CN101788051A - Hydraulic control system used in failure of electric control system of automatic speed changer - Google Patents
Hydraulic control system used in failure of electric control system of automatic speed changer Download PDFInfo
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- CN101788051A CN101788051A CN201010129014A CN201010129014A CN101788051A CN 101788051 A CN101788051 A CN 101788051A CN 201010129014 A CN201010129014 A CN 201010129014A CN 201010129014 A CN201010129014 A CN 201010129014A CN 101788051 A CN101788051 A CN 101788051A
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Abstract
The invention relates to a hydraulic control system used in failure of an electric control system of an automatic speed changer. The hydraulic control system comprises a manual control valve, a pressure reducing valve, a plurality of gear shift control valves and a plurality of electromagnetic valves, wherein each gear shift control valve is respectively controlled by one electromagnetic valve. The hydraulic control system is provided with a bumper gear control valve; a control port of each electromagnetic valve is respectively communicated with the control port of the bumper gear control valve by a one-way valve; an input port of the bumper gear control valve is communicated with an output port of the pressure reducing valve, and the output port of the bumper gear control valve is communicated with the manual control valve. When the electric control system of the vehicle automatic speed changer is failed, the manual control valve can work with other gear shift elements to realize reverse or forward gear and make sure that a vehicle can smoothly run with the forward or reverse gear. When the electric control system is suddenly failed in the normal running process of the vehicle, an energy accumulator and a throttle hole can smoothly enter the neutral gear and then slowly enter the bumper gear to run.
Description
Technical field
The present invention relates to a kind of hydraulic control system that is used for automatic transmission, when relating to a kind of automatical control system specifically and losing efficacy, can make the hydraulic control system of vehicle driving.
Background technique
At present, be loaded in the automatic transmission on the automobile, control the jointing state of a plurality of clutches or break by hydraulic pressure control device, by forming the transmission circuit of gear at each speed change retaining, each speed change retaining in the time of can realizing advancing and retreat retaining.In the above-mentioned this hydraulic pressure control device,,, and preferably use above-mentioned a plurality of solenoid valve valve of the Normally closed type of output oil pressure not when non-energising in addition in order to suppress power consumption in order to take place to prevent when some lost efficacy that this frictional engagement key element of not expecting from engaging.Therefore, this hydraulic pressure control device is under normal state, when gear being changed to forward gear or retreats retaining based on the operation of gear level, connect required solenoid valve, the fuel pressure servomotor of the frictional engagement key element that progressive speed change retaining or the speed change that retreats engage in keeping off is supplied with to engage and is pressed, but, in above-mentioned hydraulic pressure control device, because of some inefficacy, feasible formation retreats the required solenoid valve of retaining when still being in the state of non-energising, can not form and retreat retaining, promptly exist automobile can't retreat the problem of travelling, cause the vehicle driving inconvenience.
The vehicle that has was when automatical control system lost efficacy, can realize forward gear, also can realize reversing gear, but the realization of these functions is that the function by dissimilar solenoid valves realizes that its working principle is: adopt and often open and normally closed two types of solenoid valves, the normally closed solenoid valve delivery pressure reduces with the increase of electric current, when no current, produce maximum pilot pressure, control the action of shift valve with this; The normally open solenoid valve delivery pressure increases with the increase of electric current, and when no current, the pilot pressure of generation is zero, controls the action of shift valve with this.When automatical control system lost efficacy, no current was supplied with solenoid valve, this moment normally closed solenoid valve the delivery pressure maximum, this pressure control shift valve, the combination that comes solenoidoperated cluthes.Often opening each other can not be general and exchange with normally closed solenoid valve, is unfavorable for assembling, maintenance and changes, and has increased manufacturing and maintenance cost.
Summary of the invention
The technical problem to be solved in the present invention is in order to overcome above-mentioned defective, when providing a kind of automatical control system to lose efficacy, can to make the hydraulic control system of vehicle driving.
In order to address the above problem, the present invention is by the following technical solutions: the hydraulic control system when a kind of automatic speed-variator electric control system lost efficacy, comprise hand control valve, reduction valve, several gear shift control valves and several solenoid valves, gear shift control valve of each electromagnetic valve, it is characterized in that: described hydraulic control system is provided with lame car bumper control valve, the control port of each solenoid valve is communicated with through the control port of one-way valve with lame car bumper control valve respectively, the input port of lame car bumper control valve is communicated with the output port of reduction valve, and the output port of lame car bumper control valve is communicated with hand control valve.
Further improvement as last technological scheme:
Described gear shift control valve comprises the first gear shift control valve, the second gear shift control valve, the 3rd gear shift control valve, the 4th gear shift control valve and the 5th gear shift control valve, and each gear shift control valve is respectively equipped with input port, output port, first control port, second control port and drain tap.
The output port of described lame car bumper control valve is communicated with first control port of the second gear shift control valve and first control port of the 5th gear shift control valve respectively.
Described the 4th gear shift control valve and the input port of the 5th gear shift control valve are communicated with the output port of oil pump respectively.
Oil circuit between described lame car bumper control valve and the one-way valve is provided with accumulator and energy-conservation hole.
Described hand control valve is provided with first input end mouth, second input port, first output port, second output port, the 3rd output port and drain tap, and the first input end mouth is communicated with oil pump.
Described second input port is communicated with the output port of lame car bumper control valve.
First output port of described hand control valve is communicated with first control port of the first gear shift control valve.
Second output port of described hand control valve is communicated with first control port of the 4th gear shift control valve.
The 3rd output port of described hand control valve is communicated with the input port of the first gear shift control valve, the second gear shift control valve and the 3rd gear shift control valve respectively.
Described hand control valve comprises valve body, valve body is provided with first intercommunicating pore and second intercommunicating pore, first output port, second input port, second output port, second intercommunicating pore, first input end mouth and first intercommunicating pore are successively set on the valve body, and the 3rd output port is communicated with first intercommunicating pore and second intercommunicating pore.
Be provided with spool in the described valve body, be provided with valve pocket in the spool, drain tap is arranged on valve pocket one end.
Described spool is provided with six oil throughs that are communicated with valve pocket, is followed successively by first oil through, second oil through, the 3rd oil through, four-way oilhole, five-way oilhole and the 6th oil through from the side away from first output port.
Spool between described first oil through and second oil through is provided with first circular groove.
Spool between described the 3rd oil through and the four-way oilhole is provided with second circular groove.
The spool at described threeway oil-hole location place is provided with the 3rd circular groove.
Described solenoid valve is a normally open solenoid valve.
The present invention adopts technique scheme, has the following advantages: vehicular automatic transmission is under the situation that automatical control system lost efficacy, and hand control valve can cooperate other shifting element to realize reversing gear or forward gear, and vehicle can successfully be travelled with reversing gear with forward gear; In the normal vehicle operation process, under the situation of automatical control system catastrophic failure, accumulator and throttle orifice can successfully be introduced into neutral, gently enter lame car bumper then and travel; Solenoid valve all uses the normally open solenoid valve of same model, has reduced assembling, manufacturing and maintenance cost.
The invention will be further described below in conjunction with drawings and Examples.
Description of drawings
Accompanying drawing 1 is the structural representation of hydraulic control system in the embodiment of the invention;
Accompanying drawing 2 is the structural representation of the first gear shift control valve in the embodiment of the invention;
Accompanying drawing 3 is the structural representation of the second gear shift control valve in the embodiment of the invention;
Accompanying drawing 4 is the structural representation of the 3rd gear shift control valve in the embodiment of the invention;
Accompanying drawing 5 is the structural representation of the 4th gear shift control valve in the embodiment of the invention;
Accompanying drawing 6 is the structural representation of the 5th gear shift control valve in the embodiment of the invention;
Structural representation when accompanying drawing 7 is closed for lame car bumper control valve in the embodiment of the invention;
Structural representation when accompanying drawing 8 is opened for lame car bumper control valve in the embodiment of the invention;
Accompanying drawing 9 is the schematic diagram of hand control valve in the embodiment of the invention;
Phase diagram when accompanying drawing 10 is in parking shifting-position P for hand control valve in the embodiment of the invention;
Phase diagram when accompanying drawing 11 is in reversing gear R for hand control valve in the embodiment of the invention;
Phase diagram when accompanying drawing 12 is in neutral gear N for hand control valve in the embodiment of the invention;
Among the figure,
The 1-first gear shift control valve, the 2-second gear shift control valve, 3-the 3rd gear shift control valve, 4-the 4th gear shift control valve, 5-the 5th gear shift control valve, 6-first solenoid valve, 7-second solenoid valve, 8-the 3rd solenoid valve, 9-the 4th solenoid valve, 10-the 5th solenoid valve, 11-hand control valve, the lame car bumper control valve of 12-, 13-accumulator 13, the energy-conservation hole of 14-, 15-reduction valve, the 16-oil pump, 17-one-way valve, 18-second control port, 19-first control port, 20-input port, 21-output port, the 22-drain tap, 23-second control port, 24-first control port, the 25-input port, 26-output port, 27-drain tap, 28-second control port, 29-first control port, 30-input port, the 31-output port, 32-drain tap, 33-second control port, 34-first control port, 35-input port, 36-output port, the 37-drain tap, 38-second control port, 39-first control port, the 40-input port, 41-output port, 42-drain tap, the 43-control port, 44-input port, 45-output port, the 46-drain tap, the 47-hole of damming, 60-the 3rd circular groove, 61-valve body, the 62-spool, the 63-valve pocket, 64-first output port, 65-second circular groove, 66-first input end mouth, 67-first oil through, 70-second oil through, 71-the 3rd oil through, 72-four-way oilhole, 73-five-way oilhole, 74-the 6th oil through, 75-drain tap, 611-first circular groove, 612-first intercommunicating pore, 613-the 3rd output port, 614-second intercommunicating pore, 615-second output port, 616-second input port.
Embodiment
Embodiment, as shown in Figure 1, hydraulic control system when a kind of automatic speed-variator electric control system lost efficacy, comprise hand control valve 11, reduction valve 15 and five gear shift control valves and five solenoid valves, gear shift control valve of each electromagnetic valve, five gear shift control valves comprise the first gear shift control valve 1, the second gear shift control valve 2, the 3rd gear shift control valve 3, the 4th gear shift control valve 4 and the 5th gear shift control valve 5, each gear shift control valve is respectively equipped with input port, output port, first control port, second control port and drain tap, five solenoid valves comprise first solenoid valve 6, second solenoid valve 7, the 3rd solenoid valve 8, the 4th solenoid valve 9 and the 5th solenoid valve 10, five solenoid valves are normally open solenoid valve, the operation of first solenoid valve, 6 controls, the second gear shift control valve 2, the operation of second solenoid valve, 7 controls, the first gear shift control valve 1, the operation of the 3rd solenoid valve 8 controls the 3rd gear shift control valve 3, the operation of the 4th solenoid valve 9 controls the 4th gear shift control valve 4, the operation of the 5th solenoid valve 10 controls the 5th gear shift control valve 5.
Hydraulic control system is provided with lame car bumper control valve 12, the input port 44 of lame car bumper control valve 12 is communicated with the output port of reduction valve 15, the output port 45 of lame car bumper control valve 12 is communicated with second input port 616 of hand control valve 11, and the control port of five solenoid valves is communicated with the control port 43 of lame car bumper control valve 12 through an one-way valve 17 respectively.
The oil circuit that the control port 43 of lame car bumper control valve 12 is connected with five one-way valves 17 is provided with accumulator 13 and energy-conservation hole 14, the output port of reduction valve 15 is communicated with respectively with the control port of five solenoid valves, be respectively equipped with the hole 47 of damming on the control port of five solenoid valves and the oil circuit that the output port of reduction valve 15 is communicated with, the arrow among the figure is represented the flow direction of oil.
As shown in Figure 2, the input port 20 of the first gear shift control valve 1 is communicated with the 3rd output port 613 of hand control valve 11, first control port 19 of the first gear shift control valve 1 is communicated with first output port 64 of hand control valve 11, second control port 18 of the first gear shift control valve 1 is communicated with the control port of second solenoid valve 7, and the output port 21 of the first gear shift control valve 1 is communicated with the input port of clutch C1.
As shown in Figure 3, the input port 25 of the second gear shift control valve 2 is communicated with the 3rd output port 613 of hand control valve 11, first control port 24 of the second gear shift control valve 2 is communicated with the output port of lame car bumper control valve 12, second control port 23 of the second gear shift control valve 2 is communicated with the control port of first solenoid valve 6, and the output port 26 of the second gear shift control valve 2 is communicated with the input port of clutch C2.
As shown in Figure 4, the input port 30 of the 3rd gear shift control valve 3 is communicated with the 3rd output port 613 of hand control valve 11, second control port 28 of the 3rd gear shift control valve 3 is communicated with the control port of the 3rd solenoid valve 8, and the output port 31 of the 3rd gear shift control valve 3 is communicated with the input port of clutch C3.
As shown in Figure 5, the input port 35 of the 4th gear shift control valve 4 is communicated with the output port of oil pump 16, first control port 34 of the 4th gear shift control valve 4 is communicated with second output port 615 of hand control valve 11, second control port 33 of the 4th gear shift control valve 4 is communicated with the control port of the 4th solenoid valve 9, and the output port 36 of the 4th gear shift control valve 4 is communicated with the input port of break B1.
As shown in Figure 6, the input port 40 of the 5th gear shift control valve 5 is communicated with the output port of oil pump 16, first control port 39 of the 5th gear shift control valve 5 is communicated with the output port of lame car bumper control valve 12, second control port 38 of the 5th gear shift control valve 5 is communicated with the control port of the 5th solenoid valve 10, and the output port 41 of the 5th gear shift control valve 5 is communicated with the input port of clutch C4.
The drain tap 32 of the drain tap 22 of the first gear shift control valve 1, the drain tap 27 of the second gear shift control valve 2, the 3rd gear shift control valve 3, the drain tap 37 of the 4th gear shift control valve 4 and the drain tap 42 of the 5th gear shift control valve 5 are communicated with drain mast through spring non-return valve 18, the first input end mouth 66 of the input port of reduction valve 15 and hand control valve 11 is communicated with the output port of oil pump 16 respectively, and the drain tap 46 of lame car bumper control valve 12 and the drain tap 75 of hand control valve 11 are communicated with drain mast respectively.
As shown in Figure 7, under the situation of normal vehicle operation, during the solenoid valve proper functioning, the oil pressure of electromagnetic valve port acts on the control port 43 of lame car bumper control valve 12 as pilot pressure, the spool of lame car bumper control valve 12 moves, input port 44 is closed, and do not have pressure oil to exist this moment on lame car bumper control valve 12 and oil circuit that hand control valve 11 is connected, this moment the vehicle proper functioning.
As shown in Figure 8, when the automatic speed-variator electric control system of vehicle breaks down, electronic control unit no longer provides the control electric current to solenoid valve, this moment first solenoid valve 6, second solenoid valve 7, the 3rd solenoid valve 8, the 4th solenoid valve 9 and the 5th solenoid valve 10 quit work, the pilot pressure that acts on the lame car bumper control valve 12 disappears, the spool of the lame car bumper control valve 12 of this moment is under the spring force effect, return to initial position, input port 44 is opened, entered second input port 616 of hand control valve 11 and enter first control port 24 of the second gear shift control valve 2 and first control port 39 of the 5th gear shift control valve 5 from the oil pressure of reduction valve 15 output port 45 by lame car bumper control valve 12.
As Fig. 9, shown in Figure 10, hand control valve 11 comprises valve body 61, valve body 61 is provided with first input end mouth 66, second input port 616, first output port 64, second output port 615 and first intercommunicating pore 612 and second intercommunicating pore 614, first output port 64, second input port 616, second output port 615, second intercommunicating pore 614, the first input end mouth 66 and first intercommunicating pore 612 are successively set on the valve body 61, be communicated with the 3rd output port 613 between first intercommunicating pore 612 and second intercommunicating pore 614, be provided with spool 62 in the valve body 61, be provided with valve pocket 63 in the spool 62, drain tap 75 is arranged on valve pocket 63 1 ends, spool 62 is provided with six oil throughs that are communicated with valve pocket 63, be followed successively by first oil through 67 from a side away from first output port 64, second oil through 70, the 3rd oil through 71, four-way oilhole 72, five-way oilhole 73 and the 6th oil through 74, four-way oilhole 72, five-way oilhole 73 and the 6th oil through 74 are communicated with first output port 64 and valve pocket 63 selectively, spool 62 between first oil through 67 and second oil through 70 is provided with first circular groove 611, the spool 62 that spool 62 between the 3rd oil through 71 and the four-way oilhole 72 is provided with second circular groove, 65, the three oil throughs, 71 positions is provided with the 3rd circular groove 60.
Hand control valve comprises four positions: parking shifting-position P, reversing gear R, empty wagons gear N and the gear D that advances, and the relation such as the following table of these four gears and break and clutch, line expression bonding state, not line expression separated state:
As shown in figure 11, hand control valve 11 is in the R position of reversing gear, enter hand control valve 11 from the pressure oil of oil pump 16 from the first input end mouth 66 of hand control valve 11, as first circular groove 611 of control oil pressure through hand control valve 11, first intercommunicating pore 612 is from 613 outputs of the 3rd output port, enter the input port 20 of the first gear shift control valve 1 respectively, the input port 25 of the second gear shift control valve 2 and the input port 30 of the 3rd gear shift control valve 3, pressure oil from oil pump 16 directly enters the input port 35 of the 4th gear shift control valve 4 and the input port 40 of the 5th gear shift control valve 5, pressure oil from lame car bumper control valve 12 enters hand control valve 11 from second input port 616, export from second output port 615 through second circular groove 65 of hand control valve 11 as the control oil pressure, enter first control port 34 of the 4th gear shift control valve 4, this moment, the 4th gear shift control valve 4 was opened under the effect of first control port 34, break B1 combination, pressure oil from lame car bumper control valve 12 enters first control port 24 of the second gear shift control valve 2 and first control port 39 of the 5th gear shift control valve 5, the second gear shift control valve 2 and the 5th gear shift control valve 5 are opened, clutch C2 and clutch C4 combination, first output port 64 of hand control valve 11 is through five-way oilhole 73, valve pocket 63 is communicated with drain tap 75, first control port 19 of the first gear shift control valve 1 does not have pressure, clutch C1 is in separated state, clutch C3 also is in separated state, realized under the situation of automatically controlled inefficacy, to the control of the R that reverses gear.
As shown in figure 12, hand control valve is in N neutral gear, the first input end mouth 66 of hand control valve 11 and second input port 616 are closed, pressure oil from oil pump 16 and lame car bumper control valve 12 ends at hand control valve 11, first output port 64 is through four-way oilhole 72, valve pocket 63 is communicated with drain tap 75, second output port 615 is through the 3rd circular groove 60, second oil through 70, valve pocket 63 is communicated with drain tap 75, the 3rd output port 613 is through first intercommunicating pore 612, first oil through 67, valve pocket 63 is communicated with drain tap 75, this moment, 5 gear shift control valves cut out, 5 gearshift solenoid valves do not have electric current, can not produce pilot pressure, clutch C1, clutch C2, clutch C3, clutch C4 and break B1 are in separated state.
As shown in figure 13, hand control valve is in the D gear that advances, enter hand control valve 11 from the pressure oil of oil pump 16 from the first input end mouth 66 of hand control valve 11, as first circular groove 611 of control oil pressure through hand control valve 11, first intercommunicating pore 612 is from 613 outputs of the 3rd output port, enter the input port 20 of the first gear shift control valve 1 respectively, the input port 25 of the second gear shift control valve 2 and the input port 30 of the 3rd gear shift control valve 3, pressure oil from oil pump 16 directly enters the input port 35 of the 4th gear shift control valve 4 and the input port 40 of the 5th gear shift control valve 5, pressure oil from lame car bumper control valve 12 enters hand control valve 11 from second input port 616, export from first output port 64 through second circular groove 65 as the control oil pressure, enter first control port 19 of the first gear shift control valve 1, the first gear shift control valve 1 is opened, clutch C1 combination, pressure oil from lame car bumper control valve 12 enters first control port 24 of the second gear shift control valve 2 and first control port 39 of the 5th gear shift control valve 5, the second gear shift control valve 2 and the 5th gear shift control valve 5 are opened, clutch C2 and clutch C4 combination, second output port 615 of hand control valve 11 is communicated with drain tap 75, at this moment, first control port 34 of the 4th gear shift control valve 4 is communicated with drain tap 75, break B1 is in separated state, clutch C3 also is in separated state, therefore realized under the situation that automatical control system lost efficacy, the control of forward gear.
If vehicle is in the process of moving, the automatical control system catastrophic failure, this moment, all solenoid valves all quit work, and made speed changer can not enter lame car bumper pattern immediately and travel, but at first enter neutral that the mild then lame car bumper that enters travels.Accumulator makes the control port of lame car bumper control valve maintain oil pressure, lame car bumper control valve is in closed condition, hydraulic oil flows to fuel tank from throttle orifice gradually simultaneously, the oil pressure of the control port of lame car bumper control valve reduces gradually, when being lower than certain pressure, this valve resets under the effect of spring force, and lame car bumper control valve is opened, and enters lame car bumper pattern.
Because the 4th gear shift control valve is communicated with the output port of oil pump with the input port of the 5th gear shift control valve, without the hand control valve fuel feeding, clutch C4 and break B1 can be at any time in conjunction with other shifting elements, therefore, no matter enter forward gear or reverse gear from P or N, pressure oil is only supplied with a shifting element through hand control valve and is got final product, and has guaranteed the oil-filled time of shifting element, makes start-up time shorten.
Claims (17)
1. the hydraulic control system a when automatic speed-variator electric control system lost efficacy, comprise hand control valve (11), reduction valve (15), oil pump (16), several gear shift control valves and several solenoid valves, gear shift control valve of each electromagnetic valve, it is characterized in that: described hydraulic control system is provided with lame car bumper control valve (12), the control port of each solenoid valve is communicated with the control port (43) of lame car bumper control valve (12) through one-way valve respectively, the input port (44) of lame car bumper control valve (12) is communicated with the output port of reduction valve (15), and the output port (45) of lame car bumper control valve (12) is communicated with hand control valve (11).
2. the hydraulic control system when a kind of automatic speed-variator electric control system as claimed in claim 1 lost efficacy, it is characterized in that: described gear shift control valve comprises the first gear shift control valve (1), the second gear shift control valve (2), the 3rd gear shift control valve (3), the 4th gear shift control valve (4) and the 5th gear shift control valve (5), and each gear shift control valve is respectively equipped with input port, output port, first control port, second control port and drain tap.
3. the hydraulic control system when a kind of automatic speed-variator electric control system as claimed in claim 2 lost efficacy, it is characterized in that: the output port (45) of described lame car bumper control valve (12) is communicated with first control port (24) of the second gear shift control valve (2) and first control port (39) of the 5th gear shift control valve (5) respectively.
4. the hydraulic control system when a kind of automatic speed-variator electric control system as claimed in claim 3 lost efficacy is characterized in that: described the 4th gear shift control valve (4) and the input port of the 5th gear shift control valve (5) are communicated with the output port of oil pump (16) respectively.
5. the hydraulic control system when a kind of automatic speed-variator electric control system as claimed in claim 4 lost efficacy, it is characterized in that: the oil circuit between described lame car bumper control valve (12) and the one-way valve is provided with accumulator (13) and energy-conservation hole (14).
6. the hydraulic control system when losing efficacy as one of them described a kind of automatic speed-variator electric control system of claim 2-5, it is characterized in that: described hand control valve (11) is provided with first input end mouth (66), second input port (616), first output port (64), second output port (615), the 3rd output port (613) and drain tap (75), and first input end mouth (66) is communicated with oil pump (16).
7. the hydraulic control system when a kind of automatic speed-variator electric control system as claimed in claim 6 lost efficacy, it is characterized in that: described second input port (616) is communicated with the output port (45) of lame car bumper control valve (12).
8. the hydraulic control system when a kind of automatic speed-variator electric control system as claimed in claim 6 lost efficacy, it is characterized in that: first output port (64) of described hand control valve (11) is communicated with first control port (19) of the first gear shift control valve (1).
9. the hydraulic control system when a kind of automatic speed-variator electric control system as claimed in claim 6 lost efficacy, it is characterized in that: second output port (615) of described hand control valve (11) is communicated with first control port (34) of the 4th gear shift control valve (4).
10. the hydraulic control system when a kind of automatic speed-variator electric control system as claimed in claim 6 lost efficacy, it is characterized in that: the 3rd output port (613) of described hand control valve (11) is communicated with the input port of the first gear shift control valve (1), the second gear shift control valve (2) and the 3rd gear shift control valve (3) respectively.
The hydraulic control system when 11. a kind of automatic speed-variator electric control system as claimed in claim 6 lost efficacy, it is characterized in that: described hand control valve (11) comprises valve body (61), valve body (61) is provided with first intercommunicating pore (612) and second intercommunicating pore (614), first output port (64), second input port (616), second output port (615), second intercommunicating pore (614), first input end mouth (66) and first intercommunicating pore (612) are successively set on the valve body (61), and the 3rd output port (613) is communicated with first intercommunicating pore (612) and second intercommunicating pore (614).
The hydraulic control system when 12. a kind of automatic speed-variator electric control system as claimed in claim 11 lost efficacy, it is characterized in that: be provided with spool (62) in the described valve body (61), be provided with valve pocket (63) in the spool (62), drain tap (75) is arranged on valve pocket (63) one ends.
The hydraulic control system when 13. a kind of automatic speed-variator electric control system as claimed in claim 12 lost efficacy, it is characterized in that: described spool (62) is provided with six oil throughs that are communicated with valve pocket (63), is followed successively by first oil through (67), second oil through (70), the 3rd oil through (71), four-way oilhole (72), five-way oilhole (73) and the 6th oil through (74) from the side away from first output port (64).
The hydraulic control system when 14. a kind of automatic speed-variator electric control system as claimed in claim 13 lost efficacy, it is characterized in that: the spool (62) between described first oil through (67) and second oil through (70) is provided with first circular groove (611).
The hydraulic control system when 15. a kind of automatic speed-variator electric control system as claimed in claim 14 lost efficacy, it is characterized in that: the spool (62) between described the 3rd oil through (71) and the four-way oilhole (72) is provided with second circular groove (65).
The hydraulic control system when 16. a kind of automatic speed-variator electric control system as claimed in claim 15 lost efficacy, it is characterized in that: the spool (62) of described the 3rd oil through (71) position is provided with the 3rd circular groove (60).
The hydraulic control system when 17. a kind of automatic speed-variator electric control system as claimed in claim 1 lost efficacy, it is characterized in that: described solenoid valve is a normally open solenoid valve.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201010129014 CN101788051B (en) | 2010-03-22 | 2010-03-22 | Hydraulic control system used in failure of electric control system of automatic speed changer |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
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| CN 201010129014 CN101788051B (en) | 2010-03-22 | 2010-03-22 | Hydraulic control system used in failure of electric control system of automatic speed changer |
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| CN101788051A true CN101788051A (en) | 2010-07-28 |
| CN101788051B CN101788051B (en) | 2013-04-03 |
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| CN102644734A (en) * | 2012-04-12 | 2012-08-22 | 盛瑞传动股份有限公司 | Hydraulic control device of automatic speed changer |
| CN103410801A (en) * | 2013-07-31 | 2013-11-27 | 联合汽车电子有限公司 | Limp home oil circuit system of continuously variable transmission with wet clutch |
| CN103671897A (en) * | 2013-12-25 | 2014-03-26 | 盛瑞传动股份有限公司 | Safety control device in automatic transmission hydraulic control system |
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| CN106502089A (en) * | 2016-12-27 | 2017-03-15 | 河南森源重工有限公司 | A kind of redundancy control method of compression type garbage truck loading process |
| CN106838292A (en) * | 2016-12-26 | 2017-06-13 | 湖北航天技术研究院特种车辆技术中心 | A kind of self shifter hydraulic control system |
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| CN102152739A (en) * | 2011-02-28 | 2011-08-17 | 中国北方车辆研究所 | Emergent gear shift device |
| CN102644734A (en) * | 2012-04-12 | 2012-08-22 | 盛瑞传动股份有限公司 | Hydraulic control device of automatic speed changer |
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| CN102644734B (en) * | 2012-04-12 | 2014-12-24 | 盛瑞传动股份有限公司 | Hydraulic control device of automatic speed changer |
| CN103410801B (en) * | 2013-07-31 | 2016-09-28 | 联合汽车电子有限公司 | The limp-home oil piping system of the infinitely variable transmission containing wet clutch |
| CN103410801A (en) * | 2013-07-31 | 2013-11-27 | 联合汽车电子有限公司 | Limp home oil circuit system of continuously variable transmission with wet clutch |
| CN103671897A (en) * | 2013-12-25 | 2014-03-26 | 盛瑞传动股份有限公司 | Safety control device in automatic transmission hydraulic control system |
| CN103671897B (en) * | 2013-12-25 | 2015-11-18 | 盛瑞传动股份有限公司 | Safety control in a kind of hydraulic control system of automatic speed changer |
| CN105221740A (en) * | 2015-10-13 | 2016-01-06 | 哈尔滨东安汽车发动机制造有限公司 | A kind of automatic transmission limping Schema control oil circuit |
| CN105221740B (en) * | 2015-10-13 | 2017-04-19 | 哈尔滨东安汽车发动机制造有限公司 | Limping mode control oil way of automatic transmission |
| CN106838292A (en) * | 2016-12-26 | 2017-06-13 | 湖北航天技术研究院特种车辆技术中心 | A kind of self shifter hydraulic control system |
| CN106502089A (en) * | 2016-12-27 | 2017-03-15 | 河南森源重工有限公司 | A kind of redundancy control method of compression type garbage truck loading process |
| CN107975594A (en) * | 2017-12-28 | 2018-05-01 | 吉孚汽车技术(浙江)有限公司 | The hydraulic system of automatic transmission |
| CN107975594B (en) * | 2017-12-28 | 2023-09-19 | 浙江万里扬智能传动有限公司 | Hydraulic system of automatic transmission |
| CN109899511A (en) * | 2019-04-26 | 2019-06-18 | 南京劲力传动技术有限公司 | Hydraulic control system with limping function and the automatic gear-box using it |
| CN109899511B (en) * | 2019-04-26 | 2024-03-22 | 南京劲力变速器科技有限公司 | Hydraulic control system with limp function and automatic gearbox using same |
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Inventor after: Liu Xiangwu Inventor after: Zhou Liting Inventor after: Yu Xintao Inventor after: Song Tingbin Inventor after: Liang Jian Inventor after: Guo Mingzhong Inventor after: Li Weiqiang Inventor before: Liu Xiangwu Inventor before: Zhou Liting Inventor before: Yu Xintao Inventor before: Song Yanbin Inventor before: Liang Jian Inventor before: Guo Mingzhong Inventor before: Li Weiqiang |