CN103363103B

CN103363103B - The hydraulic pressure control device of automatic transmission

Info

Publication number: CN103363103B
Application number: CN201310091170.0A
Authority: CN
Inventors: 加藤芳章
Original assignee: JATCO Ltd
Current assignee: JATCO Ltd
Priority date: 2012-03-28
Filing date: 2013-03-21
Publication date: 2016-06-01
Anticipated expiration: 2033-03-21
Also published as: KR101468293B1; KR20130110028A; CN103363103A; JP2013204660A; JP5693507B2

Abstract

The present invention provides the control device of a kind of vehicle that starting performance reduces when suppressing engine to restart from idle stop, bidirectional electromagnetic valve and uses the oil gear of this bidirectional electromagnetic valve. In the bidirectional electromagnetic valve of the present invention, possess: carry out the plunger driven based on connection and the cut-out of electric current; Moved by the driving of described plunger and it separate and the valve body of switch oil circuit with valve seat; To the first elastomerics that described plunger is exerted a force by described valve body from the direction that described valve seat leaves; The 2nd elastomerics described valve body exerted a force to the direction that described valve body contacts with described valve seat, connecting with described electric current and make described valve body be landed on described valve seat, described electric current cuts off and makes described valve body set the reactive force of first and second elastomerics described from the mode that described valve seat leaves.

Description

The hydraulic pressure control device of automatic transmission

Technical field

The present invention relates to and according to the magnetic valve of the condition switch of regulation or maintenance, can especially relate to the technology of the control device of the vehicle of the idle stop control being suitable for carrying out when the condition specified is set up stopping the idling of engine.

Background technology

As the vehicle carrying out idle stop control, it is known that there is the technology that patent documentation 1 is recorded. In the art, possess and it is connected with start clutch to the oil circuit of start clutch supply line pressure and is provided with the oil circuit of pressure retaining valve, switches the switching valve of these oil circuits, if line pressure reduces, then utilize switching valve switching oil circuit, utilize pressure retaining valve to keep the oil pressure of start clutch. Thus, even if making engine stop and oil pressure can not be supplied from oil pump driven by the engine to start clutch by idle stop control, it is also possible to keep the oil pressure of start clutch. Thus, compared with the situation supplying oil pressure with electronic oil pump or store battery to start clutch, inhibit the increase of cost, and the deterioration of responsiveness when avoiding recurrence step.

Patent documentation 1:(Japan) JP 2007-270953 publication

But, when realizing above-mentioned action, it is necessary to arrange from oil pump to the oil circuit of start clutch fuel feeding and these two oil circuits of oil circuit possessing pressure retaining valve, need to arrange the switching valve of the connected state of these two oil circuits of switching in addition, therefore, there is the complicated such problem in oil pressure loop.

Summary of the invention

The present invention is conceived to the problems referred to above and proposes, and its object is to offer and can not cause the complicated of oil pressure loop, the valve opening when electric current cuts off, can remain the bidirectional electromagnetic valve of specified pressure when electric current is connected.

In order to realize above-mentioned purpose, the bidirectional electromagnetic valve of the present invention possesses: plunger, and it drives based on connection and the cut-out of electric current; Valve body, it is moved by the driving of described plunger, separate and switch oil circuit with valve seat; First elastomerics, described plunger is exerted a force from the direction that described valve seat leaves by it to described valve body; 2nd elastomerics, described valve body is exerted a force by its direction contacted with described valve seat to described valve body, connecting with described electric current and make described valve body be landed on described valve seat, described electric current cuts off and makes described valve body set the reactive force of first and second elastomerics described from the mode that described valve seat leaves.

Therefore, when electric current cuts off, the not inaccessible stream road of valve body, so oil pressure can be supplied from oil pressure source to pressure supply side. In addition, when electric current is connected, owing to valve body is by inaccessible for oil circuit and can keep the oil pressure of pressure supply side. Namely, it is not necessary to possess multiple oil circuit or switching valve etc., it is possible to realize the simplification in oil pressure loop.

Accompanying drawing explanation

Fig. 1 is the overall system view of the idling stop vehicle of the control device representing the vehicle applying embodiment 1;

Fig. 2 is the sectional view of the forward clutch of the automatic transmission for embodiment 1;

Fig. 3 is the path increment of clutch reset spring and the mutual relationship figure of load on spring of the forward clutch of embodiment 1;

Fig. 4 is the oil pressure loop figure in the oil pressure cntrol valve cell of embodiment 1;

Fig. 5 is the oil pressure loop figure of the forward clutch connection oil pressure of control embodiment 1;

Fig. 6 is the oil pressure loop figure of the forward clutch connection oil pressure of control embodiment 1;

Description of symbols

2d: forward clutch (start clutch)

3: buncher (CVT)

7: oil pump

8: oil pressure cntrol valve cell

22: manual valve

80: bidirectional electromagnetic valve

81: coil

82: return spring (the first elastomerics)

83: plunger

84: pin parts

85: valve body

86: plate member

86a: valve seat

87: circulation hole

88: spring (the 2nd elastomerics)

89a: suction port

89b: relief outlet

Embodiment

(embodiment 1)

�� outline of automatic transmission ��

Fig. 1 is the figure of the control system of the automobile-used automatic transmission of the FF of the bidirectional electromagnetic valve representing and applying the present invention and the oil gear possessing this bidirectional electromagnetic valve. Automatic transmission has: the torque converter 1 that amplified by the moment of torsion from the engine outside figure, the forward-reverse switching mechanism 2 of (forward clutch and retreat stopper) that has start clutch, below the buncher 3(that carries out stepless change between input and output are CVT3). In addition, as the mechanism to each unit feeding oil pressure and lubricating oil, there is oil pump 7 driven by the engine and oil pressure cntrol valve cell 8.

Forward-reverse switching mechanism 2 is made up of the sun and planet gear mechanism comprising ring gear 2a, planet carrier 2b and sun wheel 2c. Ring gear 2a is connected with torque converter output shaft 13. Sun wheel 2c is connected with CVT input shaft 14. The retrogressing stopper 2e being provided with on wheel box fixed carrier 2b on planet carrier 2b and the forward clutch 2d that CVT input shaft 14 and planet carrier 2b one are connected.

CVT3 has: the elementary movable pulley 30a of primary pulley 30(and elementary fixed pulley 30b being located at the end of CVT input shaft 14), secondary pulley 31(level movable pulley 31a and secondary fixed pulley 31b of being located on driven shaft 16), be wound around between the groove of each belt wheel 30,31 and transmit the band 15 of the revolving force of primary pulley 30 to secondary pulley 31.

The axial location (groove width of primary pulley 30) of elementary movable pulley 30a is specified by the oil pressure acting on primary pulley cylinder room 30c and elementary clamping room 30d. The axial location (groove width of secondary pulley 31) of secondary movable pulley 31a is specified by the oil pressure acting on secondary pulley cylinder room 31c and secondary clamping room 31d.

CVT control unit 9 is inputted the throttle opening TVO from throttle opening sensor 5a, the motor speed Ne from motor speed sensor 5b, the oil temperature T from oil temperature sensor 5c, the elementary rotating speed Npri from elementary tachogenerator 6a, the input signal such as secondary rotating speed Nsec from secondary tachogenerator 6b. CVT control unit 9 carries out computing based on these input signals, exports control signal to the oil pressure cntrol valve cell 8 using oil pump 7 driven by the engine as oil pressure source.

Input the control signal from CVT control unit 9 to oil pressure cntrol valve cell 8, drive the solenoid coil in oil pressure cntrol valve cell 8 based on this control signal. Thus, by carrying out variable speed control to each cylinder room and clamping room (Network �� Application �� room) supply control pressure, and the connection oil pressure that subtend forward clutch 2d and retrogressing stopper 2e supplies controls.

(forward clutch)

Fig. 2 is the CVT input shaft 14 directional profile figure of forward clutch 2d. Forward clutch 2d has: connect with torque converter output shaft 13 and the clutch coupling drum 50 that rotates integrally connects with sun wheel 2c and the clutch coupling wheel hub 51 that rotates integrally multiple input side friction plate 50as chimeric with clutch coupling drum 50 spline multiple outgoing side friction plate 51as chimeric with clutch coupling wheel hub 51 spline, clutch coupling piston 52, dish spring 53, clutch reset spring 54 and spring fixer 55.

In order to be described, the axis of CVT input shaft 14 is set as x-axis, relative to clutch coupling piston 52, the direction being provided with spring fixer 55 is defined as positive dirction. Forward clutch piston chamber 62 it is provided with between clutch coupling drum 50 and clutch coupling piston 52. The centrifugal decontamination chamber 63 of the impact getting rid of centrifugal oil pressure it is provided with between spring fixer 55 and clutch coupling piston 52.

In centrifugal decontamination chamber 63, to be provided with clutch reset spring 54 in x-axis in the way of movable. The x-axis positive dirction end of clutch reset spring 54 is fixed on spring fixer 55, and the x-axis negative direction end of clutch reset spring 54 is fixed on clutch coupling piston 52. Clutch coupling piston 52 is to arrange to moveable mode in x-axis. It is irremovable that spring fixer 55 utilizes stopper ring 56 to be fixed as in x-axis positive dirction.

Via forward clutch input aperture 61, forward clutch piston chamber 62 supplied working oil and discharge working oil from forward clutch piston chamber 62. If supplying working oil from forward clutch input aperture 61, then the power of the product size of the load area of the oil pressure in forward clutch piston chamber 62 (following, to be called that clutch coupling connects oil pressure Pc) and clutch coupling piston 52 acts on clutch coupling piston 52 along x-axis positive dirction. Therefore, clutch coupling piston 52 moves to x-axis positive dirction.

On the other hand, when clutch coupling piston 52 moves to x-axis positive dirction, clutch reset spring 54 is compressed, and the elastic force of the path increment x of clutch reset spring 54 and the product size of coefficient of elasticity acts on clutch coupling piston 52 along x-axis negative direction.

Fig. 3 represents the path increment x of clutch reset spring 54 and the relation of the elastic force of clutch reset spring 54 and load on spring F.

Clutch coupling piston 52 moves to the position that the load on spring F of the reactive force based on Pc and clutch reset spring 54 balances. When the clutch coupling piston chamber 62 that do not march forward supplies working oil and Pc is zero, clutch coupling piston 52 is exerted a force to x-axis negative direction by clutch reset spring 5, is pressed against on clutch coupling drum 50, and the path increment x of clutch coupling piston 52 is zero. The load on spring F of clutch reset spring 54 now is set to initial setting up load F0.

In clutch coupling piston 52 and multiple gap being provided with specified amount between friction plate 50a, 51a, clutch coupling piston 52 needs to move specified amount stroke to x-axis positive dirction, until multiple friction plate 50a, 51a of input side and outgoing side contact mutually completely. If the trip amount is x1. X is zero from zero (above-mentioned gap is maximum) to the above-mentioned gap of x1(), not producing frictional force each other at multiple friction plate 50a, 51a, forward clutch 2d does not have connection capacity.

That is, forward clutch 2d is non-coupled state. Clutch coupling piston 52 is moving the position of x1 to x-axis positive dirction, when stopping at this position because balancing based on the load on spring F of the reactive force of Pc and clutch reset spring 54, if the size of Pc is Pc1. In addition, if the load on spring F of clutch reset spring 54 now is F1. When x is x1, when Pc is greater than Pc1, dish spring 53 starts to be compressed, and produces frictional force each other at multiple friction plate 50a, 51a, and forward clutch 2d has connection capacity Tc. That is, the coupled situation of forward clutch 2d starts.

(outline in oil pressure loop)

Fig. 4 represents the part in the oil pressure loop in oil pressure cntrol valve cell 8. At the relief outlet of oil pump 7, it is connected with the relief valve (P.REG.V) 110 regulating pipeline pressure P L via oil circuit 101. The oil circuit 102,103 being connected with oil circuit 101 will be supplied to by the first oil pressure (PL) after pressure regulation between oil pump 7 and P.REG.V110. Oil circuit 102 is connected with by the oil circuit 70 that elementary clamping room 30d and secondary clamping room 31d is connected. Always it is fed into elementary clamping room 30d and secondary clamping room 31d via oil circuit 70 by the PL after P.REG.V110 pressure regulation.

Oil circuit 103 is connected with oil circuit 104 and oil circuit 106��108. In oil circuit 104, it is connected with oil circuit 111 via throttle orifice 105. Oil circuit 106 is connected with the secondary valve (SEC.V) 140 of the oil pressure of supply secondary pulley cylinder room 31c. Oil circuit 107 is connected with the speed change control valve 170 of the oil pressure of supply primary pulley cylinder room 30c.

Speed change control valve 170 and the oil circuit 171 supplying primary pulley oil pressure to primary pulley cylinder room 30c. In addition, being connected with mechanism (ratio of gear sensor 30i) and the step-by-step motor 10 of the groove width representing primary pulley 30 at speed change control valve 170 via link rod 172, they form the mechanical feedback mechanism that namely drive volume according to step-by-step motor 10 rotates number of steps (�� number) feedback control ratio of gear.

In the downstream of P.REG.V110, it is connected with the clutch and regulating valve (CL.REG.V) 120 regulating two oil pressure (the connection oil pressure of such as forward clutch 2d) lower than PL via oil circuit 111. To system selector switch valve (SELECT.SW.V) 182 and select control valve (SELECT.CONT.V) 183 supply via oil circuit 112 by the 2nd oil pressure after CL.REG.V120 pressure regulation, and supply to the secondary control valve (SEC.CONT.V) 150 as ratio control valve via oil circuit 113.

Oil circuit 104 is connected with switching valve 190 via oil circuit 109. Switching valve 190 is connected with oil circuit 112 via oil circuit 191, is switched by the connected state of the oil circuit 103 of supply belt wheel oil pressure and the oil circuit 112 of supply forward clutch pressure.

Oil circuit 108 is connected with pilot valve (PILOT.V) 130. PILOT.V130 supplies the former pressure i.e. first pilot of signal pressure. First pilot supplies to secondary pressure electromagnetic valve (SEC.SOL.V) 160, lock-up solenoid valve (L/U.SOL.V) 180 and system selector switch magnetic valve (SELECT.SW.SOL.V) 181 via oil circuit 131.

Supply as the back pressure of SEC.CONT.V150 via oil circuit 161 by the signal pressure after SEC.SOL.V160 pressure regulation. SEC.CONT.V150 is supplied as the back pressure of SEC.V140 via oil circuit 151 by the 3rd oil pressure (oil pressure after the 2nd oil pressure has been carried out pressure regulation) after pressure regulation. In SEC.V140, using PL, as former pressure, oil pressure after pressure regulation is fed into secondary pulley cylinder room 31c.

The output pressure of SELECT.SW.SOL.V181 is supplied to system selector switch valve (SELECT.SW.V) 182 via oil circuit 185, and controls the action of SELECT.SW.V182 as signal pressure. The output pressure of L/U.SOL.V180 is supplied to SELECT.SW.V182 via oil circuit 184.

When SELECT.SW.SOL.V181 connects (ON), the signal pressure (exporting pressure) of SELECT.SW.SOL.V181 is inputted to SELECT.SW.V182. So, SELECT.SW.V182 cuts off the oil circuit 112 being connected with CL.REG.V120 and the oil circuit 40 being connected with manual valve 22, and the oil circuit 115 being connected with SELECT.CONT.V183 is connected with oil circuit 40. Meanwhile, the oil circuit 184 making to be connected with L/U.SOL.V180 and the oil circuit 186 being connected with SELECT.CONT.V183 are connected.

Now, therefore, the working oil (the 2nd oil pressure) from oil circuit 112 is all supplied to SELECT.CONT.V183, on the other hand, in SELECT.CONT.V183, carries out pressure regulation according to the signal pressure from L/U.SOL.V180. The clutch coupling being adjusted to the oil pressure (tentative pressure) lower than the 2nd oil pressure connects oil pressure Pc, supplies to manual valve 22 via oil circuit 115, SELECT.SW.V182 and oil circuit 40.

When SELECT.SW.SOL.V181 disconnects (OFF), the signal (exporting pressure) of SELECT.SW.SOL.V181 is zero, does not supply signal pressure to SELECT.SW.V182. Therefore, SELECT.SW.V182 makes oil circuit 112 be connected with oil circuit 40, and oil circuit 115 and oil circuit 40 is cut off. Meanwhile, the oil circuit 184 being connected with L/U.SOL.V180 is connected with the not shown lock oil circuit 187 that only control valve connects, and oil circuit 184 and oil circuit 186 are cut off.

Now, therefore, working oil (the 2nd oil pressure) from oil circuit 112 is all fed into manual valve 22 via oil circuit 40. On the other hand, the signal pressure from L/U.SOL.V180 is fed into not shown lock only control valve, and the signal pressure stopping control valve as this lock plays a role.

Oil circuit 40 is provided with oil pressure sensor 40a.

(formation of hydraulic pressure control device)

The electronic type oil pressure control device that the hydraulic pressure control device of the present invention has SELECT.SW.V182, SELECT.CONT.V183, manual valve 22, the mechanical type hydraulic pressure control device being made up of bidirectional electromagnetic valve 80, CVT control unit 9, L/U.SOL.V180 and is made up of SELECT.SW.SOL.V181.

(electronic type oil pressure control device)

In order to improve burn-up rate, CVT control unit 9 carries out idle stop control engine being stopped when meeting prescribed condition. The situation that CVT control unit 9 detects the situation of the extremely low speed of a motor vehicle and engine idle rotates, and then and with the signal of the various sensors such as brake switch or oil temperature sensor 5c, judge that idle stop control starts and end. Such as, if meet that the speed of a motor vehicle is zero, idle stop switch is connected, brake switch is connected, oil temperature T in specialized range, angle of turning be the condition such as zero, then make engine stop. Now, electric current by bidirectional electromagnetic valve 80 described later is formed as connection state. In addition, if brake switch is disconnected, then drive starter and engine is restarted. When engine is restarted, the electric current of bidirectional electromagnetic valve 80 is formed as cut-out state.

In addition, CVT control unit 9 is to L/U.SOL.V180 and SELECT.SW.SOL.V181 output order, it may also be useful to SELECT.SW.V182 and SELECT.CONT.V183 carries out when engine is restarted making marching forward tentative pressure (canopy) control that the connection oil pressure Pc that clutch coupling 2d supplies rises gradually.

When engine is restarted, oil pump 7 is started working, when the clutch coupling 2d that marches forward supplies oil pressure, elementary movable pulley 30a and secondary movable pulley 31a is produced respectively to elementary fixed pulley 30b and secondary fixed pulley 31b side pressure lean on the clamping pressure of clamping band 15 simultaneously, consequently, it is desirable to supply oil pressure to primary pulley cylinder room 30c, elementary clamping room 30d, secondary pulley cylinder room 31c, secondary clamping room 31d. May be difficult to guarantee clamping pressure when engine is restarted when the oil pressure supply of the clutch coupling 2d that marches forward is too smooth and easy. Therefore, CVT control unit 9, after being connected by SELECT.SW.V182, utilizes the signal pressure control SELECT.CONT.V183 of L/U.SOL.V180. Thus, from the working oil (hereinafter referred to as the 2nd oil pressure) of oil circuit 112,114 at SELECT.CONT.V183 by pressure regulation, the oil pressure (hereinafter referred to as tentative pressure) lower than the 2nd oil pressure is become to be supplied to forward clutch 2d via oil circuit 115, SELECT.SW.V182 and oil circuit 40 by pressure regulation. Like this, by the tentative pressure-controlling that performs the best of forward clutch 2d, the band of the reduction that pump when restarting with engine discharges pressure can be avoided to skid, and as hereinafter described, it is possible to realize engine restart after starting smoothly.

(oil pressure control circuit of forward clutch)

The part of the mechanical type hydraulic pressure control device of the hydraulic pressure control device of Fig. 5,6 expression the present invention, namely control to march forward the oil pressure control circuit 20 of connection oil pressure Pc that clutch coupling 2d supplies from manual valve 22. Fig. 5 represents that bidirectional electromagnetic valve 80 is closing condition, Fig. 6 represents that bidirectional electromagnetic valve 80 is for opened condition. The discharge pressure of oil pump 7 is regulated by above-mentioned electronic type oil pressure control device, and the oil pressure after pressure regulation supplies to manual valve 22 via oil circuit 40. Manual valve 22 is connected with bidirectional electromagnetic valve 80. Bidirectional electromagnetic valve 80 is connected with forward clutch 2d. Bidirectional electromagnetic valve 80 and forward clutch 2d are connected by oil circuit 45.

(manual valve)

It is connected from the oil circuit 40 of SELECT.SW.V182 and the suction port 221 of manual valve 22. Manual valve 22 has D shelves mouth 222, R shelves mouth 223 and discharge outlet 224,225. D shelves mouth 222 is connected with bidirectional electromagnetic valve 80 via oil circuit 42. R shelves mouth 223 is connected with retrogressing stopper 2e via oil circuit 43.

Manual valve 22 is connected with shift bar via not shown link rod, and according to the operation of shift bar, the switching clutch coupling 2d that marches forward supplies working oil or the stopper 2e that draws back and supplies working oil.

When shift bar is operated to D file location, D shelves mouth 222 is connected with suction port 221, D shelves mouth 222 and discharge outlet 224 are cut off. Meanwhile, R shelves mouth 223 is connected with discharge outlet 225, R shelves mouth 223 and suction port 221 are cut off.

When shift bar is operated to R file location, R shelves mouth 223 is connected with suction port 231, R shelves mouth 223 and discharge outlet 231 are cut off. Meanwhile, D shelves mouth 222 is connected with discharge outlet 224, D shelves mouth 222 and suction port 221 are cut off.

When being operated to N file location by shift bar, the sliding post of manual valve 22 moves to D shelves and the mid-way of R shelves, D shelves mouth 222 is connected with discharge outlet 224, D shelves mouth 222 and suction port 221 is cut off. Meanwhile, R shelves mouth 223 is connected with discharge outlet 225, R shelves mouth 223 and suction port 221 are cut off.

(about bidirectional electromagnetic valve)

The D shelves mouth of manual valve 22 is connected with the suction port 89a of bidirectional electromagnetic valve 80. Bidirectional electromagnetic valve 80 clips plate member 86 and is formed with suction port 89a in side, is formed with relief outlet 89b in another side. Hereinafter, suction port 89a side is defined as oil pressure source side, relief outlet 89b side is defined as pressure supply side side. Relief outlet 89b is connected with oil circuit 45, and the forward clutch input aperture 61(of oil circuit 45 and forward clutch 2d is with reference to Fig. 5) it is connected.

As shown in the sectional view of the bidirectional electromagnetic valve 80 of Fig. 5, bidirectional electromagnetic valve 80 has the plunger 83 producing the coil 81 of electromagnetic force, the inner circumferential being configured at coil 81 and the roughly cylinder shape that utilizes electromagnetic attraction and work, return spring 82(first elastomerics being arranged in plunger 83). Plunger 83 and little and that diameter ratio valve body described later 85 the is little pin parts 84 of this plunger 83 of diameter ratio are assembled integratedly. The plate member 86 being formed with circulation hole 87 and valve seat 86a it is provided with in the front of pin parts 84. In addition, the diameter ratio circulation hole 87 selling parts 84 is little.

Spheroid and valve body 85 it is provided with in the oil pressure source side of plate member 86. Valve body 85 is configured to by spring 88(the 2nd elastomerics) it is landed on valve seat 86a to plate member 86 side force, thus can by inaccessible for circulation hole 87. Valve body 85 is configured to utilize pin parts 84 to press from the pressure supply side side in circulation hole 87, and pin parts 84 are resisted the reactive force of spring 88 and pressed down by valve body 85, thus can be opened by valve.

That is, open state according to the circulation hole 87 of plate member 86 determines oil pressure source side and the connected state of pressure supply side side.

(effect of bidirectional electromagnetic valve)

Then, the effect of bidirectional electromagnetic valve 80 is described. In addition, the reactive force of return spring 82 is defined as f1, the reactive force of spring 88 is defined as f2(< f1), electromagnetic attraction is defined as F. As shown in Figure 5, when bidirectional electromagnetic valve 80 is for electric current cut-out state, owing to the reactive force f1 of return spring 82 is bigger than the reactive force f2 of spring 88, so valve body 85 is pressed down and leave from valve seat 86a by pin parts 84. Thus, suction port 89a and relief outlet 89b becomes connected state, have passed the line pressure of manual valve 22 be can march forward clutch coupling 2d supply state. Therefore, when usual traveling state, by the electric current of bidirectional electromagnetic valve 80 is cut off and the clutch coupling 2d that marches forward supplies oil pressure.

Then, after vehicle stops, when the condition specified is set up and carried out idle stop, the electric current of bidirectional electromagnetic valve 80 is formed as connection state. Fig. 6 is the figure representing that the electric current of bidirectional electromagnetic valve connects state. As shown in Figure 6, when becoming electric current and connect state, produce electromagnetic attraction F, pin parts 84 top in Fig. 6 is picked up. That is, the relation of F > f1-f2 is set up, and valve body 85 utilizes the effect f2 of spring 88 and is landed on valve seat 86a. Thus, suction port 89a and relief outlet 89b becomes cut-out state, in forward clutch 2d, in the scope of the reactive force f2 of spring 88, keeps connecting oil pressure Pc. In addition, oil pressure Pc is connected bigger than the elastic force F0 of clutch reset spring 54 and be less than the elastic force F1 that clutch coupling gap switches to the clutch reset spring 54 in zero (clutch coupling travel of piston amount x is x1) moment. Therefore, the non-coupled state that can maintain forward clutch 2d is constant, the gap blocking (�� Network ��: the gap blocking of the clutch coupling of separation) of the forward clutch 2d carried out when being restarted by the engine after idle stop reduces the amount connecting oil pressure Pc, carries out rapidly the connection of forward clutch 2d.

As mentioned above, it is necessary, be connected state by being formed as by bidirectional electromagnetic valve 80 under electric current cut-out state, under electric current connection state, keep the formation of specified pressure, it is possible to keep the oil pressure in forward clutch 2d with an oil circuit. Therefore, if not needing to arrange multiple oil circuit, not needing to be switched by multiple oil circuit yet, the complicated of oil circuit can be avoided.

In addition, even if becoming apparatus failure state or entering safe pattern because of other reason and become the state that can not supply electric current to bidirectional electromagnetic valve 80, owing to the electric current of bidirectional electromagnetic valve 80 is that the state and suction port 89a cut off and relief outlet 89b maintain connected state, so bring any impact can not to common traveling. Therefore, electric current cuts off and maintains connected state, is also favourable as fault countermeasure.

(effect of embodiment 1)

The hydraulic pressure control device of the automatic transmission of embodiment 1 has the following effect enumerated.

(1) bidirectional electromagnetic valve of the present invention possesses: plunger 83, and it drives based on connection and the cut-out of electric current; Valve body 85, it is moved by the driving of plunger 83, is contacting and separating with valve seat 86a and opens and closes oil circuit; Return spring 82(first elastomerics), plunger 83 is exerted a force from the direction that valve seat 86a leaves by it to valve body 85; Spring 88(the 2nd elastomerics), valve body 85 is exerted a force by its direction contacted with valve seat 86a to valve body 85, connecting with electric current and make valve body 85 be landed on valve seat 86a, electric current cuts off and makes valve body 85 set reactive force f1, f2 of return spring 82 and spring 88 from the mode that valve seat leaves.

Therefore, when keeping the oil pressure of the supply side as oil pressure and forward clutch 2d, it is not necessary to multiple oil circuit and switching valve etc. are set, the complicated of oil pressure loop can be avoided.

(2) valve seat 86a is located at and supplies the suction port 89a(oil pressure source of oil pressure from oil pump 7) and the relief outlet 89b(pressure supply side that is connected with forward clutch 2d) between, return spring 82 is configured in than valve seat 86a more by relief outlet 89b side, and to the parts that the base end part of plunger 83 exerts a force from relief outlet 89b side direction suction port 89a side, valve body 85 is configured in than valve seat 86a more by suction port 89a side, spring 88 is the parts that valve body 85 exports 89b side force from suction port 89a lateral row, plunger 83 is when electric current cuts off, utilize the reactive force of return spring 82 by its leading section from relief outlet 89b side direction suction port 89a side pressing valve body 85, when electric current is connected, leading section is positioned at more lean on relief outlet 89b side than valve body 85 and allow the parts that valve body 85 is landed on valve seat 86a.

Namely, under electric current is connection state, valve body 85 is exported 89b side force from suction port 89a lateral row by spring 88, therefore, exceed the reactive force f2 of spring 88 at the oil pressure of forward clutch 2d during, the oil circuit of bidirectional electromagnetic valve 80 becomes connected state, and the oil of forward clutch 2d flows out via bidirectional electromagnetic valve 80. Then, when the oil pressure of forward clutch 2d becomes lower than the pressure corresponding with the reactive force f2 of spring 88, bidirectional electromagnetic valve 80 is cut off, and can prevent the oil pressure in forward clutch 2d from reducing further. That is, according to above-mentioned formation, if being set to the reactive force f1 < electromagnetic attraction F of return spring 82, then by electric current is connected, it is possible to the oil pressure of the reactive force f2 corresponding to spring 88 is remained in forward clutch 2d. In other words, by suitably setting reactive force f2, it is possible to regulate the size of the oil pressure kept in forward clutch 2d.

(3) pressure supply side is the forward clutch 2d utilizing oil pressure and connect when vehicle start, and oil pressure source take engine as the oil pump 7 driving source.

Namely, for the forward clutch 2d wanting to guarantee oil pressure to a certain degree when idle stop controls, with the relation of oil pump 7 that can lose the function as oil pressure source during idle stop, by application bidirectional electromagnetic valve 80, when restarting, based on engine, the vehicle start carried out etc., it may be achieved start to walk smoothly.

(4) valve body 85 is spheroid. That is, as covered in the prior art, have employed when carrying out, by sliding moving of post, the formation switched, when switching the oil circuit with pressure retaining valve and do not have the oil circuit of pressure retaining valve, sliding post likely can block because of dirt etc. Assume the words that sliding post blocks, then likely can not switch oil circuit, can not carry out the pressurize of forward clutch 2d, or the oil pressure in forward clutch 2d can not discharge, producing when not being the intention of officer, engine driven power is transmitted such discomfort sense to driving wheel. To this, in embodiment 1, owing to valve body 85 is spheroid, it is possible to avoid blocking such situation because of dirt etc.

(other embodiments)

Above, the preferred embodiment of the present invention being illustrated based on embodiment 1, but the concrete formation of the present invention is not limited to embodiment 1, the design change etc. of the scope not departing from the main idea of invention is also contained in the present invention. Such as, in embodiment 1, the hydraulic pressure control device of the present invention is applied to the automatic transmission with variable v-belt drive, but can also apply the present invention to have the stepped automatic transmission of planetary set. In addition, in embodiment 1, illustrate as the formation that starting connects key element the present invention and only applies the clutch coupling of advance, but the clutch coupling (stopper) retreated also can be used for the present invention.

Claims

1. a hydraulic pressure control device for automatic transmission, this automatic transmission is located on the vehicle of the idle stop control carrying out stopping the idling of engine when the condition specified is set up, it is characterised in that,

Described hydraulic pressure control device has:

Oil pump, it is using described engine as driving source;

Bidirectional electromagnetic valve, supplies oil pressure from the described oil pump as oil pressure source to this bidirectional electromagnetic valve;

Start clutch, it is when described vehicle start, utilizes the oil pressure supplied via described bidirectional electromagnetic valve and connects,

Described bidirectional electromagnetic valve possesses:

Plunger, it drives based on connection and the cut-out of electric current;

Valve body, it is moved by the driving of described plunger, separate and switch oil circuit with valve seat;

First elastomerics, described plunger is exerted a force from the direction that described valve seat leaves by it to described valve body;

2nd elastomerics, described valve body is exerted a force by its direction contacted with described valve seat to described valve body,

Described valve seat is located between described oil pump and described start clutch,

Described first elastomerics is configured in described plunger, and the parts base end part of described plunger exerted a force from oil pump side described in described start clutch side direction,

Described valve body is configured in than described valve seat more by the position of described oil pump side,

Described 2nd elastomerics is the parts exerted a force from described oil pump side towards described start clutch side by described valve body,

The reactive force of first and second elastomerics described is set as, described electric current is connected and made described valve body be landed on described valve seat, and described electric current cuts off and described valve body is left from described valve seat,

Electric current is cut off by described bidirectional electromagnetic valve when described vehicle is in traveling state, after described vehicle stops, when the condition of regulation is set up and carried out idle stop control, being connected by electric current.

2. the hydraulic pressure control device of automatic transmission as claimed in claim 1, it is characterised in that,

What be provided with the supply of start clutch described in subtend between described oil pump with described bidirectional electromagnetic valve connects the control valve that oil pressure carries out controlling.

3. the hydraulic pressure control device of automatic transmission as claimed in claim 1 or 2, it is characterised in that,

Described plunger is when electric current cuts off, the reactive force of described first elastomerics is utilized to be pressed from described start clutch side towards described oil pump side by described valve body by its leading section, when electric current is connected, leading section is positioned at and more leans on described start clutch side than described valve body and allow described valve body to be seated at the parts of described valve seat.

4. the hydraulic pressure control device of automatic transmission as claimed in claim 1 or 2, it is characterised in that,

Described valve body is spheroid.