CN102729815A - Oil pressure supply device of driving force distribution device - Google Patents
Oil pressure supply device of driving force distribution device Download PDFInfo
- Publication number
- CN102729815A CN102729815A CN2012101016898A CN201210101689A CN102729815A CN 102729815 A CN102729815 A CN 102729815A CN 2012101016898 A CN2012101016898 A CN 2012101016898A CN 201210101689 A CN201210101689 A CN 201210101689A CN 102729815 A CN102729815 A CN 102729815A
- Authority
- CN
- China
- Prior art keywords
- oil
- valve
- pressure
- oil circuit
- power fluid
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Images
Abstract
The invention provides an oil pressure supply device of a driving force distribution device. The oil pressure supply device seals a working oil in a sealed oil pressure loop in an oil path which is connected with a piston chamber of a clutch. When an opening-closing valve in the oil path has a fault and the oil pressure rises unusually, the pressure reduction of the oil path can be carries out, so the part damage can not happen. The oil pressure supply device is provided with a relief valve (70) which can release the oil pressure when the oil pressure of the working oil sealed in the oil path (49) between a check valve (39) and the piston chamber (15) exceeds a preset threshold (PO). When an adhesion fault (the piston chamber oil pressure sealing fault) occurs in a solenoid valve (43) which is arranged in the oil path (sealed oil path) between the check valve (39) and the piston chamber (15), an oil pump (35) is driven, and an oil pressure which is higher than a common regulated pressure is generated by the oil path (49), so the relief valve (70) is forced to work, and consequently the working oil in the oil path (49) can be discharged.
Description
Technical field
The present invention relates in the propulsive effort distribution device of the 4Wdvehicle that will be assigned to main drive wheel and secondary drive wheel from the propulsive effort of primary mover to supply with the hydraulic pressure supplying device of oil pressure, this oil pressure is used to produce the activating pressure of the power-transfer clutch that the propulsive effort distribution device had.
Background technology
In the past, had such 4Wdvehicle: this 4Wdvehicle possesses the propulsive effort distribution device that is used for the propulsive effort that is produced by drive sources such as driving engines is assigned to main drive wheel and secondary drive wheel.In this 4Wdvehicle; Be main drive wheel and trailing wheel is under the situation of secondary drive wheel for example at front-wheel; The propulsive effort that is produced by drive source is passed to front-wheel via drive axle and preceding diff, and is passed to the propulsive effort distribution device with clutch with multiple laminated disc via transmission shaft.Then, through supplying with the power fluid of set pressure to the propulsive effort distribution device from hydraulic pressure supplying device, thus the activating pressure of controlling and driving power distribution device.Thus, make drive source drives power be passed to trailing wheel with predetermined distribution ratio.
And the hydraulic pressure supplying device as being used for supplying with to the clutch with multiple laminated disc of propulsive effort distribution device oil pressure existed patent documentation 1, the hydraulic pressure supplying device shown in 2 in the past.Patent documentation 1, the hydraulic pressure supplying device shown in 2 are following structure: it possesses electric oil pump from power fluid to piston chamber that supply with, and electric oil pump is connected through the oil pressure supply passageway with piston chamber, and wherein this piston chamber produces the oil pressure that is used to push clutch with multiple laminated disc.And, in the hydraulic pressure supplying device of patent documentation 1, the rotating speed of motor-drive pump is controlled so that the output valve of motor-drive pump becomes the operation pressure that requires of oil clutch.In addition, in the hydraulic pressure supplying device of patent documentation 2 records, the motor driven of motor-drive pump is controlled with the distribution ratio cooresponding oil pressure of generation with propulsive effort.
In addition; As the structure beyond patent documentation 1, the structure shown in 2; The hydraulic pressure supplying device that also has following structure: through the valve that boiler check valve or electromagnetic valve etc. can be enclosed power fluid is set in the oil circuit between electric oil pump and piston chamber, thereby with oil circuit that piston chamber is communicated with in enclose power fluid.In this hydraulic pressure supplying device, in the oil circuit of enclosing between valve and the piston chamber, be provided for the open and close valves such as electromagnetic valve that the power fluid of this oil circuit is discharged.And, through under the open and close valve closing state, driving electric oil pump, thereby to passing to the oil circuit force feed power fluid of piston chamber and piston chamber is pressurizeed from enclosing valve., piston chamber stops electric oil pump after reaching the required pressure of the joint of power-transfer clutch.Thus, utilization makes clutch engagement from the pressure that the inclosure valve passes to the oil circuit of piston chamber.On the other hand, when releasing clutch, through opening open and close valve, will emit from enclosing the power fluid that valve passes to the oil circuit of grease chamber.Thus, piston chamber is reduced pressure, reduce the engaging force of power-transfer clutch.
What but, the hydraulic pressure supplying device of said structure adopted is following structure: discharge the power fluid of oil circuit and piston chamber is reduced pressure through opening open and close valves such as electromagnetic valve.Yet, just in case open and close valve can't normally be opened because of the et out of orders such as obstruction of foreign matter (dirt), can't carry out the decompression of piston chamber, the possibility that existence can't releasing clutch.Such problem was arranged in the past: owing to when the oil pressure of such piston chamber is enclosed fault, do not take appropriate emergency protection action, exist the driving condition of vehicle to remain on the four wheel drive state, vehicle is absorbed in the possibility of unstable movement.
In addition, from enclose the oil circuit that valve passes to piston chamber, be provided with the pressure discharge-service valve aforesaid, this pressures discharge-service valve is used for discharging power fluid above permissible range under the situation of abnormal ascending at the oil pressure of this oil circuit or temperature.Yet pressure discharge-service valve in the past is not to be envisioned for through common oil pressure control action to work, and therefore is designed to damaged along with work.Therefore, carried out at this pressure discharge-service valve of contingency needing the part replacement of disassembling/repairing and force discharge-service valve of hydraulic pressure supplying device under the situation of work.
Patent documentation 1: TOHKEMY 2004-19768 communique
Patent documentation 2: TOHKEMY 2001-206092 communique
Summary of the invention
The present invention accomplishes just in view of the above problems; Its purpose is to provide a kind of hydraulic pressure supplying device of propulsive effort distribution device; It possesses the oil hydraulic circuit of sealed-in type; The oil hydraulic circuit of this sealed-in type is sealing into the oil circuit that is communicated with the piston chamber that is used for making clutch engagement with power fluid, and unfavorable condition such as open and close valve et out of order that this hydraulic pressure supplying device is provided with in oil circuit and making under the situation of oil pressure abnormal ascending can be carried out the decompression of oil circuit and can not caused breakage of parts etc.
Be used for solving the hydraulic pressure supplying device (60) of the present invention of above-mentioned problem for the propulsive effort distribution device of 4Wdvehicle (1); This 4Wdvehicle (1) possesses: propulsive effort bang path (20), and this propulsive effort bang path (20) will be passed to main drive wheel (W1, W2) and secondary drive wheel (W3, W4) from the propulsive effort of drive source (3); And propulsive effort distribution device (10); This propulsive effort distribution device (10) is configured between the said drive source (3) and said secondary drive wheel (W3, W4) in the said propulsive effort bang path (20); Said propulsive effort distribution device (10) is made up of the frictional engagement key element; This frictional engagement key element has piston chamber (15) and range upon range of a plurality of friction members (13), and said piston chamber (15) produces oil pressure to piston (12), and said piston (12) is pushed said friction member (13) and said friction member (13) is engaged on stacked direction; Said hydraulic pressure supplying device (60) has oil hydraulic circuit (30); This oil hydraulic circuit (30) comprising: oil pump (35), and this oil pump (35) is driven by motor (37), is used for supplying with power fluid to said piston chamber (15); Power fluid is enclosed valve (39), and this power fluid is enclosed valve (39) and is used for power fluid is sealing into the oil circuit (49) that passes to said piston chamber (15) from said oil pump (35); And open and close valve (43); This open and close valve (43) is used for the said oil circuit (49) that said power fluid is enclosed between valve (39) and the said piston chamber (15) is opened and closed; The hydraulic pressure supplying device of this propulsive effort distribution device (60) is characterised in that; The hydraulic pressure supplying device of this propulsive effort distribution device (60) has by pass valve (70); To enclose the oil pressure of the power fluid in the said oil circuit (49) between valve (39) and the said piston chamber (15) be that predetermined threshold (P0) discharges this oil pressure when above to this by pass valve (70) being sealing into said power fluid, and said by pass valve (70) has: the first-class hand-hole (81a) and second ostium (81b) that are formed by said oil circuit (49) branch that power fluid circulated from said oil pump (35); Guiding valve (76), this guiding valve (76) have and bear from first compression face (76a) of the pressure of the power fluid of said first-class hand-hole (81a) and bear second compression face (76b) from the pressure of the power fluid of said second ostium (81b); Spool (79), this spool (79) is through being pushed and move to the open position of opening said oil circuit (49) from the off position that seals said oil circuit (49) by said guiding valve (76); And force application component (85); This force application component (85) to a side of leaving said spool (79) to said guiding valve (76) application of force; The area of said first compression face (76a) of said guiding valve (76) and the area of said second compression face (76b) differ from one another; Oil pressure at said oil circuit (49) is under the situation more than the said threshold value (P0) thus, and said guiding valve (76) overcomes the application force of said force application component (85) and moves, thereby pushes said spool (79) and open said oil circuit (49).
Hydraulic pressure supplying device according to propulsive effort distribution device of the present invention; Enclose unfavorable condition such as the open and close valve et out of order that is provided with in the oil circuit between valve and the piston chamber at power fluid and under the situation of the oil pressure abnormal ascending of this oil circuit, can be through opening the oil pressure that by pass valve discharges oil circuit.Thus, can carry out the decompression of oil circuit and can as urgent discharge-service valve in the past, not be accompanied by the breakage of parts.Therefore, carried out at the contingency by pass valve also can alleviating the trouble of safeguarding hydraulic pressure supplying device under the situation of work.In addition, even owing to be that by pass valve work can damaged structure yet, so parts can continue to use.In addition, owing to be the structure of opening by pass valve with the oil pressure of oil circuit linkedly, the action response property rapidly the when oil pressure that therefore can guarantee oil circuit rises.Therefore and by pass valve of the present invention has the effect of the urgent discharge-service valve that is provided with in the oil circuit in the past concurrently, can not cause increase or structure complicated of the number of components of hydraulic pressure supplying device.In addition, by pass valve of the present invention is the valve of the so-called controllable type of correspondingly working with the oil pressure of oil circuit, therefore compares with the urgent discharge-service valve of structure in the past damaged when the work, has the advantage of high precision of operating oil pressure.
And; Above-mentioned by pass valve is to push the valve that spool is opened the such simple structure of oil circuit through spool actuation; And constitute and put on first compression face of guiding valve and the variation of the power fluid load on second compression face is driven by guiding valve accordingly, therefore under the situation of the oil pressure abnormal ascending of oil circuit, can discharge this oil pressure reliably.
In addition, also can be that the hydraulic pressure supplying device of propulsive effort distribution device of the present invention possesses: control member (50), this control member (50) control is by the driving of the said oil pump (35) of said motor (37) realization and the switching of said open and close valve (43); And oil pressure detection means (45); This oil pressure detection means (45) detects the oil pressure of said oil circuit (49); Said control member (50) is after sending OPEN to said open and close valve (43); Passed through the schedule time (T0) and do not become yet under the situation below the set pressure, through driving the control that pressure that said oil pump (35) makes said oil circuit (49) by the strong hand rises to said threshold value (P0) by the oil pressure of the detected said oil circuit of said oil pressure detection means (45) (49).
In this structure; Enclose the open and close valves such as electromagnetic valve that are provided with in the oil circuit (inclosure oil circuit) between valve and the piston chamber when oil pressure inclosure fault (piston chamber) taken place under the situation of the adhesion fault under the closed condition etc. being judged as power fluid; Come to make by the strong hand by pass valve work through producing the oil pressure higher, can discharge the power fluid that is enclosed in the oil circuit than common pressure regulation.Like this, owing to taken place to make by pass valve work reliably under the situation of fault being judged as open and close valve, therefore can discharge the oil pressure of oil circuit.In addition; Owing to make the oil pressure rising of oil circuit make by pass valve work through closing the such simple procedure of open and close valve driving oil pump; Therefore need not complicated structure and control member; Through with the same simple structure and the control of situation of the oil pressure control of carrying out common piston chamber, just can make by pass valve work reliably.
In addition, note is a label of stating cooresponding inscape in the embodiment after illustrating as a reference and for example with reference to label in bracket above.
Hydraulic pressure supplying device according to propulsive effort distribution device of the present invention; It possesses the oil hydraulic circuit of sealed-in type; The oil hydraulic circuit of this sealed-in type is sealing into power fluid the oil circuit that is communicated with the piston chamber that is used for making clutch engagement; Under the situation of unfavorable conditions such as the open and close valve et out of order that in this oil circuit, is provided with and oil pressure abnormal ascending, can carry out the decompression of oil circuit and can not cause breakage of parts etc.
Description of drawings
Fig. 1 is the figure of summary structure of 4Wdvehicle that the hydraulic pressure supplying device of the propulsive effort distribution device that possesses embodiment of the present invention is shown.
Fig. 2 is the figure that the oil hydraulic circuit of hydraulic pressure supplying device is shown.
Fig. 3 is the sectional view that the detailed structure of by pass valve is shown.
Fig. 4 is the figure that is used to explain the work of by pass valve, (a) is the figure that is illustrated in the state that by pass valve is not worked when common, (b) is the figure that by pass valve has carried out the state of work when being illustrated in the fault of electromagnetic valve.
Fig. 5 is the diagram of circuit that is used to explain the control process of the hydraulic pressure supplying device when making by pass valve work.
Fig. 6 is the sequential chart of variation of open and-shut mode of operative condition, the electromagnetic valve of oil pressure (actual oil pressure) that the oil circuit of by pass valve before and after opening is shown, motor (oil pump).
Label declaration
1: 4Wdvehicle;
10: the front and back torque distribution is with power-transfer clutch (power-transfer clutch);
15: piston chamber;
30: oil hydraulic circuit;
35: oil pump;
37: motor;
39: boiler check valve (power fluid inclosure valve);
43: electromagnetic valve (open and close valve);
45: oil pressure sensor (oil pressure detection means);
47: oil temperature sensor;
49: oil circuit (inclosure oil circuit);
50:ECU (control member);
60: hydraulic pressure supplying device;
70: by pass valve;
71: piston shell;
72: the pump housing;
72b: second inflow entrance;
73: pump cover;
74: the guiding valve housing;
74a: first-class inlet;
74c: flow export;
74d: urgent discharge orifice;
75: valve chamber;
76: guiding valve;
76a: upper surface (first compression face);
76b: lower surface (second compression face);
76c: spring engagement groove;
76d: press section;
77: inner core;
78: urceolus;
79: overflow spheroid (spool);
81a: first-class hand-hole;
81b: second ostium;
81c: tap hole;
81d: urgent discharge orifice;
85: the first coil springs (force application component);
86: the second coil springs;
87: the spheroid ingathering chamber;
89: seat portion.
The specific embodiment
Below, with reference to accompanying drawing embodiment of the present invention is described at length.Fig. 1 is the figure of summary structure of 4Wdvehicle that the hydraulic pressure supplying device of the propulsive effort distribution device that possesses one embodiment of the present invention is shown.4Wdvehicle 1 shown in this figure possesses: driving engine (drive source) 3, and it is equipped on the front portion of vehicle horizontally; Automatic transmission with hydraulic torque converter 4, itself and driving engine 3 are provided with integratedly; And propulsive effort bang path 20, it is used for the propulsive effort from driving engine 3 is passed to front-wheel W1, W2 and trailing wheel W3, W4.
The output shaft of driving engine 3 (not shown) via automatic transmission with hydraulic torque converter 4, preceding diff 5, about drive axle 6,6 and be connected with left and right sides front-wheel W1, W2 as main drive wheel.And, the output shaft of driving engine 3 via automatic transmission with hydraulic torque converter 4, preceding diff 5, transmission shaft 7, back differential unit 8, about rear drive shaft 9,9 and be connected with left and right sides trailing wheel W3, W4 as secondary drive wheel.
Be provided with in the back differential unit 8: back diff 19, the rear drive shaft 9,9 about it is used for propulsive effort is assigned to; And the front and back torque distribution is with power-transfer clutch 10, and it is used to connect/cut off the propulsive effort bang path from transmission shaft 7 to back diff 19.The front and back torque distribution is power-transfer clutchs of hydraulic type with power-transfer clutch 10, is to be used at the propulsive effort distribution device of propulsive effort bang path 20 Control Allocation to the propulsive effort of trailing wheel W3, W4.In addition, also be provided with hydraulic pressure supplying device 60, this hydraulic pressure supplying device 60 possesses: oil hydraulic circuit 30, and it is used for forwards, backwards torque distribution and supplies with power fluides with power-transfer clutch 10; And 4WDECU 50, it is the control member that is used to control the supply oil pressure of oil hydraulic circuit 30.4WDECU 50 is made up of microcomputer etc.
4WDECU 50 (being designated hereinafter simply as " ECU ") 50 is through the supply oil pressure of control oil hydraulic circuit 30, thereby control is distributed to the propulsive effort of trailing wheel W3, W4 by the front and back torque distribution with power-transfer clutch (being designated hereinafter simply as " power-transfer clutch ") 10.Thus, carry out being main drive wheel, being the drive controlling of secondary drive wheel with trailing wheel W3, W4 with front-wheel W1, W2.
Promptly; ECU 50 comes dispensed to give propulsive effort and the oil pressure delivery volume to power-transfer clutch 10 cooresponding with it of trailing wheel W3, W4 based on the detection of the various detection meanss (not shown) of the motoring condition that is used to detect vehicle, and to the drive signal of power-transfer clutch 10 outputs based on this result of calculation.Thus, when power-transfer clutch 10 discharged (disconnection), the rotation of transmission shaft 7 can not be passed to back diff 19 sides, and the torque of driving engine 3 all is passed to front-wheel W1, W2, thereby becomes f-w-d (2WD) state.On the other hand, when power-transfer clutch 10 connected, the rotation of transmission shaft 7 was passed to back diff 19 sides, thereby the torque distribution of driving engine 3 becomes four wheel drive (4WD) state to front-wheel W1, W2 and trailing wheel W3, W4 both sides.At this moment, the engaging force through suitable control clutch 10 comes Control Allocation to give the propulsive effort of trailing wheel W3, W4.
Fig. 2 is the oil hydraulic circuit figure that the detailed structure of oil hydraulic circuit 30 is shown.Oil hydraulic circuit 30 shown in this figure possesses: oil pump 35, and it sucks via filter 33 and is stored in the power fluid in the fuel tank 31 and carries out force feed; Motor 37, it drives oil pump 35; And oil circuit 40, it is communicated to the piston chamber 15 of power-transfer clutch 10 from oil pump 35.
Power-transfer clutch 10 possesses: cylinder housing 11; And piston 12, it moves through advance and retreat in cylinder housing 11 and pushes range upon range of a plurality of friction members 13.In cylinder housing 11, and piston 12 between define the piston chamber 15 that imports power fluid.Piston 12 disposes with an end of the stacked direction of a plurality of friction members 13 relatively.Therefore, the oil pressure of the power fluid through being supplied to piston chamber 15, piston 12 is pushed friction member 13 on stacked direction, thereby power-transfer clutch 10 is engaged with predetermined activating pressure.
The oil circuit 40 that is communicated to piston chamber 15 from oil pump 35, be provided with boiler check valve 39, by pass valve 70, electromagnetic valve (open and close valve) 43, oil pressure sensor 45 in order.Boiler check valve 39 constitutes and makes power fluid logical from oil pump 35 side direction piston chamber 15 effluents, but stops power fluid circulation in the opposite direction.Thus, under the driving of oil pump 35, can the power fluid in the downstream that is sent to boiler check valve 39 be sealing in the oil circuit (following be called sometimes " inclosure oil circuit ") 49 between boiler check valve 39 and the piston chamber 15.Through being provided with the oil circuit 49 of above-mentioned boiler check valve 39 and oil pump 35, constituted the oil hydraulic circuit 30 of sealed-in type.And in this embodiment, boiler check valve 39 is to be used for power fluid is sealing into the power fluid inclosure valve that passes to the oil circuit 49 of piston chamber 15 from oil pump 35.
By pass valve 70 is following valves that constitute: the pressure of its oil circuit 49 between boiler check valve 39 and piston chamber 15 surpasses predetermined threshold (the threshold value P0 that afterwards states) and opens during abnormal ascending, thus discharge power fluid and discharge the oil pressure of oil circuit 49.Get back to fuel tank 31 from the power fluid that by pass valve 70 is discharged through oil circuit 41.The detailed structure of by pass valve 70 is narrated in the back.Electromagnetic valve 43 is open and close valves of break-make type, receives PWM control (dutycycle control) based on the instruction of ECU 50, thus switching that can control oil channel 49.Thus, oil pressure that can control plunger chamber 15.In addition, electromagnetic valve 43 is opened and is got back to fuel tank 31 from the power fluid that oil circuit 49 is discharged.In addition, oil pressure sensor 45 is the oil pressure detection means that are used to detect the oil pressure of oil circuit 49 and piston chamber 15, and its detected value is sent to ECU 50.In addition, piston chamber 15 is communicated with energy storage 18.Energy storage 18 have after the oil pressure stated suppress the effect of the oil pressure variation in piston chamber 15 and the oil circuit 49 when keeping.In addition, in fuel tank 31, be provided with the oil temperature sensor 47 of the temperature that is used for testing oil.The detected value of oil temperature sensor 47 is sent to ECU 50.
Then, the structure to by pass valve 70 describes.Fig. 3 is the sectional view that the detailed structure of by pass valve 70 is shown.In addition, in following explanation, mention or following time, expression be state shown in Figure 3 under go up or following.By pass valve 70 shown in this figure is set at piston shell 71 and between the pump housing 72 and pump cover 73 of the overlapping setting of downside of this piston shell 71.Piston shell 71, the pump housing 72 and pump cover 73 all are the parts of a part that constitute the shell of propulsive effort distribution device, and this propulsive effort distribution device comprises hydraulic pressure supplying device 60.By pass valve 70 possesses: guiding valve housing 74, and it is arranged in the piston shell 71; Valve chamber 75, it is formed at from the inside of guiding valve housing 74 to the in-to-in scope of the pump housing 72; Guiding valve 76, it is arranged in the valve chamber 75; And overflow spheroid (spool) 79, it is driven by guiding valve 76.
The oil circuit 49 (with reference to figure 2) that is communicated to by pass valve 70 from oil pump 35 is divided into two (having omitted the diagram of branching portion) through the effect of by pass valve 70; The first-class hand-hole 81a that wherein is provided with on a square tube to the piston shell 71, the opposing party pass to the second ostium 81b that is provided with between the pump housing 72 and the pump cover 73.On the other hand, the tap hole 81c that is provided with on the piston shell 71 passes to oil circuit 49, and this oil circuit 49 is communicated to piston chamber 15 from by pass valve 70.In addition, the urgent discharge orifice 81d that is located at the upper end of piston shell 71 is communicated with oil circuit 41 (with reference to figure 2), and this oil circuit 41 passes to fuel tank 31 from by pass valve 70.
In addition, on guiding valve housing 74, be provided with: first-class inlet 74a, it is communicated with first-class hand-hole 81a with valve chamber 75; Flow export 74c, it is communicated with tap hole 81c with valve chamber 75; And urgent discharge orifice 74d, it is communicated with urgent discharge orifice 81d with valve chamber 75.In addition, on the pump housing 72, be provided with the second inflow entrance 72b, this second inflow entrance 72b is communicated with the second ostium 81b with valve chamber 75.
Guiding valve 76 is that profile is roughly columned parts, is the double structure of inner core 77 and urceolus 78, between these inner cores 77 and urceolus 78, is formed with spring engagement groove 76c, the end engaging of first coil spring 85 that this spring engagement groove 76c states after supplying.Valve chamber 75 is made up of recess, and this recess has from guiding valve housing 74 to valve body 72, and what be provided with is axial inner peripheral surface roughly cylindraceous with above-below direction, and the guiding valve 76 that is disposed in the valve chamber 75 slides (advance and retreat are mobile) freely vertically.In addition, the double structure that guiding valve 76 is formed inner core 77 and urceolus 78 is for the big spring engagement groove 76c of depth dimensions is set between them.Thus, as long as spring engagement groove 76 can be set, guiding valve 76 might not be as this embodiment by inner core 77 and urceolus 78 these two component set-ups, also can be to constitute integratedly by parts.
In addition, be provided with between guiding valve housing 74 in being arranged at piston shell 71 and the piston shell 71 and be used for leak free O type circle (sealing element) 83 is carried out in the gap between them.In addition, between the inner peripheral surface of the outer peripheral face of guiding valve 76 and the pump housing 72, be provided with and be used for leak free O type circle (sealing element) 84 is carried out in the gap between them.
The spring engagement groove 76c of guiding valve 76 and and the inwall (upper wall) of its opposed valve chamber 75 between be provided with first coil spring (force application component) 85.By the elastic force of first coil spring 85 to guiding valve 76 lower end side (the second inflow entrance 72b side) application of force in valve chamber 75.Under this state, the lower surface 76b through guiding valve 76 seals the second inflow entrance 72b.In addition, guiding valve 76 becomes the state of keeping out of the way valve chamber 75 belows to the guiding valve housing 74.Thus, become the state that first-class inlet 74a (first-class hand-hole 81a) is communicated with flow export 74c (tap hole 81c) via valve chamber 75.
Be formed with spheroid ingathering chamber 87 between urgent discharge orifice 81d in piston shell 71 and the urgent discharge orifice 74d.In spheroid ingathering chamber 87, be provided with the overflow spheroid (spool) 79 that is used to seal urgent discharge orifice 74d.The top of guiding valve 79 and and the inwall (upper wall) of its opposed spheroid ingathering chamber 87 between be provided with second coil spring 86.On the other hand, on the urgent discharge orifice 74d of guiding valve housing 74, be provided with and be used to seat portion 89 that overflow spheroid 79 is taken a seat.By the elastic force of second coil spring 86 to overflow spheroid 79 lower end side (urgent discharge orifice 74d side) application of force in spheroid ingathering chamber 87.Thus, be seated at seat portion 89 through overflow spheroid 79, thereby by the urgent discharge orifice 74d of overflow spheroid 79 sealings.
On the urceolus 78 of guiding valve 76, be provided with: upper surface (first compression face) 76a, it bears the pressure from the power fluid of first-class hand-hole 81a; And lower surface (second compression face) 76b, it bears the pressure from the power fluid of the second ostium 81b.And upper surface 76a and lower surface 76b are set to the area that differs from one another.Thus; The load that upper surface 76a receives from the power fluid of first-class hand-hole 81a and the application force of first coil spring 85 act on guiding valve 76 from upside with joint efforts; Lower surface 76b acts on guiding valve 76 from the load that the power fluid of the second ostium 81b receives from downside, makes the magnitude relationship of guiding valve 76 and these power move up at upper and lower accordingly (driving) thus.
In addition, the upper end of the inner core 77 of guiding valve 76 be formed with to above the press section 76d of outstanding overshooting shape.Press section 76d forms the external diameter size littler than the internal diameter of urgent discharge orifice 74d.Thus, guiding valve 76 in valve chamber 75 to above move under the state of the end, be inserted into the lower end of the press section 76d of urgent discharge orifice 74d by pressurized overflow spheroid 79, thus overcome second coil spring 86 application force and with overflow spheroid 79 jack-up.Thus, overflow spheroid 79 portion 89 that lifts off a seat, urgent discharge orifice 74d opens.
In addition, first-class inlet 74a that is provided with on the guiding valve housing 74 and flow export 74c are configured in and clip valve chamber 75 and at its opposed position place, both sides.And, the open height of flow export 74c is set at the size bigger than the open height of first-class inlet 74a.Thus, guiding valve 76 in valve chamber 75 to above move under the state of the end, first-class inlet 74a becomes the state by guiding valve 76 complete closed, on the other hand, flow export 74c forms the state that one of which partially opens.
Then, the action to the by pass valve 70 of said structure describes.Fig. 4 is the figure that is used to explain the work of by pass valve 70, (a) is the figure that is illustrated in the state that by pass valve 70 is not worked when common, (b) is the figure of the state that by pass valve 70 has been worked when being illustrated in the fault of electromagnetic valve 43.The power fluid that is delivered to oil circuit 49 from oil pump 35 flows into by pass valve 70.This power fluid flows into by pass valve 70 from the first-class hand-hole 81a and the second ostium 81b both sides.As above-mentioned; In by pass valve 70; Balance between the load that load that receives from the power fluid of first-class hand-hole 81a (first-class inlet 74a) according to upper surface 76a and lower surface 76b receive from the power fluid of the second ostium 81b (the second inflow entrance 74b), the guiding valves 76 in the valve chamber 75 move.
Specifically; Set as follows: when the oil pressure of the power fluid oil circuit 49 in is lower than predetermined threshold value (the threshold value P0 that afterwards states), put on the load that puts on the lower surface 76b of guiding valve 76 with joint efforts greater than power fluid of application force of load and first coil spring 85 of the upper surface 76a of guiding valve 76 by the power fluid of first-class inlet 74a by the second inflow entrance 72b.On the other hand; Set as follows: when the oil pressure of the power fluid oil circuit 49 in is higher than threshold value P0, the load that puts on the lower surface 76b of guiding valve 76 by the power fluid of the second inflow entrance 72b put on greater than power fluid by first-class inlet 74a guiding valve 76 upper surface 76a load and first coil spring 85 application force with joint efforts.
Therefore, shown in Fig. 4 (a), when the oil pressure of oil circuit 49 was lower than threshold value P0, guiding valve 76 was positioned at the lower end of valve chamber 75.Thus, the second ostium 81b (the second inflow entrance 72b) is closed, and first-class hand-hole 81a (first-class inlet 74a) is communicated with via valve chamber 75 with tap hole 81c (flow export 74c).In addition, overflow spheroid 79 is seated at seat portion 89, becomes the state that urgent discharge orifice 81d (urgent discharge orifice 74d) is closed.Therefore, the power fluid of oil circuit 49 can not discharged from by pass valve 70.
On the other hand, shown in Fig. 4 (b), if the oil pressure of oil circuit 49 is higher than threshold value P0, then guiding valve 76 overcomes the application force of first coil spring 85 and moves to the upper end side of valve chamber 75.Thus, by guiding valve 76 sealing first-class hand-hole 81a (first-class inlet 74a).In addition, the second ostium 81b (the second inflow entrance 72b) continues the state that maintenance is closed.On the other hand, tap hole 81c (flow export 74c) becomes by guiding valve 76 and partly seals and its part stays open.In addition, move to the press section 76d jack-up overflow spheroid 79 of guiding valve 76 of the upper end side of valve chamber 75, portion 89 thereby overflow spheroid 79 is lifted off a seat.Thus, urgent discharge orifice 81d (urgent discharge orifice 74d) opens.Therefore, tap hole 81c is communicated with via valve chamber 75 with urgent discharge orifice 81d.Thus, the power fluid of being enclosed in the oil circuit 49 is discharged to fuel tank 31 from the urgent discharge orifice 81d of by pass valve 70.Therefore, the oil pressure of oil circuit 49 reduces.
In addition, power fluid is discharged and when the oil pressure of oil circuit 49 is reduced via by pass valve 70, the application force through first coil spring 85 makes guiding valve 76 descend once more, gets back to the state shown in Fig. 4 (a).Thus, urgent discharge orifice 81d (urgent discharge orifice 74d) sealing and get back to original state.
The process of the oil pressure of control oil hydraulic circuit 30 describes when then, above-mentioned by pass valve 70 being worked.Fig. 5 is the diagram of circuit that is used to explain the process of this control.In addition, Fig. 6 is the sequential chart of variation of open and-shut mode of operative condition, the electromagnetic valve 43 of oil pressure (actual oil pressure), the motor 37 (oil pump 35) of the oil circuit 49 when by pass valve 70 being shown opening.At first, the process that should control along the flowchart text of Fig. 5.ECU 50 judges enclosing power fluid to oil circuit 49 and in piston chamber 15, having produced under the state of oil pressure whether electromagnetic valve 43 fault (oil pressure is crossed major break down) (step ST1) has taken place.The fault of the electromagnetic valve 43 here be electromagnetic valve 43 because of foreign matter (dirt) thus the oil pressure that adhesions such as obstruction are closed condition to produce is crossed major break down.Of the back, according to when sending the OPEN of electromagnetic valve 43, whether observing suitable oil pressure reduce, judge that this oil pressure crosses major break down.As a result, if taking place, oil pressure do not cross major break down (denying), then with regard to this end process; If cross major break down (being) and oil pressure has taken place, promptly the oil pressure of oil circuit 49 surpasses threshold value P0, then starter motor 37 and oil pump 35; To oil circuit 49 transportation works oil, improve the pressure (step ST2) of oil circuit 49.After this, judge whether to have passed through the predefined time (setting-up time T0) (step ST3).Addition value according to time meter judges whether to have passed through setting-up time T0 here.As a result, if do not pass through setting-up time T0 (denying), then to time meter progressively increase (step ST4).On the other hand, if passed through setting-up time T0 (being), then stop motor 37 and oil pump 35 (step ST5).After this, initialization time meter (step ST6), end process.
The process of above-mentioned control then, is described with reference to the sequential chart of figure 6.In this control, under with oil circuit 49 osed top states, start oil pump 35 (motor 37) and the pressurization of beginning oil circuit 49 at moment T1 closing electromagnetic valve 43 in advance.Thus, the oil pressure of the power fluid in the oil circuit 49 rises.After this, stop oil pump 35 (motor 37), finish the pressurization of oil circuit 49 at moment T2.After this, in the of short duration time, the oil pressure that continues to be sealing into the power fluid in the oil circuit 49 keeps the pressure status of almost fixed.Then, send OPEN at moment T3 to electromagnetic valve 43.At this moment, if there is not adhesion fault in electromagnetic valve 43 and normally works, then electromagnetic valve 43 is opened and the power fluid of oil circuit 49 is discharged, thereby after this shown in the dotted line of this figure, the oil pressure of piston chamber 15 reduces.Relative therewith, stick together fault and under the situation about can't open rightly at electromagnetic valve 43, owing to can't discharge the power fluid of oil circuits 49 via electromagnetic valve 43, thereby after this shown in the solid line of this figure, the oil pressure of piston chamber 15 does not reduce and maintains higher degree.Though like this in the OPEN of having sent electromagnetic valve 43 but do not observe under the situation that oil pressure reduces, wait for the predetermined scheduled wait time (setting-up time T0), confirm that through fault detection oil pressure crosses major break down at moment T4 then.At this constantly, oily through starting oil pump 35 (motor 37) to oil circuit 49 transportation works, thus oil circuit 49 is further pressurizeed.Pressurization through this oil pump 35 is risen the oil pressure of oil circuit 49, and at moment T5, this oil pressure surpasses the threshold value P0 that opens by pass valve 70.Thus, the urgent discharge orifice 81d of by pass valve 70 is opened, and the power fluid of oil circuit 49 is discharged through by pass valve 70.In addition, stop oil pump 35 (motor 37) and finish the pressurization of oil circuit 49 at moment T5, thereby after this through the power fluid of the oil circuit 49 urgent discharge orifice 81d from by pass valve 70 is discharged, thereby the oil pressure of oil circuit 49 reduces.
As described above; The by pass valve 70 that the hydraulic pressure supplying device 60 of this embodiment is possessed is through being provided with difference between the compression area of the upper surface of guiding valve 76 76a and lower surface 76b, thereby constitutes the structure that the oil pressure with oil circuit 49 makes guiding valve 76 move accordingly.Thus, even the by pass valve of simple structure 70 also can discharge this oil pressure reliably under the situation of the oil pressure abnormal ascending of oil circuit 49.
What in addition, the by pass valve 70 of this embodiment adopted is that guiding valve housing 74 and guiding valve 76 are clipped in the structure that is provided with between range upon range of piston shell 71 and the pump housing 72 and the pump cover 73.Thus, need not to be used for fixing the other parts of guiding valve housing 74 and guiding valve 76 etc., can realize the reduction of number of components and the simplification of structure.In addition, as with the urgent discharge-service valve of in the past oil hydraulic circuit in the existing parts general-duty parts that use, by pass valve 70 possesses coil spring (second coil spring) 86 that pump cover 73, the pump housing 72, piston shell 71, overflow spheroid 79, overflow spheroid use etc.Therefore, when existing urgent discharge-service valve was replaced by the by pass valve 70 of this embodiment, the parts of newly establishing are less to get final product.Thus, can under the situation that does not increase new components number and total parts number, constitute the hydraulic pressure supplying device 60 that possesses by pass valve 70.
In addition; The hydraulic pressure supplying device 60 of this embodiment has the oil hydraulic circuit 30 that power fluid is sealing into the sealed-in type of the oil circuit 49 that is communicated with the piston chamber 15 that is used for power-transfer clutch 10 is engaged; And has by pass valve 70; The oil pressure of the power fluid of this by pass valve 70 in the oil circuit 49 that is sealing between boiler check valve 39 and the piston chamber 15 is that threshold value P0 discharges this oil pressure when above; Therefore the electromagnetic valve (open and close valve) 43 that in this oil circuit 49, is provided with sticks together under the situation of oil pressure abnormal ascending of unfavorable condition such as fault and oil circuit 49, also can discharge the oil pressure of oil circuits 49 through by pass valve 70.Thus, can carry out the decompression of oil circuit 49 and can as the urgent discharge-service valve of structure in the past, not be accompanied by the breakage of parts.Therefore, reduced the trouble of the maintenance of hydraulic pressure supplying device 60.In addition, even having worked, by pass valve 70 also can continue to use parts.In addition, owing to be the structure of opening by pass valve 70 with the oil pressure of oil circuit 49 linkedly, so the action response property of oil circuit 49 oil pressure when rising is fast.Therefore and the by pass valve 70 of this embodiment has the effect that all the time is arranged at the urgent discharge-service valve in the oil circuit 49 concurrently, can not cause increase or structure complicated of the number of components of hydraulic pressure supplying device 60.In addition, the by pass valve 70 of this embodiment is the valve of the controllable type of working accordingly with the oil pressure of oil circuit 49, therefore compares with the urgent discharge-service valve of structure in the past damaged when the work, has the advantage of high precision of operating oil pressure.
And above-mentioned by pass valve 70 possesses: the first-class hand-hole 81a and the second ostium 81b, and it is formed by the oil circuit that power fluid circulated 49 branches from oil pump 35; Guiding valve 76, it has and bears from upper surface (first compression face) 76a of the pressure of the power fluid of first-class hand-hole 81a and lower surface (second compression face) 76b that bears from the pressure of the power fluid of the second ostium 81b; Overflow spheroid (spool) 79, off position from closing oil path 49 moves to the open position of opening oil circuit 49 through being pushed by guiding valve 76 for it; And first coil spring 85, its to a side who leaves overflow spheroid 79 to guiding valve 76 application of forces.And; The area of the upper surface 76a of guiding valve 76 and the area of lower surface 76b differ from one another; Therefore when the oil pressure of oil circuit 49 reached more than the threshold value P0, guiding valve 76 overcame the application force of first coil spring 85 and moves, thereby by pressurized overflow spheroid 79 oil circuit 49 is opened.Thus, become the by pass valve 70 that drives the simple structure of guiding valve 76 with the oil pressure of oil circuit 49 accordingly, and can under the situation of the oil pressure abnormal ascending of oil circuit 49, discharge this oil pressure reliably.
In addition; In the hydraulic pressure supplying device 60 of this embodiment; ECU 50 has passed through schedule time T0 but the oil pressure of oil pressure sensor 45 detected oil circuits 49 is not lower than under the situation of set pressure yet after sending OPEN to electromagnetic valve 43, be judged as the fault of electromagnetic valve 43; And come to make by the strong hand the pressure of oil circuit 49 to rise to threshold value P0 through driving oil pump 35, by pass valve 70 is opened.
Promptly; (when piston chamber's oil pressure is enclosed fault) under the situation of adhesion fault taken place in the electromagnetic valve 43 in being judged as the oil circuit of being located between boiler check valve 39 and the piston chamber 15 (inclosure oil circuit) 49; Come to make by the strong hand by pass valve 70 work through producing the oil pressure higher, sealed-in power fluid in the oil circuit 49 is discharged than common pressure regulation.Thus, owing to by pass valve 70 work have taken place can make reliably under the situation of fault being judged as electromagnetic valve 43, therefore can discharge oil pressure reliably.In addition; Through driving oil pump 35 oil pressure of oil circuit 49 is risen and make by pass valve 70 work; Therefore need not complicated structure and control device, through with the same simple structure and the control of situation of the oil pressure control of carrying out common piston chamber 15, by pass valve 70 is worked.
More than, embodiment of the present invention has been described, yet the present invention is not limited to above-mentioned embodiment, can carry out various distortion in the scope of the technological thought of in the scope that does not break away from claim and specification sheets and accompanying drawing, putting down in writing.
Claims (2)
1. the hydraulic pressure supplying device of the propulsive effort distribution device in the 4Wdvehicle,
This 4Wdvehicle has: the propulsive effort bang path, and this propulsive effort bang path will be passed to main drive wheel and secondary drive wheel from the propulsive effort of drive source; And said propulsive effort distribution device, this propulsive effort distribution device is configured between the said drive source and said secondary drive wheel in the said propulsive effort bang path,
Said propulsive effort distribution device is made up of the frictional engagement key element, and this frictional engagement key element has piston chamber and range upon range of a plurality of friction members, and said piston chamber produces oil pressure to piston, and said piston is pushed this friction member and this friction member is engaged on stacked direction,
Said hydraulic pressure supplying device has oil hydraulic circuit, and this oil hydraulic circuit comprises: oil pump, this oil pump are used for supplying with power fluid to said piston chamber by motor driven; Power fluid is enclosed valve, and this power fluid is enclosed valve and is used for power fluid is sealing into the oil circuit that passes to said piston chamber from said oil pump; And open and close valve, this open and close valve is used for the said oil circuit that said power fluid is enclosed between valve and the said piston chamber is opened and closed,
The hydraulic pressure supplying device of this propulsive effort distribution device is characterised in that,
The hydraulic pressure supplying device of this propulsive effort distribution device has by pass valve, and to enclose the oil pressure of the power fluid in the said oil circuit between valve and the said piston chamber be that predetermined threshold discharges this oil pressure when above to this by pass valve being sealing into said power fluid,
Said by pass valve has:
By power fluid circulated the first-class hand-hole and second ostium that said oil circuit branch forms from said oil pump;
Guiding valve, this guiding valve have and bear from first compression face of the pressure of the power fluid of said first-class hand-hole and second compression face that bears from the pressure of the power fluid of said second ostium;
Spool, this spool is through being pushed and move to the open position of opening said oil circuit from the off position that seals said oil circuit by said guiding valve; And
Force application component, this force application component to a side of leaving said spool to the said guiding valve application of force,
The area of said first compression face of said guiding valve and the area of said second compression face differ from one another; Oil pressure at said oil circuit is under the situation more than the said threshold value thus; Said guiding valve overcomes the application force of said force application component and moves, thereby pushes said spool and open said oil circuit.
2. the hydraulic pressure supplying device of propulsive effort distribution device according to claim 1 is characterized in that, the hydraulic pressure supplying device of this propulsive effort distribution device has:
Control member, this control member control is by the driving of the said oil pump of said motor realization and the switching of said open and close valve; And
The oil pressure detection means, this oil pressure detection means detects the oil pressure of said oil circuit,
Said control member is controlled as follows: after sending OPEN to said open and close valve; Passed through the schedule time and the oil pressure of the detected said oil circuit of said oil pressure detection means does not become under the situation below the set pressure yet, risen to said threshold value through driving the pressure that said oil pump comes to make by the strong hand said oil circuit.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2011-089125 | 2011-04-13 | ||
| JP2011089125A JP2012218668A (en) | 2011-04-13 | 2011-04-13 | Hydraulic pressure feeder of driving force distributing device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN102729815A true CN102729815A (en) | 2012-10-17 |
| CN102729815B CN102729815B (en) | 2015-03-04 |
Family
ID=46986366
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201210101689.8A Active CN102729815B (en) | 2011-04-13 | 2012-04-09 | Oil pressure supply device of driving force distribution device |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP2012218668A (en) |
| CN (1) | CN102729815B (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105276162A (en) * | 2014-07-16 | 2016-01-27 | 本田技研工业株式会社 | Apparatus for detecting abnormal hydraulic pressure of automatic transmission |
| CN110857029A (en) * | 2018-08-24 | 2020-03-03 | 广州汽车集团股份有限公司 | Method and system for treating jamming of electromagnetic valve of clutch of hybrid vehicle and automobile |
| CN111433480A (en) * | 2018-09-10 | 2020-07-17 | Ｋｙｂ株式会社 | Brake system and hydraulic motor provided with same |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP6969206B2 (en) | 2017-08-07 | 2021-11-24 | 株式会社ジェイテクト | Control method for four-wheel drive vehicles and four-wheel drive vehicles |
| JP7000903B2 (en) * | 2018-02-15 | 2022-01-19 | いすゞ自動車株式会社 | Power transmission device |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN86102606A (en) * | 1985-07-01 | 1987-02-04 | 克罗斯比阀门测量公司 | Non-flowing modulating pilot operated relief valve |
| JPH0351521A (en) * | 1989-07-20 | 1991-03-05 | Tochigi Fuji Ind Co Ltd | Booster for power transmission device |
| JP2001206092A (en) * | 2000-01-24 | 2001-07-31 | Fuji Univance Corp | Driving force distribution device |
| US20020162722A1 (en) * | 2001-05-07 | 2002-11-07 | Satoru Suzuki | Driving force distributing apparatus |
| EP1371868A1 (en) * | 2002-06-14 | 2003-12-17 | Koyo Seiko Co., Ltd. | Electronic controlled coupling |
| CN101081596A (en) * | 2007-06-22 | 2007-12-05 | 哈尔滨工业大学 | Transmission system of double-bridge liquid-driving mixed power automobile |
-
2011
- 2011-04-13 JP JP2011089125A patent/JP2012218668A/en not_active Withdrawn
-
2012
- 2012-04-09 CN CN201210101689.8A patent/CN102729815B/en active Active
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN86102606A (en) * | 1985-07-01 | 1987-02-04 | 克罗斯比阀门测量公司 | Non-flowing modulating pilot operated relief valve |
| JPH0351521A (en) * | 1989-07-20 | 1991-03-05 | Tochigi Fuji Ind Co Ltd | Booster for power transmission device |
| JP2001206092A (en) * | 2000-01-24 | 2001-07-31 | Fuji Univance Corp | Driving force distribution device |
| US20020162722A1 (en) * | 2001-05-07 | 2002-11-07 | Satoru Suzuki | Driving force distributing apparatus |
| EP1371868A1 (en) * | 2002-06-14 | 2003-12-17 | Koyo Seiko Co., Ltd. | Electronic controlled coupling |
| CN101081596A (en) * | 2007-06-22 | 2007-12-05 | 哈尔滨工业大学 | Transmission system of double-bridge liquid-driving mixed power automobile |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105276162A (en) * | 2014-07-16 | 2016-01-27 | 本田技研工业株式会社 | Apparatus for detecting abnormal hydraulic pressure of automatic transmission |
| CN110857029A (en) * | 2018-08-24 | 2020-03-03 | 广州汽车集团股份有限公司 | Method and system for treating jamming of electromagnetic valve of clutch of hybrid vehicle and automobile |
| CN110857029B (en) * | 2018-08-24 | 2020-12-08 | 广州汽车集团股份有限公司 | Method and system for treating jamming of electromagnetic valve of clutch of hybrid vehicle and automobile |
| CN111433480A (en) * | 2018-09-10 | 2020-07-17 | Ｋｙｂ株式会社 | Brake system and hydraulic motor provided with same |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2012218668A (en) | 2012-11-12 |
| CN102729815B (en) | 2015-03-04 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN102729815A (en) | Oil pressure supply device of driving force distribution device | |
| US8327986B2 (en) | Combined power transmission, start-up unit and drive system | |
| US9097336B2 (en) | Device for controlling a hydraulic accumulator of a hydraulic system | |
| JP4577733B2 (en) | Pressure medium device | |
| US9334946B1 (en) | Vehicle transmission pressure regulator valve | |
| CN105090134B (en) | Hydraulic supply unit | |
| CN101907165A (en) | The hydraulic supply unit of automatic transmission | |
| JP2008546972A (en) | Method and apparatus for operating a vehicle clutch | |
| KR101466607B1 (en) | Electro-hydraulic clutch system | |
| CN105026781B (en) | The hydraulic disk clutch of AWD vehicles | |
| KR20120099035A (en) | Device for releasing, in a pulsed manner, an amount of fluid that can be stored in an accumulator housing | |
| JP2008190720A (en) | Two-step check valve for automatic transmission system | |
| JP6089533B2 (en) | Clutch control device for clutch device for hybrid vehicle | |
| KR20130049158A (en) | System and method for controlling an automatic engine stop-start accumulator | |
| US20090250310A1 (en) | Transmission apparatus comprising at least one positive shifting element hydraulically actuated by way of a hydraulic system | |
| US10054241B2 (en) | Valve, and the use thereof for a clutch | |
| WO2016158200A1 (en) | Electromagnetic valve and transmission-use fuel pressure control device using electromagnetic valve | |
| US9115702B2 (en) | Hydraulic control system | |
| CN103109113A (en) | Power transmitting device | |
| CN110966400A (en) | Gearbox hydraulic control system and vehicle | |
| CN103119337A (en) | Fluid pressure control device | |
| CN107923522B (en) | Hydraulic system of automatic transmission | |
| JP5773876B2 (en) | Hydraulic device for controlling the transmission | |
| US10012310B2 (en) | Hydraulic control unit for automatic transmission | |
| US9212670B2 (en) | Composite accumulator |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant |