumulating chamber, when hydraulic pressure in the 2nd pressure accumulating chamber side supplies the hydraulic pressure of object and Hydraulic Pump 31 side higher than hydraulic pressure, hydraulic pressure is made to supply object and end between Hydraulic Pump 31 and the 2nd pressure accumulating chamber.

According to this structure, shutoff valve is formed can optionally be controlled as non-return valve mode and valve opening pattern, under boiler check valve pattern, when hydraulic pressure in the 2nd pressure accumulating chamber side supplies the hydraulic pressure of object and hydraulic pressure pump side lower than hydraulic pressure, hydraulic pressure is made to supply object and be communicated with between Hydraulic Pump with the 2nd pressure accumulating chamber, hydraulic pressure in the 2nd pressure accumulating chamber side supplies the hydraulic pressure of object and hydraulic pressure pump side higher than hydraulic pressure, makes hydraulic pressure supply object and end between Hydraulic Pump and the 2nd pressure accumulating chamber.Thereby, it is possible to effectively obtain the above-mentioned effect of the invention based on second aspect, that is, in the future the hydraulic pressure of self-hydraulic pump to be accumulated in the 2nd pressure accumulating chamber and the effect that accumulated hydraulic pressure can be kept such.In addition, under boiler check valve pattern, there is no need for the special control action that the opening and closing of shutoff valve is switched, therefore, it is possible to carry out the accumulation/maintenance of hydraulic pressure to the 2nd pressure accumulating chamber simply.

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

According to this structure, the 1st forcing unit and the 2nd forcing unit are made up of public single force application part each other, therefore, correspondingly can cut down number of components because of this part.In addition, utilize this force application part to exert a force to valve body towards detent position side, and via valve body Chao 1 pressure accumulating chamber side, piston is exerted a force, thereby, it is possible to suitably carry out the accumulation of valve body towards the maintenance of detent position and the hydraulic pressure based on the 1st accumulator.

The feature of the invention of the 5th aspect is, in the hydraulic pressure feeding mechanism described in fourth aspect, valve body 65h is formed as spherical, by making valve body 65h abut with the edge of intercommunicating pore 65g, intercommunicating pore 65g is closed.

According to this structure, to abut with the edge of intercommunicating pore by making valve body and intercommunicating pore is closed.In addition, valve body is formed as spherical, therefore, it is possible to suppress the one-sided abutting towards the edge of intercommunicating pore, thus valve body can be utilized to come suitably closed communication hole.

The feature of the invention of the 6th aspect is, in the hydraulic pressure feeding mechanism described in any one in the second ~ five, room, the back side 65e of the 1st accumulator is not to supply object via the mode of shutoff valve 64 with hydraulic pressure and Hydraulic Pump 31 is communicated with.

According to this structure, the room, the back side of the 1st accumulator supplies object with hydraulic pressure and Hydraulic Pump is communicated with, and therefore, in Hydraulic Pump running, the hydraulic pressure from Hydraulic Pump is supplied in this room, back side.Room, the back side be between across the 1st accumulator piston and mark off in the side contrary with the 1st pressure accumulating chamber, therefore, Hydraulic Pump running in, the hydraulic pressure being fed to room, the back side plays a role as back pressure, thus, Chao 1 pressure accumulating chamber side pushing piston.Like this, in Hydraulic Pump running, piston by the application force of above-mentioned 1st forcing unit and these both sides of back pressure effect by Chao 1 pressure accumulating chamber thruster pressure, therefore, by suitably setting the application force of the 1st forcing unit, the hydraulic pressure from Hydraulic Pump can be made to accumulate hardly in the 1st pressure accumulating chamber, and suitably accumulate in the 2nd pressure accumulating chamber at above-mentioned 2nd accumulator.

In addition, when making Hydraulic Pump stop, no longer effect has above-mentioned back pressure thereupon.In addition, room, the back side is not to supply object via the mode of shutoff valve with hydraulic pressure and Hydraulic Pump is communicated with, and therefore, the hydraulic pressure in the closed-loop comprising the 2nd pressure accumulating chamber be closed because of the cut-off based on shutoff valve is no longer fed to room, the back side.In addition, as mentioned above, the 1st pressure accumulating chamber of the 1st accumulator is not to be communicated with the 2nd pressure accumulating chamber of the 2nd accumulator via the mode of shutoff valve.According to above explanation, such as, because of the connection based on above-mentioned shutoff valve in the future the hydraulic pressure of self-hydraulic pump accumulate in the 2nd pressure accumulating chamber, and when utilizing the cut-off based on shutoff valve to keep being accumulated in the hydraulic pressure in the 2nd pressure accumulating chamber so far during Hydraulic Pump stops, following effect can be obtained.

That is, according to said structure, along with Hydraulic Pump stops, only the application force of the 1st forcing unit presses the thrust pressure of the piston of the 1st accumulator to play a role as the thruster of Chao 1 pressure accumulating chamber.Therefore, can by suitably setting the application force of the 1st forcing unit, utilize the hydraulic pressure of the interior accumulation of the closed-loop being cut off valve closure, piston is made to resist the application force of the 1st forcing unit and move towards side, room, the back side, a part for hydraulic pressure (working oil) in this closed-loop can be fed to the 1st pressure accumulating chamber, and be accumulated in wherein.Therefore, in Hydraulic Pump stops, the hydraulic pressure in closed-loop can be made to reduce and to fall its redundance.Thus, as shutoff valve, the small-sized shutoff valve that resistance to pressure is lower can be adopted, therefore, it is possible to realize the reduction of the manufacturing cost of hydraulic pressure feeding mechanism.

In addition, such as, when again starting the running of Hydraulic Pump, when having carried out the connection based on shutoff valve, along with the hydraulic pressure accumulated in the 2nd pressure accumulating chamber is supplied to hydraulic pressure supply object, the thrust pressure be made up of these both sides of application force of back pressure and the 1st forcing unit presses the thrust pressure of the piston of the 1st accumulator to play a role again as the thruster of Chao 1 pressure accumulating chamber.Thus, when again starting the running of Hydraulic Pump, object can be supplied without lavishly the hydraulic pressure (working oil) being accumulated in the 1st pressure accumulating chamber in the stopping of above-mentioned Hydraulic Pump being fed to hydraulic pressure together with the hydraulic pressure from the 2nd pressure accumulating chamber.

In addition, as mentioned above, when again starting the running of Hydraulic Pump, the working oil be accumulated in the 1st pressure accumulating chamber can be discharged, therefore, when Hydraulic Pump stops again, can suitably a part for the hydraulic pressure in closed-loop be accumulated in the 1st pressure accumulating chamber.Therefore, even if when repeatedly carrying out the running/stopping of Hydraulic Pump, also above-mentioned effect can effectively be obtained.

In addition, room, the back side supplies object with hydraulic pressure and Hydraulic Pump is communicated with, therefore, by above-mentioned overflow mechanism (intercommunicating pore/valve body/the 2nd forcing unit), the hydraulic pressure be discharged in room, the back side can be discharged into hydraulic pressure supply object and hydraulic pressure pump side further, thus, effectively can obtain the above-mentioned effect of the invention of second aspect, namely can avoid the 1st accumulator and the damaged such effect of the 2nd accumulator.

Accompanying drawing explanation

Fig. 1 is the skeleton diagram of the vehicle that the hydraulic pressure feeding mechanism applying present embodiment is roughly shown.

Fig. 2 is the hydraulic circuit diagram that hydraulic pressure feeding mechanism etc. is shown.

Fig. 3 is the block diagram of the ECU that hydraulic pressure feeding mechanism is shown etc.

Fig. 4 is the figure of the pressure accumulater roughly illustrated in internal combustion engine operation etc.

Fig. 5 be illustrate that ECU as shown in Figure 3 performs, for the diagram of circuit of the process of the action of the various valves of hydraulic control feeding mechanism.

Fig. 6 is less than the situation of set upper limit value for the hydraulic pressure in closed-loop and the figure of the pressure accumulater in the automatic stopping of combustion engine etc. is roughly shown.

Fig. 7 reaches the situation of higher limit for the hydraulic pressure in closed-loop and the figure of the pressure accumulater in the automatic stopping of combustion engine etc. is roughly shown.

Fig. 8 is the figure of pressure accumulater when roughly illustrating that combustion engine is reset from automatic stop condition etc.

Fig. 9 is the sequential chart of the action case that hydraulic pressure feeding mechanism is shown.

Label declaration

3 driving engines (propulsion source of vehicle)

4c LU power-transfer clutch (hydraulic pressure supply object)

6 toric transmissions (hydraulic pressure supply object)

12 forward clutch (hydraulic pressure supply object)

13 reverse brake (hydraulic pressure supply object)

31 Hydraulic Pumps

63 main accumulators (the 2nd accumulator)

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

64 shutoff valves

65 auxiliary accumulators (the 1st accumulator)

65a cylinder body

65b piston

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

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

Room, the 65e back side

65g intercommunicating pore

65h valve body

Detailed description of the invention

Below, with reference to accompanying drawing, the preferred embodiment of the present invention is described in detail.The drive system of the vehicle shown in Fig. 1 has: combustion engine (hereinafter referred to as " driving engine ") 3, and it is the propulsion source of vehicle; And torque transfer T, it is for being delivered to the left and right sidesing driving wheel DW (illustrate only right drive wheel) of vehicle by the propulsive effort of this driving engine 3.Driving engine 3 is engine petrol, and it has the bent axle 3a for output drive strength.In addition, torque transfer T has tor-con 4, forward/backward switching mechanism 5 and toric transmission 6.

Tor-con 4 is made up of pump impeller 4a, turbine 4b and lock-up clutch (hereinafter referred to as " LU power-transfer clutch ") 4c etc.Pump impeller 4a and bent axle 3a connects, and turbine 4b and input shaft described later 14 connect, between both 4a, 4b, be filled with working oil.Substantially, the propulsive effort (hereinafter referred to as " engine drive power ") of driving engine 3 is passed to input shaft 14 via pump impeller 4a, working oil and turbine 4b.

LU power-transfer clutch 4c is hydraulic clutch, and LU power-transfer clutch 4c is provided with 1LU grease chamber 4d and 2LU grease chamber 4e (with reference to Fig. 2).Supply the hydraulic pressure to 1LU grease chamber 4d, and from 2LU grease chamber 4e, hydraulic pressure (working oil) is discharged, LU power-transfer clutch 4c becomes engagement state thus, in contrast, supply the hydraulic pressure to 2LU grease chamber 4e, and discharged by working oil from 1LU grease chamber 4d, LU power-transfer clutch 4c becomes release position thus.By the joint of this LU power-transfer clutch 4c, make the state becoming directly connection between the bent axle 3a of driving engine 3 and input shaft 14.In addition, the degree of engagement of LU power-transfer clutch 4c changes with the hydraulic pressure (amount of working oil) being fed to 1LU grease chamber 4d or 2LU grease chamber 4e.

Forward/backward switching mechanism 5 has planetary gear apparatus 11, forward clutch 12 and reverse brake 13.Planetary gear apparatus 11 is the planetary gear apparatus of single pinion type, and it is formed by with lower part: sun gear 11a; Gear ring 11b; The multiple planetary wheel 11c (only illustrating 2) engaged with sun gear 11a and gear ring 11b; And pinion carrier 11d, these planetary wheels 11c supports as rotating by it.Sun gear 11a and input shaft 14 are set to one.

Forward clutch 12 is hydraulic clutch, is installed as one inside it with input shaft 14, and the outside of forward clutch 12 and gear ring 11b and main shaft 21 are installed as integrally.This main shaft 21 is formed as hollow form, is configured with input shaft 14 within it in the mode that can rotate.By the joint of forward clutch 12, input shaft 14 and main shaft 21 are directly connect, allow the differential speed rotation between input shaft 14 and main shaft 21 by the release of forward clutch 12.In addition, reverse brake 13 is made up of the power-transfer clutch etc. of fluid pressure type, and it is installed in pinion carrier 11d, when being in engagement state, pinion carrier 11d is held in and cannot rotates by reverse brake 13, and when being in release position, reverse brake 13 allows the rotation of pinion carrier 11d.

In addition, forward clutch 12 has FWD grease chamber 12a (with reference to Fig. 2), by FWD grease chamber 12a sap pressure supply, making forward clutch 12 become engagement state, by stopping the supply of this hydraulic pressure, making forward clutch 12 become release position.In addition, reverse brake 13 has RVS grease chamber 13a (with reference to Fig. 2), by RVS grease chamber 13a sap pressure supply, making reverse brake 13 become engagement state, by stopping the supply of this hydraulic pressure, making reverse brake 13 become release position.The degree of engagement of forward clutch 12 and reverse brake 13 changes along with the hydraulic pressure (amount of working oil) supplied to FWD grease chamber 12a and RVS grease chamber 13a respectively.

In the forward/backward switching mechanism 5 of above structure, when vehicle advances, engage forward clutch 12, and discharge reverse brake 13.Thus, main shaft 21 and input shaft 14 rotate to equidirectional with same rotational speed.On the other hand, when vehicle rollback, release forward clutch 12, and engage reverse brake 13.Thus, main shaft 21 rotates to the direction contrary with input shaft 14.

Toric transmission 6 is belt-type transmission, and it possesses described main shaft 21, driving pulley 22, driven pulley 23, driving band 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, and it can move along the axis direction of main shaft 21, and cannot relatively rotate, and fixed part 22b is fixed on main shaft 21.Between both 22a, 22b, be formed with the trough of belt of V shape, this trough of belt is for the driving band 24 that reels.In addition, movable part 22a is provided with DR grease chamber 22c (with reference to Fig. 2), and by making movable part 22a move in the axial direction to this DR grease chamber 22c sap pressure supply, thus, the belt wheel width of driving pulley 22 is changed, and its effective diameter changes.

Driven pulley 23 is formed in the mode same with described driving pulley 22, and its movable part 23a is installed in countershaft 25, and this movable part 23a can move along the axis direction of countershaft 25 and cannot rotate, and fixed part 23b is fixed on countershaft 25.The trough of belt of V shape is formed between both 23a, 23b.In addition, movable part 23a is provided with DN grease chamber 23c (with reference to Fig. 2) and pull back spring 23d.By making movable part 23a move in the axial direction to this DN grease chamber 23c sap pressure supply, the belt wheel width of driven pulley 23 is changed thus, and its effective diameter changes.In addition, pull back spring 23d exerts a force to fixed part 23b side to movable part 23a.Driving band 24 hangs around two belt wheels 22,23 with the state of the trough of belt being embedded in two belt wheels 22,23.

Above, in toric transmission 6, by the DR grease chamber 22c of driving pulley 22 and the DN grease chamber 23c sap pressure supply of driven pulley 23, infinitely change the effective diameter of two belt wheels 22,23, come thus infinitely to control its converter speed ratio.This converter speed ratio is the ratio of the rotating speed of driving pulley 22 and the rotating speed of driven pulley 23.

In addition, be fixed with gear 25a at countershaft 25, this gear 25a engages with the gear G of differential gear train DF via idler gear IG1, IG2, and idler gear IG1, IG2 and pony axle IS are set to one, and this idler gear IG1, IG2 are small one and large one.The drive wheel DW of differential gear train DF and left and right connects.

In the drive system of above structure, engine drive power is passed to the drive wheel DW of left and right via tor-con 4, forward/backward switching mechanism 5, toric transmission 6 and differential gear train DF.Now, utilize forward/backward switching mechanism 5, the hand of rotation of the propulsive effort of transmission is switched between forward direction and reverse directions, carries out the forward/backward of vehicle thus.In addition, engine drive power, under carrying out infinite variable speed state by toric transmission 6, is passed to drive wheel DW.

Next, with reference to Fig. 2, be described hydraulic pressure feeding mechanism, this hydraulic pressure feeding mechanism is to the 1st and 2LU grease chamber 4d, the 4e of above-mentioned LU power-transfer clutch 4c, the FWD grease chamber 12a of forward clutch 12, the RVS grease chamber 13a of reverse brake 13 and the hydraulic pressure DR grease chamber 22c of toric transmission 6 and DN grease chamber 23c being supplied to work.Below, suitably LU power-transfer clutch 4c, forward clutch 12, reverse brake 13 and toric transmission 6 are referred to as " hydraulic pressure supply object ".

Hydraulic pressure feeding mechanism possesses: Hydraulic Pump 31; LU hydraulic tubing LUL, it is for 1LU grease chamber 4d and 2LU grease chamber 4e sap pressure supply; Clutch hydraulic pressure pipeline CLL, it is for FWD grease chamber 12a and RVS grease chamber 13a sap pressure supply; And belt wheel hydraulic tubing PUL, it is for DR grease chamber 22c and DN grease chamber 23c sap pressure supply.

The gear type pump that Hydraulic Pump 31 is is drive source with driving engine 3, and connect with bent axle 3a.Hydraulic Pump 31 is connected with PH pressure regulating valve (PH REG VLV) 32 via oil circuit, and the working oil be accumulated in oil reservoir R is pumped into PH pressure regulating valve 32.PH pressure regulating valve 32 is made up of mechanical type guiding valve, and in Hydraulic Pump 31 operates, the hydraulic pressure of self-hydraulic pump 31 is carrying out being fed to above-mentioned LU hydraulic tubing LUL, clutch hydraulic pressure pipeline CLL and belt wheel hydraulic tubing PUL under the state adjusted in the future.

LU hydraulic tubing LUL is made up of following part etc.: TC pressure regulating valve (TC REG VLV) 33, and it is connected with PH pressure regulating valve 32 via oil circuit; LU control cock (LU CTL VLV) 34, it is connected with TC pressure regulating valve 33 via oil circuit; And LU transfer valve (LU SFT VLV) 35, it is connected with 2LU grease chamber 4e via the 1LU grease chamber 4d of oil circuit with LU control cock 34 and LU power-transfer clutch 4c.This TC pressure regulating valve 33, LU control cock 34 and LU transfer valve 35 are made up of guiding valve.In oil pump 31 operates, be fed to 1LU grease chamber 4d or the 2LU grease chamber 4e of LU power-transfer clutch 4c via TC pressure regulating valve 33, LU control cock 34 and LU transfer valve 35 etc. from the hydraulic pressure of PH pressure regulating valve 32.

In addition, the hydraulic pressure from aftermentioned reducing valve (CR VLV) 42 is fed to LU control cock 34 with the state after utilizing the 1st electromagnetic valve (LS-LCC) SV1 to carry out pressure regulation.Thus, by driving LU control cock 34, making hydraulic pressure (amount of the working oil) change being fed to 1LU grease chamber 4d or 2LU grease chamber 4e, and then changing the degree of engagement of LU power-transfer clutch 4c.Like this, by making the aperture of the 1st electromagnetic valve SV1 change, the degree of engagement of LU power-transfer clutch 4c is changed.The aperture of the 1st electromagnetic valve SV1 is controlled (with reference to Fig. 3) by ECU described later (Electronic Control Unit: electronic control unit) 2.

In addition, the 2nd electromagnetic valve (SOL-A) SV2 is connected with at LU transfer valve 35.Drive LU transfer valve 35 by the excitation/non-excitation of the 2nd electromagnetic valve SV2, thus, the supply destination of the hydraulic pressure from LU control cock 34 is switched to 1LU grease chamber 4d or 2LU grease chamber 4e.Thus, supply the hydraulic pressure to 1LU grease chamber 4d as described above, and from 2LU grease chamber 4e, working oil is discharged, become engagement state thus, in contrast, supply the hydraulic pressure to 2LU grease chamber 4e, and from 1LU grease chamber 4d, working oil is discharged, become release position thus.Excitation/non-the excitation of the 2nd electromagnetic valve SV2 control by ECU2 (with reference to Fig. 3).

Described clutch hydraulic pressure pipeline CLL is made up of branch's oil circuit 41, reducing valve 42, CL working connection 43, the 3rd electromagnetic valve (LS-CPC) SV3 and hand valve (MAN VLV) 44 etc.One end of branch's oil circuit 41 is connected with PU working connection 51 described later, and the other end is connected with reducing valve 42.PU working connection 51 is connected with PH pressure regulating valve 32, and in the running of Hydraulic Pump 31, the hydraulic pressure from PH pressure regulating valve 32 is fed to reducing valve 42 via PU working connection 51 and branch's oil circuit 41.

Reducing valve 42 is made up of mechanical type guiding valve, and it is connected with hand valve 44 via CL working connection 43, in the midway of CL working connection 43, is provided with the 3rd electromagnetic valve SV3 for making it carry out opening and closing.In the running of Hydraulic Pump 31, the hydraulic pressure being fed to reducing valve 42 by PH pressure regulating valve 32 is depressurized valve 42 and reduces pressure, and further to be fed to hand valve 44 by the state after the 3rd electromagnetic valve SV3 pressure regulation via CL working connection 43.

Hand valve 44 is made up of guiding valve, and it is connected with RVS grease chamber 13a with FWD grease chamber 12a via oil circuit.In addition, when the gear of the shifter bar (not shown) of driver's operation of vehicle is in activation point, movement position or low gear position, hand valve 44 selects FWD grease chamber 12a to be used as the supply destination of the hydraulic pressure from the 3rd electromagnetic valve SV3, when being in car backing position, select RVS grease chamber 13a as the supply destination of the hydraulic pressure from the 3rd electromagnetic valve SV3.Thus, aforesaid forward/backward switching mechanism 5 is utilized to carry out the switching of the hand of rotation of propulsive effort.Now, by making the aperture of the 3rd electromagnetic valve SV3 change, adjust the hydraulic pressure being fed to FWD grease chamber 12a or RVS grease chamber 13a, thus change the degree of engagement of forward clutch 12 or reverse brake 13.The aperture of the 3rd electromagnetic valve SV3 control by ECU2 (with reference to Fig. 3).

Described belt wheel hydraulic tubing PUL is made up of PU working connection 51, DR pressure regulating valve (DR REG VLV) 52 and DN pressure regulating valve (DN REG VLV) 53 etc.One end of PU working connection 51 is connected with PH pressure regulating valve 32, and the branch 51c on way is branched off into 1PU working connection 51a and 2PU working connection 51b two strands wherein.In addition, DR pressure regulating valve 52 and DN pressure regulating valve 53 are formed by guiding valve, and are arranged on the midway of 1PU working connection 51a and 2PU working connection 51b respectively.The tributary circuit 41 of aforesaid clutch hydraulic pressure pipeline CLL from PU working connection 51 than branch 51c by PH pressure regulating valve 32 side element branches out.In the running of Hydraulic Pump 31, the hydraulic pressure from PH pressure regulating valve 32 is supplied to DR grease chamber 22c and DN grease chamber 23c respectively via PU working connection 51,1PU working connection 5a and 2PU working connection 51b and DR pressure regulating valve 52 and DN pressure regulating valve 53.

In addition, the hydraulic pressure from reducing valve 42 is fed to DR pressure regulating valve 52 with the state after utilizing the 4th electromagnetic valve (LS-DR) SV4 pressure regulation.Thus, by driving DR pressure regulating valve 52, making hydraulic pressure (amount of the working oil) change being fed to DR grease chamber 22c, and then changing the effective diameter of driving pulley 22.Like this, by making the aperture of the 4th electromagnetic valve SV4 change, the effective diameter of driving pulley 22 is changed.The aperture of the 4th electromagnetic valve SV4 is controlled (with reference to Fig. 3) by ECU2.

Hydraulic pressure from reducing valve 42 is fed to DN pressure regulating valve 53 with the state after utilizing the 5th electromagnetic valve (LS-DN) SV5 pressure regulation.Thus, by driving DN pressure regulating valve 53, making hydraulic pressure (amount of the working oil) change being fed to DN grease chamber 23c, and then changing the effective diameter of driven pulley 23.Like this, by making the aperture of the 5th electromagnetic valve SV5 change, the effective diameter of driven pulley 23 is changed.The aperture of the 5th electromagnetic valve SV5 is controlled (with reference to Fig. 3) by ECU2.

In addition, in the part than DN pressure regulating valve 53 downstream of 2PU working connection 51b, hydraulic pressure transducer 71 is connected with via oil circuit.Hydraulic pressure transducer 71 is the strain gage sensors by carrying out action from the electric power supply of aftermentioned power supply 2a, its hydraulic pressure detecting the part than DN pressure regulating valve 53 downstream of 2PU working connection 51b is (following, be called " PU hydraulic pressure "), and its detection signal is outputted to ECU2.Below, the PU hydraulic pressure detected by hydraulic pressure transducer 71 is called " detecting PU hydraulic pressure POD ".

In addition, hydraulic pressure feeding mechanism is provided with standby valve (B/U VLV) BV, this standby valve BV is used for the supply of the hydraulic pressure guaranteed when the 3rd electromagnetic valve SV3 fault forward clutch 12 and reverse brake 13.This standby valve BV is arranged on the part of ratio the 3rd electromagnetic valve SV3 by hand valve 44 side of aforesaid CL working connection 43, and it is connected with reducing valve 42 via with the oil circuit OL that CL working connection 43 is set up in parallel.Oil circuit OL is connected to ratio reducing valve 42 downstream in CL working connection 43 and leans on the part of upstream side than the 3rd electromagnetic valve SV3.In addition, backup valve BV is connected with LU transfer valve 35 and DR pressure regulating valve 52 via oil circuit.

When the 3rd electromagnetic valve SV3 et out of order, the hydraulic pressure from reducing valve 42 is supplied to standby valve BV under the state being adjusted to higher pressure by aforesaid 4th electromagnetic valve SV4.Thus, by driving standby valve BV, in the following manner the hydraulic pressure being fed to standby valve BV via above-mentioned oil circuit OL from reducing valve 42 is fed to various key element.That is, the part being fed to the hydraulic pressure of standby valve BV is fed to FWD grease chamber 12a or RVS grease chamber 13a via the part of the ratio standby valve BV downstream of CL working connection 43 and hand valve 44, makes forward clutch 12 or reverse brake 13 engage thus.In addition, the part be supplied in the remainder of the hydraulic pressure of standby valve BV is supplied to LU transfer valve 35, and this remainder is supplied to DR grease chamber 22c via DR pressure regulating valve 52.Thus, LU power-transfer clutch 4c is controlled in release position, and the effective diameter of fixed drive belt wheel 22.

In addition, from explanation so far, the 4th electromagnetic valve SV4 is also used as the driving electromagnetic valve of DR pressure regulating valve 52 and standby valve BV, therefore, when the 3rd electromagnetic valve SV3 is normal, the hydraulic pressure from the 4th electromagnetic valve SV4 is supplied to DR pressure regulating valve 52 and these both sides of standby valve BV.Standby valve BV is provided with pull back spring (not shown), utilize the application force of this pull back spring, when making standby valve BV abnormal by the 3rd electromagnetic valve SV3 the lower hydraulic-driven of supplying, and only by during the 3rd electromagnetic valve SV3 fault the higher hydraulic-driven of supplying.Thus, when the 3rd electromagnetic valve SV3 is normal, action during above-mentioned fault can not be carried out.

In addition, in hydraulic pressure feeding mechanism, pressure accumulater 61 is provided with.As shown in Figure 4, pressure accumulater 61 has looped pipeline road 62, main accumulator 63, shutoff valve 64 and auxiliary accumulator 65.One end on looped pipeline road 62 is connected to ratio reducing valve 42 downstream in above-mentioned CL working connection 43 and leans on the part of upstream side than the connecting bridge with oil circuit OL, and the other end is connected with main accumulator 63.

Main accumulator 63 has cylinder body 63a, is slidably arranged on piston 63b in cylinder body 63a and the spring 63c that is made up of compression ring spring.Between cylinder body 63a and piston 63b, delimit out pressure accumulating chamber 63d, piston 63b is exerted a force to pressure accumulating chamber 63d side by spring 63c.Above-mentioned looped pipeline road 62 is communicated with pressure accumulating chamber 63d.As mentioned above, pressure accumulating chamber 63d supplies object with above-mentioned hydraulic pressure such as forward clutch 12 grade and Hydraulic Pump 31 is communicated with.The application force (spring constant) of spring 63c is set to: make savings be such as 0.3 ~ 0.5MPa at the hydraulic pressure of pressure accumulating chamber 63d.

Shutoff valve 64 is made up of the electromagnetic valve of the valve opening pattern that can optionally control as being forced open and the boiler check valve pattern played a role as boiler check valve, and it is arranged on the midway on looped pipeline road 62.Specifically, shutoff valve 64 is formed by with lower part: valve body 64a, and it can move between the valve closing position shown in the valve opening position shown in Fig. 4 and aftermentioned Fig. 6; Retracing spring 64b, it exerts a force in the mode making valve body 64a and remain on valve closing position; And for driving the electromagnetic valve 64c etc. of valve body 64a.Electromagnetic valve 64c has plunger 64d, and is connected with ECU2 (with reference to Fig. 3).When controlling shutoff valve 64 with valve opening pattern, from ECU2 to electromagnetic valve 64c input drive signal ASO.Under this valve opening pattern, plunger 64d resists the application force of retracing spring 64b and pushes valve body 64a, and thus, valve body 64a is maintained at valve opening position.That is, under valve opening pattern, shutoff valve 64 is forced to keep valve opening state.

On the other hand, when controlling shutoff valve 64 with boiler check valve pattern, stop from ECU2 to electromagnetic valve 64c input drive signal ASO.Under boiler check valve pattern, make plunger 64d keep the state left from valve body 64a, thus, shutoff valve 64 is played a role as boiler check valve.In addition, under boiler check valve pattern, ratio shutoff valve in looped pipeline road 62 64 by the hydraulic pressure of the part of main accumulator 63 side lower than during than the hydraulic pressure of shutoff valve 64 by the part of CL working connection 43 side, due to the effect of this hydraulic pressure, valve body 64a resists the application force of retracing spring 64b and is automatically moved to valve opening position, thus, working oil is allowed to flow into the part of main accumulator 63 side from the part of CL working connection 43 side.

In addition, under boiler check valve pattern, contrary to the above, ratio shutoff valve in looped pipeline road 62 64 by the hydraulic pressure of the part of main accumulator 63 side higher than during than the hydraulic pressure of shutoff valve 64 by the part of CL working connection 43 side, due to the effect of this hydraulic pressure and the force of retracing spring 64b, valve body 64a is automatically moved to valve closing position, thus, stops working oil to flow into the part of CL working connection 43 side from the part of main accumulator 63 side.

Auxiliary accumulator 65 is accumulators more small-sized than main accumulator 63, has cylinder body 65a, is slidably arranged on the piston 65b in cylinder body 65a and the spring 65c that is made up of compression ring spring.Pressure accumulating chamber 65d and room, back side 65e is divided into by piston 65b in cylinder body 65a.In addition, in the part of the 65e side, room, the back side of piston 65b, be formed with recess 65f, the space of the inner side of this recess 65f forms a part of above-mentioned back side room 65e.Spring 65c is arranged in the 65e of room, the back side, and its part is incorporated in recess 65f.Piston 65b is exerted a force to pressure accumulating chamber 65d side via aftermentioned valve body 65h by spring 65c.For the application force (spring constant) of spring 65c setting as described later.In addition, the maxim of the amount of contraction of spring 65c is greater than the stroke of piston 65b.

In addition, in the part of the pressure accumulating chamber 65d side of piston 65b, being formed with cross section is circular intercommunicating pore 65g, and pressure accumulating chamber 65d and room, back side 65e is communicated with each other.In addition, between piston 65b and spring 65c, the valve body 65h for making intercommunicating pore 65g carry out opening and closing is provided with.Valve body 65h is formed as spherical, has the diameter larger than intercommunicating pore 65g, and is incorporated in recess 65f.Valve body 65h, intercommunicating pore 65g and spring 65c are set to same heart shaped.

In addition, valve body 65h can move between the release position shown in the detent position shown in Fig. 4 and aftermentioned Fig. 7, is exerted a force to keep the mode of detent position by spring 65c.When valve body 65h is positioned at detent position, valve body 65h abuts with the edge of the 65e side, room, the back side of intercommunicating pore 65g, intercommunicating pore 65g is made to close thus, on the other hand, when valve body 65h is positioned at release position, valve body 65h leaves from the edge of the 65e side, room, the back side of intercommunicating pore 65g, makes intercommunicating pore 65g open thus.In the edge of the 65e side, room, the back side of intercommunicating pore 65g, be concentrically provided with the valve seat (not shown) of the ring-type be made up of elastic body.

In addition, auxiliary accumulator 65 is to make the mode of shutoff valve 64 bypass be connected with looped pipeline road 62 via the 1st oil circuit 66 and the 2nd oil circuit 67.Thus, room, the back side 65e of auxiliary accumulator 65 is communicated with looped pipeline road 62 via the 1st oil circuit 66, and pressure accumulating chamber 65d is communicated with looped pipeline road 62 via the 2nd oil circuit 67.As mentioned above, pressure accumulating chamber 65d, via shutoff valve 64, supplies object (forward clutch 12 etc.) with hydraulic pressure and Hydraulic Pump 31 is communicated with, and room, back side 65e does not supply object via shutoff valve 64 with hydraulic pressure and Hydraulic Pump 31 is communicated with.Therefore, in Hydraulic Pump 31 operates, from the hydraulic pressure of CL working connection 43 via looped pipeline road 62 and the 1st oil circuit 66, act on the end face of the 65e side, room, the back side of piston 65b as back pressure.In addition, pressure accumulating chamber 65d not via shutoff valve 64, but is communicated with the pressure accumulating chamber 63d of main accumulator 63 via the 2nd oil circuit 67 and looped pipeline road 62.

In addition, pressure accumulating chamber 65d can be made to be communicated with the pressure accumulating chamber 63d of the 1st accumulator 63 via the 2nd oil circuit 67 and looped pipeline road 62, but also can be only communicated with pressure accumulating chamber 63d via the 2nd oil circuit 67.In addition, room, back side 65e can be made to be communicated with CL working connection 43 via the 1st oil circuit 66 and looped pipeline road 62, but also can only be communicated with CL working connection 43 via the 1st oil circuit 66.

In addition, as shown in Figure 3, the detection signal of rotating speed (hereinafter referred to as " the engine speed ") NE representing driving engine 3 is exported from engine speed sensor 72 to ECU2.In addition, the operational ton exporting the Das Gaspedal (not shown) representing vehicle from accelerator open degree sensor 73 to ECU2 is (following, be called " accelerator open degree ") detection signal of AP, the detection signal of the vehicle velocity V P representing vehicle is exported from car speed sensor 74 to ECU2.

In addition, the ignition lock (hereinafter referred to as " IG/SW ") 75 of ECU2 and vehicle and brake switch (hereinafter referred to as " BR/SW ") 76 are connected.IG/SW75 is turned on/off because of the operation of the ignition key (not shown) of driver, and this on/off signal is outputted to ECU2.In this case, in driving engine 3 stops, when connecting IG/SW75, starter (not shown) carries out action etc. therefrom, thus fire an engine 3.In addition, in driving engine 3 operates, when closing IG/SW75, driving engine 3 stops therefrom (manually stopping).In addition, BR/SW76, when the brake pedal (not shown) of vehicle is operated, exports connection signal to ECU2, when not being operated, exports cut-off signal to ECU2.

ECU2 is made up of microcomputer, and this microcomputer is made up of I/O interface, CPU, RAM and ROM etc.CPU is according to from the detection signal of above-mentioned various sensor 71 ~ 74 and the on/off signal from IG/SW75 and BR/SW76, according to the control program stored in ROM, the action of driving engine 3, the 1st electromagnetic valve SV1 ~ the 5th electromagnetic valve SV5 and shutoff valve 64 is controlled.In addition, in ECU2, be provided with the power supply 2a of its electric power supply, its on/off is controlled by CPU.As mentioned above, power supply 2a as ECU2 and above-mentioned hydraulic pressure transducer 71 power supply and shared.

Next, with reference to Fig. 5, the process performed by CPU is described.Fig. 5 shows the process of the action for controlling the various valves such as above-mentioned shutoff valve 64, and the control cycle (such as, 100msec) of present treatment as prescribed is performed repeatedly.First, in the step 1 (being illustrated as " S1 ", identical below) of Fig. 5, differentiate whether output connection signal from IG/SW75.When its answer is "Yes" and exports connection signal from IG/SW75, differentiate whether idle stop flag F_IDLESTP is " 1 " (step 2).

With " 1 ", this idle stop flag F_IDLESTP represents that driving engine 3 is in stopping automatically, such as, when multiple stop conditions of the regulation comprising following defined terms A ~ D are all set up, perform the automatic stopping of driving engine 3.The automatic stopping of driving engine 3 is by stopping performing the fuel supply etc. of driving engine 3.

A: export connection signal from IG/SW75;

B: the vehicle velocity V P detected is below specified value VPREF;

C: the accelerator open degree AP detected is below specified value APREF;

D: export connection signal from BR/SW76.

In addition, in the automatic stopping of driving engine 3, such as, when multiple at least 1 of resetting in condition of the regulation comprising following defined terms E and F set up, driving engine 3 is automatically made to reset.Resetting of driving engine 3 is by controlling to perform the fuel supply etc. of starter and driving engine 3.

E: accelerator open degree AP has exceeded specified value APREF because stepping on the throttle pedal;

F: trampling of brake off pedal, exports cut-off signal from BR/SW76.

When the answer of described step 2 is "No" (F_IDLESTP=0), time namely in the automatic stopping not being in driving engine 3, differentiate whether the previous value F_IDLESTPZ of idle stop flag is " 1 " (step 3).When this answer is "No" (F_IDLESTPZ=0), namely, during driving engine 3 in running condition, in order to control the various valves such as shutoff valve 64 according to during running by master mode, in step 4, be set as during running " 1 " with control mark F_OPECO, and, all being set as " 0 " with controlling mark F_MSTCO with control mark F_ASTCO and when manually stopping with when control mark F_RESCO, automatically stopping when resetting, terminating present treatment.

When this running under master mode, according to operative condition, the vehicle velocity V P and accelerator open degree AP of the driving engines 3 such as the engine speed NE detected, control the aperture of the 1st electromagnetic valve SV1 ~ the 5th electromagnetic valve SV5, thus LU power-transfer clutch 4c, forward clutch 12, toric transmission 6 etc. are controlled.In addition, also control the aperture of the 5th electromagnetic valve SV5 according to the detection PU hydraulic pressure POD detected, thus, the effective diameter of driven pulley 23 and side pressure (driven pulley 23 clamps the pressure of transfer tape 24) are controlled.In addition, stop inputting above-mentioned drive singal ASO to shutoff valve 64, thus, control shutoff valve 64 with boiler check valve pattern as described above, thus make it play a role as boiler check valve.

On the other hand, the answer of described step 2 be "Yes" (F_IDLESTP=1) be in the automatic stopping of driving engine 3 time, in order to control various valve according to when automatically stopping by master mode, in steps of 5, be set as when automatically stopping " 1 " with control mark F_ASTCO, further, by during running with control mark F_OPECO, reset time with when controlling mark F_RESCO and manually stop with controlling to indicate that F_MSTCO is all set as " 0 ", end present treatment.When this stops automatically under master mode, the 1st electromagnetic valve SV1 ~ the 5th electromagnetic valve SV5 is controlled as driving engine 3 is by state when automatically stopping.In addition, the stop solution press pump 31 along with the automatic stopping of driving engine 3, thus, stops the hydraulic pressure supply to above-mentioned FWD grease chamber 12a and 22c Deng Ge grease chamber of DR grease chamber.In addition, identically with the situation of master mode during above-mentioned running, by stopping the input to the drive singal ASO of shutoff valve 64, thus, shutoff valve 64 is controlled with boiler check valve pattern.

In addition, in the automatic stopping of driving engine 3, the working oil in the key element beyond the pressure accumulater 61 of hydraulic pressure feeding mechanism, i.e. 1LU grease chamber 4d and 4e, FWD grease chamber of 2LU grease chamber 13a, DR grease chamber of 12a, RVS grease chamber 22c, DN grease chamber 23c, LU hydraulic tubing LUL, clutch hydraulic pressure pipeline CLL and belt wheel hydraulic tubing PUL is discharged (discharge) in oil reservoir R via exhaust tube (not shown).

On the other hand, when the answer of described step 3 is "Yes" (F_IDLESTPZ=1), namely when resetting from the automatic stop condition of driving engine 3, in order to control various valve according to when resetting by master mode, in step 6, be set as " 1 " with control mark F_RESCO when will reset, and be all set as during running " 0 " with control mark F_ASTCO and when manually stopping with controlling mark F_MSTCO with when control mark F_OPECO, automatically stopping, terminate present treatment.When this is reset under master mode, identically with the situation of master mode during running, according to the operative condition etc. of driving engine 3, control the aperture of the 1st electromagnetic valve SV1 ~ the 5th electromagnetic valve SV5.In addition, by shutoff valve 64 input drive signal ASO, control shutoff valve 64 with above-mentioned valve opening pattern, thus, keep valve opening state forcibly.In addition, when resetting in master mode, starting from it, according to engine speed NE, continue to carry out this judgement, until the hydraulic pressure determining Hydraulic Pump 31 fully rises.

On the other hand, time when the answer of described step 1 is "No" and exports cut-off signal from IG/SW75, the manual stopping being in driving engine 3, differentiate whether engine speed NE is 0 value (step 7).When engine speed NE is greater than 0 value this answer is "No", directly terminate present treatment.

On the other hand, when the answer of above-mentioned steps 7 is "Yes", engine speed NE is 0 value, be judged to be: in the manual stopping of driving engine 3, the Hydraulic Pump 31 being propulsion source with driving engine 3 stops.In addition, in order to control various valve according to when manually stopping by master mode, in step 8, be set as when manually stopping " 1 " with control mark F_MSTCO, and, with controlling mark F_OPECO when operating, being all set as " 0 " with control mark F_ASTCO with control mark F_RESCO and when automatically stopping when resetting, terminating present treatment.

When this manually stops under master mode, control the 1st electromagnetic valve SV1 and the 4th electromagnetic valve SV4 respectively, the 3rd electromagnetic valve SV3 is made to be controlled as full-shut position, and LU control cock 34 and DR pressure regulating valve 52 are full-shut position, and, control the 5th electromagnetic valve SV5, make DN pressure regulating valve 53 for full-gear.In addition, identical by master mode with when resetting, by shutoff valve 64 input drive signal ASO, thus, with valve opening Schema control shutoff valve 64, make it keep valve opening state.

In addition, in the manual stopping of driving engine 3, identically with the situation in the automatic stopping of driving engine 3, the working oil in the key element beyond the pressure accumulater 61 of hydraulic pressure feeding mechanism is made to discharge (discharge) in oil reservoir R.In addition, when manually stopping by master mode from it starts, last till till have passed through specified time, therebetween, make power supply 2a keep on-state, terminate by master mode along with when manually stopping, power supply 2a is controlled to be off state.

In addition, as mentioned above, from closedown IG/SW75, wait for that engine speed NE becomes 0 value (answer of waiting step 7 becomes "Yes"), master mode when starting manually to stop, but also can omit step 7, the master mode when the IG/SW75 pent moment starts manually to stop.In this case, when manually stopping by master mode from it starts, last till that engine speed NE becomes 0 value till, till namely lasting till that Hydraulic Pump 31 stops completely.

Next, with reference to Fig. 4, Fig. 6 ~ Fig. 8, (Fig. 4) during driving engine 3 is operated, automatically stop in (Fig. 6, Fig. 7) and when resetting from automatic stop condition the action of the pressure accumulater 61 of (Fig. 8) be described successively.

[in driving engine 3 running]

Illustrated by with reference to Fig. 5, during in driving engine 3 operates, (step 1 of Fig. 5: be, step 2: no), i.e. Hydraulic Pump 31 operate, perform when operating with master mode (step 4).Use in the running in the execution of master mode, with boiler check valve Schema control shutoff valve 64, thus, shutoff valve 64 plays a role as only allowing working oil to become owner of the boiler check valve of accumulator 63 side from CL working connection 43 effluent.In this case, because hydraulic pressure from Hydraulic Pump 31 to CL working connection 43 that supply from is higher than the hydraulic pressure of main accumulator 63, therefore, shutoff valve 64 is automatic valve opening because of the effect of this hydraulic pressure, thus, main accumulator 63 is communicated with between CL working connection 43.

Thus, as shown in Figure 4, be supplied to the pressure accumulating chamber 63d of main accumulator 63 via looped pipeline road 62 from the hydraulic pressure of CL working connection 43, thus pushing piston 63b, thus, piston 63b resists the application force of spring 63c, moves (in the diagram, illustrating with hollow arrow) towards the side contrary with pressure accumulating chamber 63d.Consequently, in main accumulator 63, hydraulic pressure is accumulated.

In addition, from the hydraulic pressure of CL working connection 43 via looped pipeline road 62 and the 1st oil circuit 66, the end face of the 65e side, room, the back side of auxiliary accumulator 65 is acted on as back pressure.The application force of spring 65c is set to: in Hydraulic Pump 31 operates, and the application force of spring 65c and above-mentioned back pressure sum are greater than the hydraulic pressure within the loop comprising looped pipeline road 62, main accumulator 63 and the 2nd oil circuit 67.Thus, as shown in Figure 4, in the running of Hydraulic Pump 31, the end face of the pressure accumulating chamber 65d side of piston 65b is made to keep the state abutted with the inwall of cylinder body 65a, further, valve body 64a is made to keep its valve opening position, therefore, the hydraulic pressure from Hydraulic Pump 31 can be made to accumulate hardly in auxiliary accumulator 65, and suitably accumulate in main accumulator 63.

[in the automatic stopping of driving engine 3]

In driving engine 3 stops automatically (step 1 of Fig. 5: be, step 2: yes), perform when automatically stopping with master mode (step 5).When automatically stopping master mode execution in, in time operating master mode situation in the same manner as, with boiler check valve Schema control shutoff valve 64, make it play a role as boiler check valve.In this case, along with driving engine 3 stops automatically, stop the hydraulic pressure supply from Hydraulic Pump 31 pairs of CL working connections 43, and the working oil in CL working connection 43 is discharged from oil reservoir R as described above, therefore, ratio shutoff valve 64 in looped pipeline road 62 leans on the hydraulic pressure of the part of main accumulator 63 side higher than the hydraulic pressure leaning on the part of CL working connection 43 side than shutoff valve 64, and therefore, shutoff valve 64 is valve closing automatically.Thus, as shown in Figure 6, owing to being cut off between CL working connection 43 and main accumulator 63, therefore, the hydraulic pressure be accumulated in so far in main accumulator 63 is kept.In addition, due to the valve closing of shutoff valve 64, the closed-loop comprising looped pipeline road 62, main accumulator 63 and the 2nd oil circuit 67 is defined.

In addition, when stopped Hydraulic Pump 31, no longer effect has the back pressure from CL working connection 43 thereupon, and room, back side 65e is not communicated with Hydraulic Pump 31 via shutoff valve 64, therefore, the application force of spring 65c is only had to act on as the thrust pressure of the piston 65b towards the auxiliary accumulator 65 of pressure accumulating chamber 65d thruster pressure.In addition, pressure accumulating chamber 65d not via shutoff valve 64, but is communicated with the pressure accumulating chamber 63d of main accumulator 63 via the 2nd oil circuit 67 and looped pipeline road 62.Thus, along with the stopping of Hydraulic Pump 31, the piston 65b of auxiliary accumulator 65 is accumulated in the hydraulic pressure be cut off in the closed closed-loop of valve 64 and pushes, thus moves (in figure 6, illustrating with hollow arrow) towards 65e side, room, the back side.Thus, a part for the hydraulic pressure (working oil) in closed-loop is supplied to the pressure accumulating chamber 65d of auxiliary accumulator 65, and is accumulated in wherein.Therefore, it is possible to make the hydraulic pressure in closed-loop reduce fall its redundance.

In addition, in figure 6, for the hydraulic pressure in the closed-loop of main accumulator 63 grade be less than set upper limit value (such as, 2.54MPa) situation and show driving engine 3 automatically stop in pressure accumulater 61 etc.In this case, as shown in Figure 6, the valve body 65h of auxiliary accumulator 65 is maintained at detent position due to the force of spring 65c, and thus, the intercommunicating pore 65g of piston 65b is closed by valve body 65h.

On the other hand, in the figure 7, for the hydraulic pressure in closed-loop reach above-mentioned higher limit situation and show driving engine 3 automatically stop in pressure accumulater 61 etc.As shown in the drawing, the end face of the 65e side, room, the back side of piston 65b abuts with the inwall of cylinder body 65a, can not move towards 65e side, room, the back side further and hydraulic pressure in closed-loop to act on towards the mode of room, back side 65e thruster pressure valve body 65h, therefore, valve body 65h resists the application force of spring 65c, move to release position (in the figure 7, illustrating with hollow arrow) from detent position.Thus, make intercommunicating pore 65g open, thus pressure accumulating chamber 65d and room, back side 65e is communicated with each other via intercommunicating pore 65g, thus, the excess electron excess fraction of the hydraulic pressure in closed-loop is discharged in the 1st oil circuit 66 and looped pipeline road 62, CL working connection 43 etc. via room, back side 65e.Therefore, it is possible to prevent excessiveization of the hydraulic pressure in closed-loop, and then, the breakage of main accumulator 63, auxiliary accumulator 65, looped pipeline road 62, the 2nd oil circuit 67 and shutoff valve 64 can be avoided.The application force of spring 65c is set to obtain above-mentioned effect/effect.

[when driving engine 3 is reset from automatic stop condition]

When driving engine 3 is reset from automatic stop condition (step 1 of Fig. 5: be, step 2: no, step 3: yes), perform when resetting with master mode (step 6).When resetting master mode execution in, with valve opening Schema control shutoff valve 64, make it keep valve opening state, thus, main accumulator 63 be communicated with between CL working connection 43.Thus, as shown in Figure 8, the piston 63b of main accumulator 63 moves to pressure accumulating chamber 63d side (in the figure, illustrating with hollow arrow) because of the application force of spring 63c.Thus, be accumulated in hydraulic pressure in the closed-loop of above-mentioned main accumulator 63 grade via looped pipeline road 62 and CL working connection 43, be supplied to FWD grease chamber 12a, and further via branch's oil circuit 41 and PU working connection 51, be supplied to DR grease chamber 22c and DN grease chamber 23c.Further, when the hydraulic pressure of Hydraulic Pump 31 fully raises, except from except the hydraulic pressure of closed-loop, the hydraulic pressure from Hydraulic Pump 31 is also supplied to DR grease chamber 22c, DN grease chamber 23c and FWD grease chamber 12a.Therefore, according to the present embodiment, when driving engine 3 is reset from automatic stop condition, can rapidly and fully to toric transmission 6 and forward clutch 12 sap pressure supply.

In addition, Fig. 8 shows the state reset after running that accompany, that again start Hydraulic Pump 31 with driving engine 3, in this condition, the hydraulic pressure of Hydraulic Pump 31 does not also fully rise, hydraulic pressure in closed-loop is higher, therefore, as shown in the drawing, lean in the part of Hydraulic Pump 31 side at the connecting portion than looped pipeline road 62 of CL working connection 43, working oil flows to Hydraulic Pump 31 side.

In addition, along with opening of above-mentioned shutoff valve 64, the thrust pressure be made up of these both sides of application force of back pressure and spring 65c is used as the piston 65b of auxiliary accumulator 65 to act on to the thrust pressure of pressure accumulating chamber 65d thruster pressure again.Thus, piston 65b is made to move (in fig. 8 to pressure accumulating chamber 65d side, illustrate with hollow arrow), thus, savings so far is supplied to DR grease chamber 22c, DN grease chamber 23c and FWD grease chamber 12a via the 2nd oil circuit 67, looped pipeline road 62 and PU working connection 51 at the hydraulic pressure (working oil) of auxiliary accumulator 65 together with carrying out the hydraulic pressure of autonomous accumulator 63.Therefore, according to the present embodiment, when again starting the running of oil pump 31, can without lavishly the hydraulic pressure (working oil) of savings in auxiliary accumulator 65 when it stops being fed to toric transmission 6 and forward clutch 12.

In addition, Fig. 9 shows driving engine 3 from running, performs the action case automatically stopping, performing in this stops automatically hydraulic pressure feeding mechanism when resetting.In fig .9, represent to shutoff valve 64 input drive signal ASO with " 1 " respectively, represent not to shutoff valve 64 input drive signal ASO with " 0 ".In addition, in the figure, PAC is the hydraulic pressure (hereinafter referred to as " main accumulator hydraulic pressure ") of accumulation in main accumulator 63, and PFWD is the hydraulic pressure (hereinafter referred to as " FWD hydraulic pressure ") in FWD grease chamber 12a.

As shown in Figure 9, driving engine 3 operate in and vehicle velocity V P is greater than described specified value VPREF, above-mentioned stop condition is false time (before moment t0 ~ t1, the step 1 of Fig. 5: be, step 2,3: no), be set as during running " 1 " with control mark F_OPECO respectively, be set as " 0 " that (step 4) performs master mode when operating with when control mark F_RESCO and automatic stopping with control mark F_ASTCO when will reset.

Use in the running in the execution of master mode, not to shutoff valve 64 input drive signal ASO, therefore, control shutoff valve 64 with boiler check valve pattern.Thus, allow working oil to flow into main accumulator 63 from CL working connection 43, stop working oil to flow out to CL working connection 43 from main accumulator 63, therefore, main accumulator hydraulic pressure PAC changes with roughly fixing state.In addition, in this action case, owing to being in the Reduced Speed Now of vehicle, thus less to the degree of engagement of forward clutch 12 requirement, therefore, FWD hydraulic pressure PFWD is lower than main accumulator hydraulic pressure PAC.

And then when vehicle velocity V P becomes 0 value, stop condition establishment (moment t1), driving engine 3 stops automatically, and engine speed NE sharply drops to 0 value thereupon.In addition, Hydraulic Pump 31 is drive source with driving engine 3 and hydraulic pressure from Hydraulic Pump 31 is supplied to FWD grease chamber 12a, and therefore, FWD hydraulic pressure PFWD sharply drops to 0 value along with the decline of engine speed NE.

In addition, along with the establishment (step 1,2 of Fig. 5: yes) of stop condition, be set as when automatically stopping " 1 " with control mark F_ASTCO respectively, be set as during running " 0 " (step 5) with control mark F_RESCO with control mark F_OPECO and when resetting, perform master mode when automatically stopping.When automatically stopping master mode execution in, identically with the situation of master mode during running, not to shutoff valve 64 input drive signal ASO, control shutoff valve 64 with boiler check valve pattern.In addition, as used as described in Fig. 6, due to the automatic valve closing of shutoff valve 64, therefore, define the closed-loop comprising main accumulator 63, and a part for hydraulic pressure in closed-loop is supplied to auxiliary accumulator 65, and is accumulated in wherein.Thus, main accumulator hydraulic pressure PAC, after its redundance is fallen in minimizing, changes with fixing state.

And then making because of pedal of stepping on the throttle etc. above-mentionedly to reset (moment t2) when condition is set up, driving engine 3 is reset, and engine speed NE rises, and vehicle velocity V P rises gradually thereupon.In addition, why engine speed NE is not rise at once after condition of resetting is set up, and is the operating lag due to starter.

In addition, along with the establishment (step 1 of Fig. 5: be resetting condition, step 2: no, step 3: yes), be set as " 1 " with control mark F_RESCO when will reset respectively, be set as " 0 " that (step 6) perform when resetting master mode with control mark F_OPECO and when automatically stopping with control mark F_ASTCO by during running.When resetting master mode execution in, to shutoff valve 64 input drive signal ASO, thus, with valve opening Schema control shutoff valve 64, force make it keep valve opening state.Thus, as used as described in Fig. 8, the hydraulic pressure be accumulated in main closed-loop such as accumulator 63 grade is supplied to FWD grease chamber 12a etc., and therefore, main accumulator hydraulic pressure PAC sharply declines, and FWD hydraulic pressure PFWD sharply rises.

In fig .9, PUP represents the rising part because of the FWD hydraulic pressure PFWD risen to the hydraulic pressure supply of FWD grease chamber 12a from closed-loop.In this case, the accumulator hydraulic pressure PAC during beginning of this rising part PUP lower than master mode when resetting, therefore, the hydraulic pressure in closed-loop not all is supplied to FWD grease chamber 12a, but be also supplied to DR grease chamber 22c etc.

In addition, when resetting master mode execution in, engine speed NE rises because of the starting of driving engine 3, and the decline degree of main accumulator hydraulic pressure PAC diminishes thereupon, and FWD hydraulic pressure PFWD rises gradually.And then when driving engine 3 carries out incipient detonation, the hydraulic pressure from Hydraulic Pump 31 is supplied to main accumulator 63 and FWD grease chamber 12a, therefore, main accumulator hydraulic pressure PAC and these both sides of FWD hydraulic pressure PFWD rise.In this case, during owing to being in vehicle start, thus comparatively large to the degree of engagement of forward clutch 12 requirement, therefore, FWD hydraulic pressure PFWD rises with the size roughly the same with main accumulator hydraulic pressure PAC.

And then, as mentioned above, start reset time master mode after, when being judged to be that the hydraulic pressure of Hydraulic Pump 31 fully rises according to engine speed NE (moment t3), terminate master mode when resetting., be set as during running " 1 " with control mark F_OPECO respectively thereupon, with controlling mark F_ASTCO and being set as " 0 " with control mark F_RESCO when resetting when automatically stopping, master mode when operating will be performed.Thus, due to no longer to shutoff valve 64 input drive signal ASO, thus shutoff valve 64 is controlled with boiler check valve pattern.

In addition, the corresponding relation between the various key element of present embodiment and various key element of the present invention is as follows.Namely, LU power-transfer clutch 4c, forward clutch 12, reverse brake 13 and toric transmission 6 in present embodiment are equivalent to the hydraulic pressure supply object in the present invention, auxiliary accumulator 65 in present embodiment and pressure accumulating chamber 65d are equivalent to the 1st accumulator in the present invention and the 1st pressure accumulating chamber, further, the spring 65c in present embodiment is equivalent to the 1st forcing unit, the 2nd forcing unit and force application part in the present invention.In addition, the driving engine 3 in present embodiment is equivalent to the propulsion source of the vehicle in the present invention, and main accumulator 63 in present embodiment and pressure accumulating chamber 63d are equivalent to the 2nd accumulator in the present invention and the 2nd pressure accumulating chamber.

As mentioned above, according to the present embodiment, the pressure accumulating chamber 63d of main accumulator 63 supplies object with hydraulic pressure such as the Hydraulic Pump 31 being drive source with driving engine 3 and FWD grease chamber 12a and is communicated with, and can accumulate the hydraulic pressure from Hydraulic Pump 31.In addition, by shutoff valve 64, hydraulic pressure is made to supply object and be communicated with/end between Hydraulic Pump 31 with pressure accumulating chamber 63d.As with reference to Fig. 4 illustrates, by the connection of this shutoff valve 64, can future self-hydraulic pump 31 hydraulic pressure be accumulated in pressure accumulating chamber 63d.In addition, as illustrated with reference to Fig. 6, by the cut-off of shutoff valve 64, pressure accumulating chamber 63d can be closed, thus the hydraulic pressure accumulated in maintenance pressure accumulating chamber 63d.In addition, as illustrated with reference to Fig. 8, by the connection of shutoff valve 64, the hydraulic pressure accumulated can be fed to hydraulic pressure supply object in pressure accumulating chamber 63d.

In addition, the pressure accumulating chamber 65d of auxiliary accumulator 65 supplies object via shutoff valve 64 with hydraulic pressure and Hydraulic Pump 31 is communicated with, therefore, by the cut-off of above-mentioned shutoff valve 64, except can closing the pressure accumulating chamber 63d of main accumulator 63, pressure accumulating chamber 65d can also be closed, thereby, it is possible to keep the hydraulic pressure accumulated in Liang Ge pressure accumulating chamber 63d, 65d.In addition, pressure accumulating chamber 65d is not communicated with pressure accumulating chamber 63d via shutoff valve 64, therefore, as illustrated with reference to Fig. 7, can by the overflow mechanism be made up of intercommunicating pore 65g, valve body 65h and spring 65c, prevent excessiveization of the hydraulic pressure (working oil) in closed-loop that the cut-off being cut off valve 64 is closed, that comprise Liang Ge pressure accumulating chamber 63d, 65d, thereby, it is possible to avoid the 1st accumulator 63 and the 2nd accumulator 65 etc. damaged.

In addition, intercommunicating pore 65g, valve body 65h and spring 65c are not all arranged with auxiliary accumulator 65 dividually, but are arranged in the cylinder body 65a of auxiliary accumulator 65, therefore, it is possible to make the miniaturization of hydraulic pressure feeding mechanism.

In addition, shutoff valve 64 is configured to optionally to control as non-return valve mode and valve opening pattern, under boiler check valve pattern, when hydraulic pressure in pressure accumulating chamber 63d side supplies the hydraulic pressure of object and Hydraulic Pump 31 side lower than hydraulic pressure, hydraulic pressure is made to supply object and be communicated with between Hydraulic Pump 31 and pressure accumulating chamber 63d, when hydraulic pressure in pressure accumulating chamber 63d side supplies the hydraulic pressure of object and Hydraulic Pump 31 side higher than hydraulic pressure, hydraulic pressure is made to supply object and end between Hydraulic Pump 31 and pressure accumulating chamber 63d.Thereby, it is possible to effectively obtain above-mentioned effect, namely can accumulate in pressure accumulating chamber 63d and the effect that accumulated hydraulic pressure can be kept such the hydraulic pressure of in the future self-hydraulic pump 31.In addition, under boiler check valve pattern, there is no need for the special control action that the opening and closing of shutoff valve 64 is switched, therefore, it is possible to carry out the accumulation/maintenance of hydraulic pressure to pressure accumulating chamber 63d simply.

In addition, the 1st forcing unit in the present invention and the 2nd forcing unit are be made up of public single spring 65c each other, therefore, and can corresponding reduction number of components because of this part.In addition, valve body 65h is exerted a force towards detent position side by this spring 65c, and, piston 65b is exerted a force towards pressure accumulating chamber 65d side via valve body 65h, therefore, it is possible to suitably carry out the accumulation of valve body 65h towards the maintenance of detent position and the hydraulic pressure based on auxiliary accumulator 65.

In addition, by making valve body 65h abut with the edge of intercommunicating pore 65g, intercommunicating pore 65g is closed.In addition, valve body 65h is formed as spherical, therefore, it is possible to suppress, towards the one-sided abutting of the edge of intercommunicating pore 65g, can utilize valve body 65h suitably closed communication hole 65g.

In addition, room, back side 65e does not supply object via shutoff valve 64 with Hydraulic Pump 31 and hydraulic pressure and is communicated with, therefore, as illustrated with reference to Fig. 4, in Hydraulic Pump 31 operates, the hydraulic pressure from Hydraulic Pump 31 can be made to accumulate hardly in pressure accumulating chamber 65d, but suitably accumulate the pressure accumulating chamber 63d in main accumulator 63.In addition, as illustrated with reference to Fig. 6, in Hydraulic Pump 31 stops, the hydraulic pressure comprised in the closed-loop of main accumulator 63 can be made to reduce and to fall its redundance.Thereby, it is possible to adopt the lower small scaled stop valve of resistance to pressure to be used as shutoff valve 64, therefore, it is possible to realize the reduction of the manufacturing cost of hydraulic pressure feeding mechanism.In addition, as illustrated with reference to Fig. 8, when again starting the running of Hydraulic Pump 31, can without lavishly by the hydraulic pressure (working oil) be accumulated in stopping at Hydraulic Pump 31 in pressure accumulating chamber 65d with come autonomous accumulator 63 pressure accumulating chamber 63d hydraulic pressure together be fed to hydraulic pressure and supply object.

In addition, when again starting the running of Hydraulic Pump 31, the working oil accumulated in pressure accumulating chamber 65d can be discharged, therefore, when stop solution press pump 31 again, can suitably a part for the hydraulic pressure in closed-loop be accumulated in pressure accumulating chamber 65d.Therefore, even if when repeatedly carrying out the running/stopping of Hydraulic Pump 31, also above-mentioned effect can effectively be obtained.

In addition, object is supplied with hydraulic pressure and Hydraulic Pump 31 is communicated with due to room, back side 65e, therefore, the hydraulic pressure be discharged in the 65e of room, the back side by overflow mechanism (intercommunicating pore 65g/ valve body 65h/ spring 65c) can be made to be discharged into hydraulic pressure supply object and Hydraulic Pump 31 side further, thereby, it is possible to the effect effectively obtaining above-mentioned effect, namely the breakages such as main accumulator 63 and auxiliary accumulator 65 can be avoided such.

In addition, the present invention is not limited to illustrated embodiment, and can implement with various form.Such as, in embodiments, Hydraulic Pump 31 is gear type pump, but also can be gerotor pump, blade-type pump etc.In addition, in embodiments, form spring 65c with compression ring spring, and be arranged in the 65c of room, the back side, but, also can form spring 65c with extension spring, and be arranged in pressure accumulating chamber 65d.In addition, in embodiments, spring 65c is also used as the 1st forcing unit in the present invention and the 2nd forcing unit, but also two forcing unit can be set respectively.In this case, other the suitable forcing unit beyond spring can be used, such as formed the 1st forcing unit and the 2nd forcing unit with rubber etc.

In addition, in embodiments, make intercommunicating pore 65g be formed as cross section circle, but such as can be formed as other suitable shapes such as cross section rectangle.In addition, in embodiments, make valve body 65h be formed as spherical, but such as according to the shape of intercommunicating pore, other suitable shape such as coniform grade can be formed.In this case, valve body 65h can be made to be configured to so-called vane-type shutter, in this case, make valve body be formed as tabular, and be arranged at intercommunicating pore in a rotatable manner, to valve body force the 1st forcing unit is such as made up of torsion spring, it is arranged at intercommunicating pore.

In addition, in embodiments, main accumulator 63 and auxiliary accumulator 65 are connected with the CL working connection 43 of clutch hydraulic pressure pipeline CLL, but, also can be connected with the PU working connection 51 of other oil circuit such as belt wheel hydraulic tubing PUL.In addition, in embodiments, main accumulator 63 is piston type accumulator, but can be bellows accumulator etc.In addition, in embodiments, room, the back side 65e of auxiliary accumulator 65 can be made to supply object with hydraulic pressure and Hydraulic Pump 31 is communicated with, also can not be communicated with, in this case, auxiliary accumulator is different from the embodiment described above, but in the same manner as main accumulator 63, the accumulator as the accumulation of the hydraulic pressure from Hydraulic Pump uses.In addition, in this case, at least one party in main accumulator 63 and shutoff valve 64 can be omitted.In addition, the quantity of main accumulator 63 and auxiliary accumulator 65 can be multiple.

In addition, in embodiments, the electromagnetic valve that utilization can be carried out controlling under boiler check valve pattern and valve opening pattern is to form shutoff valve 64, but, also can by controlled respectively by excitation/non-excitation valve closing/valve opening (or valve opening/valve closing), common electromagnetic valve forms, or is made up of the valve of fluid pressure type.In addition, in embodiments, as the propulsion source of the vehicle in the present invention, employ as petrolic driving engine 3, but also can use diesel motor or LPG driving engine etc.

In addition, in embodiments, hydraulic pressure supply object in the present invention is LU power-transfer clutch 4c, toric transmission 6, forward clutch 12 and reverse brake 13, but, also can be other the suitable mechanism of the hydraulic pressure being supplied work, can be such as lift variable mechanism and cam phase variable mechanism etc., wherein, described lift variable mechanism can make the lift of at least one party in the air inlet valve of combustion engine and blow off valve change, described cam phase variable mechanism can change cam phase, described cam phase is the phase place of the bent axle relative at least one party driven respectively in the inlet cam of air inlet valve and blow off valve and exhaust cam.Or, can be the hydraulic pressure supply object used in boats and ships beyond vehicle and aerocraft etc.In addition, in the scope of purport of the present invention, suitably can change the structure of detail section.

Claims (6)

1. a hydraulic pressure feeding mechanism, is characterized in that, described hydraulic pressure feeding mechanism has:

Hydraulic Pump, it is for the hydraulic pressure to hydraulic pressure supply object supply work; And

1st accumulator, it supplies object with described hydraulic pressure and described Hydraulic Pump is connected, for accumulating hydraulic pressure,

1st accumulator has:

Cylinder body;

Piston, it is slidably arranged on this cylinder interior, described cylinder interior is divided into the 1st pressure accumulating chamber of room, the back side and accumulation hydraulic pressure;

1st forcing unit, it exerts a force towards described 1st pressure accumulating chamber side to this piston;

Intercommunicating pore, it is formed in described piston in the mode making described 1st pressure accumulating chamber and room, the described back side and communicate with each other;

Valve body, it is arranged on described cylinder interior, and can make to move between the open release position of this intercommunicating pore at the detent position making described intercommunicating pore close; And

2nd forcing unit, it is arranged on described cylinder interior, is configured to: exert a force in the mode making described valve body remain on described detent position, and, when hydraulic pressure in described 1st pressure accumulating chamber reaches set upper limit value, described valve body is allowed to move from described detent position to side, described release position.

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

Described Hydraulic Pump with the propulsion source of vehicle for drive source,

Described hydraulic pressure feeding mechanism also has:

2nd accumulator, it has the 2nd pressure accumulating chamber supplying object and described Hydraulic Pump with described hydraulic pressure and be communicated with, and the 2nd accumulator is used for the hydraulic pressure from described Hydraulic Pump to accumulate in described 2nd pressure accumulating chamber; And

Shutoff valve, consists of and described hydraulic pressure can be made to supply object and be communicated with/end between described Hydraulic Pump with described 2nd pressure accumulating chamber,

Described 1st pressure accumulating chamber of described 1st accumulator supplies object via described shutoff valve with described hydraulic pressure and described Hydraulic Pump is communicated with, and is communicated with described 2nd pressure accumulating chamber in the mode not via described shutoff valve.

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

Described shutoff valve is made up of electromagnetic valve, the valve opening pattern that this electromagnetic valve optionally can control the boiler check valve pattern for playing a role as boiler check valve and be forced open, under described boiler check valve pattern, when hydraulic pressure in described 2nd pressure accumulating chamber side supplies the hydraulic pressure of object and described hydraulic pressure pump side lower than described hydraulic pressure, described hydraulic pressure is made to supply object and be communicated with between described Hydraulic Pump with described 2nd pressure accumulating chamber, when hydraulic pressure in described 2nd pressure accumulating chamber side supplies the hydraulic pressure of object and described hydraulic pressure pump side higher than described hydraulic pressure, described hydraulic pressure is made to supply object and end between described Hydraulic Pump and described 2nd pressure accumulating chamber.

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

Described 1st forcing unit and described 2nd forcing unit are made up of public single force application part each other, and this force application part exerts a force towards described detent position side to described valve body, and exert a force to described piston towards described 1st pressure accumulating chamber side via described valve body.

5. hydraulic pressure feeding mechanism according to claim 4, is characterized in that,

Described valve body is formed as spherical, by abutting closed described intercommunicating pore with the edge of described intercommunicating pore.

6. the hydraulic pressure feeding mechanism according to any one in claim 2 ~ 5, is characterized in that,

The room, the described back side of described 1st accumulator is not to supply object via the mode of described shutoff valve with described hydraulic pressure and described Hydraulic Pump is communicated with.