CN205047552U - Hydraulic control system and paver - Google Patents
Hydraulic control system and paver Download PDFInfo
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- CN205047552U CN205047552U CN201520699858.1U CN201520699858U CN205047552U CN 205047552 U CN205047552 U CN 205047552U CN 201520699858 U CN201520699858 U CN 201520699858U CN 205047552 U CN205047552 U CN 205047552U
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Abstract
The utility model relates to a hydraulic control system and paver, wherein, hydraulic control system is used for controlling floating and the hydraulic pressure helping hand of execution unit, and it includes ratio pressure reducing valve, throttle speed governing unit and first switching -over valve, and when execution unit was in floating state, two work oil cavity of execution unit were linked together through first switching -over valve, and the pressure oil circuit passes through two work oil cavity benefit oil of ratio pressure reducing valve to execution unit, when execution unit needed the hydraulic pressure helping hand, two work oil cavity of execution unit broke off through first switching -over valve mutually, the pressure oil circuit pass through ratio pressure reducing valve to with the communicating work oil cavity fuel feeding of an actuator port. The utility model discloses ratio pressure reducing valve among the hydraulic control system execution unit float with hydraulic pressure helping hand operating mode under play oil and the proportion pressure regulating effect of mending respectively, realized that a valve is dual -purpose, simplified hydraulic system.
Description
Technical field
The utility model relates to engineering machinery field, particularly relates to a kind of hydraulic control system and paver.
Background technique
In engineering machinery field, paver is a kind of construction equipment being widely used in Freeway and the various material paving operation of surface layer.Wherein screed is as a groundwork device of paver, its Main Function be the mixing such as bituminous concrete, Stabilized Soil material spreader is flattened, shaping and pre-compacted.
Paver screed promotes hydraulic system has material impact to paver service behaviour and pavement spread quality.Paver paving operation process comprises starting, pave and stop three phases, stop and the starting stage at paver, stressed the changing of screed can cause screed to rise or decline, road surface is caused to produce bulge or groove, for addressing this problem, current most of screed promotes hydraulic system and all keeps lift cylinder to be in blocking to avoid screed generation displacement in paver parking and starting stage.But when paver normally paves, screed is in quick condition, lift cylinder rodless cavity and rod chamber all communicate with fuel tank, because oil tank liquid level is lower than lift cylinder mounting point, lift cylinder there will be emptying phenomenon, produce negative pressure, therefore in paver parking and starting-up process, even if lift cylinder switches to blocking by quick condition, there is negative pressure owing to inhaling sky in lift cylinder rodless cavity or rod chamber, building pressure needs certain hour, and screed still can produce displacement up or down, cause paving concrete pavement arch camber or impression, affect pavement quality; In addition, the paver screed adopted at present promotes hydraulic system when screed locking, mostly arranges oil hydraulic circuit in addition and controls, and cause hydraulic system complicated, cost is higher.
Model utility content
For overcoming above technological deficiency, the technical problem that the utility model solves is to provide a kind of hydraulic control system and paver, can simplify hydraulic system.
For solving the problems of the technologies described above, the utility model provides a kind of hydraulic control system, for controlling floating and hydraulic booster of performance element, it comprises proportional pressure-reducing valve, throttle grverning unit and the first selector valve, first actuator port of the first selector valve and the second actuator port communicate with two working oil chambers of performance element respectively, the filler opening of the first selector valve and return opening are communicated and are communicated with oil return circuit by throttle grverning unit, the filler opening of proportional pressure-reducing valve is communicated with pressure oil circuit, and oil outlet communicates with the first actuator port of the first selector valve; When performance element is in quick condition, two working oil chambers of performance element are connected by the first selector valve, and pressure oil circuit passing ratio reduction valve is to two working oil chamber repairings of performance element; When performance element needs hydraulic booster, two working oil chambers of performance element are disconnected mutually by the first selector valve, and pressure oil circuit passing ratio reduction valve is to the working oil chamber fuel feeding communicated with the first actuator port.
Preferably, throttle grverning unit is throttle orifice or series flow control valve.
Further, hydraulic control system also comprises the first one-way valve between oil outlet and the first actuator port being connected on proportional pressure-reducing valve, and the filler opening of the first one-way valve communicates with the oil outlet of proportional pressure-reducing valve, and oil outlet communicates with the first actuator port.
Further, hydraulic control system also comprises pressure transducer, the pressure-measuring point of pressure transducer is arranged on the oil circuit between the oil outlet of the first one-way valve and the first actuator port, and the force value that proportional pressure-reducing valve can detect according to pressure transducer changes delivery pressure.
Further, performance element comprises lift cylinder, and the rod chamber of lift cylinder and rodless cavity communicate with the first actuator port and the second actuator port respectively as two working oil chambers of performance element.
Further, hydraulic control system also comprises electronic one-way valve, second selector valve, reduction valve, one-way throttle valve and there is the second one-way valve of back pressure, the filler opening of the second selector valve and return opening communicate with pressure oil circuit and oil return circuit respectively, 3rd actuator port of the second selector valve all communicates with the filler opening of reduction valve and the oil outlet of the second one-way valve, the oil outlet of reduction valve and the filler opening of the second one-way valve all communicate with the rodless cavity of lift cylinder, 4th actuator port of the second selector valve communicates with the first hydraulic fluid port of one-way throttle valve, second hydraulic fluid port of one-way throttle valve communicates with the filler opening of electronic one-way valve, the oil outlet of electronic one-way valve communicates with the rod chamber of lift cylinder, when lift cylinder is in contraction state, pressure oil circuit by the second selector valve and the one-way throttle valve rod chamber fuel feeding to lift cylinder, the rodless cavity of lift cylinder by the second one-way valve and the second selector valve to oil return circuit oil return, lift cylinder be in stretch out state time, pressure oil circuit by the second selector valve and the reduction valve rodless cavity fuel feeding to lift cylinder, the rod chamber of lift cylinder by electronic one-way valve, one-way throttle valve and the second selector valve to oil return circuit oil return, when lift cylinder is in blocking, pressure oil circuit by the second selector valve and the reduction valve rodless cavity fuel feeding to lift cylinder, the rod chamber of the unidirectional locked lift cylinder of electronic one-way valve.
Preferably, the second selector valve is three-position four-way electromagnetic directional valve or the 3-position 4-way hydraulicchange-over valve of meta N-type function.
The utility model still further provides a kind of paver, and this paver has above-mentioned hydraulic control system.
Further, performance element comprises lift cylinder, the rod chamber of lift cylinder and rodless cavity communicate with the first actuator port and the second actuator port respectively as two working oil chambers of performance element, and the piston rod of lift cylinder connects the large arm of this paver to promote or to reduce the screed of paver.
Thus, based on technique scheme, the utility model provides a kind of hydraulic control system, this hydraulic control system is by Set scale reduction valve, when performance element is in quick condition, two working oil chambers of performance element are connected by the first selector valve, throttle grverning unit forms system back pressure on oil return circuit, pressure oil circuit passing ratio reduction valve is to two working oil chamber repairings of performance element, the return line of two working oil chamber connections has back pressure, two working oil chambers form certain malleation, emptying phenomenon produces negative pressure to prevent performance element from occurring in location free procedure, reduce or eliminate performance element produce displacement when stopping operation and affect operation quality, when performance element needs hydraulic booster, two working oil chambers of performance element are disconnected mutually by the first selector valve, and pressure oil circuit passing ratio reduction valve provides required pressure oil to the working oil chamber communicated with the first actuator port, ensure operation quality, therefore the proportional pressure-reducing valve in the utility model hydraulic control system floats at performance element and plays repairing and ratio pressure regulation effect respectively under hydraulic booster operating mode, achieves a valve dual-purpose, simplifies hydraulic system.The paver that the utility model provides correspondingly also has above-mentioned useful technique effect.
Accompanying drawing explanation
Accompanying drawing described herein is used to provide further understanding of the present utility model, and form a application's part, schematic description and description of the present utility model, only for explaining the utility model, is not formed improper restriction of the present utility model.In the accompanying drawings:
Fig. 1 is the hydraulic schematic diagram of the utility model hydraulic control system one embodiment.
Embodiment
Below by drawings and Examples, the technical solution of the utility model is described in further detail.
Embodiment of the present utility model is for the ease of having further description to design of the present utility model, the technical problem solved, the technical characteristics forming technological scheme and the technique effect that brings.It should be noted that, the explanation for these mode of executions is not formed restriction of the present utility model.In addition, just can mutually combine as long as the technical characteristics related in mode of execution of the present utility model described below does not form conflict each other.
In description of the present utility model, it will be appreciated that, term " " center ", " longitudinal direction ", " transverse direction ", " front ", " afterwards ", " left side ", " right side ", " vertically ", " level ", " top ", " end ", " interior ", orientation or the position relationship of the instruction such as " outward " are based on orientation shown in the drawings or position relationship, only the utility model and simplified characterization for convenience of description, instead of indicate or imply that the device of indication or element must have specific orientation, with specific azimuth configuration and operation, therefore the restriction to the utility model protection domain can not be interpreted as.
Because existing paver screed in paving process can produce displacement up or down, road surface is caused to occur arch camber or impression, and hydraulic system is complicated, manufacture cost is high, the utility model devises a kind of hydraulic control system, this hydraulic control system is by Set scale reduction valve, when performance element is in quick condition, pressure oil circuit passing ratio reduction valve is to two working oil chamber repairings of performance element, the return line of two working oil chamber connections has back pressure, two working oil chambers form certain malleation, prevent from performance element location free procedure, occurring that emptying phenomenon produces negative pressure, reduce or eliminate performance element produce displacement when stopping operation and affect operation quality, when performance element needs hydraulic booster, pressure oil circuit passing ratio reduction valve provides required pressure oil to the working oil chamber communicated with the first actuator port, ensures operation quality, proportional pressure-reducing valve in the utility model hydraulic control system floats at performance element and plays repairing and ratio pressure regulation effect respectively under hydraulic booster operating mode, achieves a valve dual-purpose, simplifies hydraulic system.
In a schematic embodiment of the utility model hydraulic control system, as shown in Figure 1, this hydraulic control system is for controlling floating and hydraulic booster of performance element, it comprises solenoid directional control valve or pilot operated directional control valve that proportional pressure-reducing valve 4, throttle grverning unit 3 and the first selector valve 7, first selector valve 7 are preferably two-position four-way.First actuator port A1 of the first selector valve 7 and the second actuator port B1 communicates with two working oil chambers of performance element respectively, the oil inlet P 1 of the first selector valve 7 and oil return inlet T 1 are communicated and are led to by throttle grverning unit 3 and oil return circuit T-phase, the filler opening of proportional pressure-reducing valve 4 is communicated with pressure oil circuit P, and oil outlet communicates with the first actuator port A1 of the first selector valve 7;
When performance element is in quick condition, two working oil chambers of performance element are connected by the first selector valve 7, and pressure oil circuit P passing ratio reduction valve 4 is to two working oil chamber repairings of performance element;
When performance element needs hydraulic booster, two working oil chambers of performance element are disconnected by the first selector valve 7 phase, and pressure oil circuit P passing ratio reduction valve 4 is to the working oil chamber fuel feeding communicated with the first actuator port A1.
In this schematic embodiment, by Set scale reduction valve 4, when performance element is in quick condition, first actuator port A1 of the first selector valve 7 and oil inlet P 1 communicate, second actuator port B1 and oil return inlet T 1 communicate, and oil inlet P 1 and oil return inlet T 1 communicate, two working oil chambers of performance element are connected by the first selector valve 7, throttle grverning unit 3 forms system back pressure on oil return circuit, pressure oil circuit P passing ratio reduction valve 4 is to two working oil chamber repairings of performance element, the return line of two working oil chamber connections has back pressure, two working oil chambers form certain malleation, emptying phenomenon produces negative pressure to prevent performance element from occurring in location free procedure, reduce or eliminate performance element produce displacement when stopping operation and affect operation quality, when performance element needs hydraulic booster, first actuator port A1 of the first selector valve 7 and oil inlet P 1 disconnect, second actuator port B1 and oil return inlet T 1 disconnect, two working oil chambers of performance element are disconnected by the first selector valve 7 phase, pressure oil circuit P passing ratio reduction valve 4 provides required pressure oil to the working oil chamber communicated with the first actuator port A1, ensures operation quality, therefore the proportional pressure-reducing valve 4 in the present embodiment floats at performance element and plays repairing and ratio pressure regulation effect respectively under hydraulic booster operating mode, achieves a valve dual-purpose, simplifies hydraulic system.Wherein, throttle grverning unit 3 is preferably throttle orifice or series flow control valve, and throttle orifice and series flow control valve are conventional throttle grverning mechanism, and be easy to obtain, save manufacture cost, certain throttle grverning unit also can select relief valve or reduction valve to replace.
As the improvement to above-described embodiment, as shown in Figure 1, hydraulic control system also comprises the first one-way valve 5 between oil outlet and the first actuator port A1 being connected on proportional pressure-reducing valve 4, the filler opening of the first one-way valve 5 communicates with the oil outlet of proportional pressure-reducing valve 4, and oil outlet communicates with the first actuator port A1.First one-way valve 5 can prevent pressure oil from flowing to proportional pressure-reducing valve 4, avoids proportional pressure-reducing valve 4 to be subject to the interference of other oil circuits, protection proportional pressure-reducing valve 4.Further, hydraulic control system also comprises pressure transducer 6, the pressure-measuring point of pressure transducer 6 is arranged on the oil circuit between the oil outlet of the first one-way valve 5 and the first actuator port A1, and the force value that proportional pressure-reducing valve 4 can detect according to pressure transducer 6 changes delivery pressure.The pressure-measuring point of pressure transducer 6 is arranged on the oil circuit between the oil outlet of the first one-way valve 5 and the first actuator port A1, pressure transducer 6 can the delivery pressure of accurate detection ratio reduction valve 4, and then the force value that can detect according to pressure transducer 6 delivery pressure that changes proportional pressure-reducing valve 4 carrys out the pressure demand of satisfied different operating mode.
The hydraulic control system of above-described embodiment is particularly useful for the control of paver screed, as shown in Figure 1, performance element comprises lift cylinder 1 and 13, the rod chamber of lift cylinder 1 and 13 and rodless cavity communicate with the first actuator port A1 and the second actuator port B1 respectively as two working oil chambers of performance element, lift cylinder 1 with 13 piston rod be connected paver large arm to promote or to reduce the screed of paver, when screed is in quick condition, passing ratio reduction valve 4 is to the rod chamber of lift cylinder 1 and 13 and rodless cavity repairing, and throttle grverning unit 3 is set on oil return circuit T, set up certain back pressure, emptying phenomenon produces negative pressure to prevent lift cylinder 1 and 13 in ironing-board float process from occurring, reduce or eliminate lift cylinder 1 and 13 in paver stop-start process produce displacement and cause impression and the arch camber on road surface, proportional pressure-reducing valve 4 in this hydraulic control system can carry out proportion adjustment when providing hydraulic booster to screed to lift cylinder 1 and 13 rod chamber pressure simultaneously, screed equivalent weight and laminated material are adapted, ensure paving thickness, achieve a valve dual-purpose, simplify hydraulic system.Certainly, the hydraulic control system of above-described embodiment can also be applied in Other Engineering mechanically, does not enumerate at this.
Further, paver is applied to for the hydraulic control system of above-described embodiment, hydraulic control system also comprises electronic one-way valve 2 and 12, second selector valve 8, reduction valve 9, one-way throttle valve 11 and there is the second one-way valve 10 of back pressure, second selector valve 8 is preferably three-position four-way electromagnetic directional valve or the 3-position 4-way hydraulicchange-over valve of meta N-type function, the oil inlet P 2 of the second selector valve 8 and oil return inlet T 2 are led to pressure oil circuit P and oil return circuit T-phase respectively, 3rd actuator port A2 of the second selector valve 8 all communicates with the oil outlet of the filler opening of reduction valve 9 and the second one-way valve 10, the oil outlet of reduction valve 9 and the filler opening of the second one-way valve 10 all with lift cylinder 1, the rodless cavity of 13 communicates, 4th actuator port B2 of the second selector valve 8 communicates with the first hydraulic fluid port of one-way throttle valve 11, second hydraulic fluid port of one-way throttle valve 11 communicates with the filler opening of electronic one-way valve 2 and 12, wherein, one-way throttle valve 11 comprises the 3rd one-way valve 11-1 and throttle valve 11-2 that are connected in parallel, it should be noted that, first hydraulic fluid port of one-way throttle valve 11 communicates with the filler opening of the 3rd one-way valve 11-1, second hydraulic fluid port communicates with the oil outlet of the 3rd one-way valve 11-1, the oil outlet of electronic one-way valve 2 and 12 communicates with the rod chamber of lift cylinder 1 and 13,
When lift cylinder 1 and 13 is in contraction state, oil inlet P 2 and the 4th actuator port B2 of the second selector valve 8 communicate, oil return inlet T 2 and the 3rd actuator port A2 communicate, pressure oil circuit P is by the rod chamber fuel feeding of the 3rd one-way valve 11-1 in the second selector valve 8 and one-way throttle valve 11 to lift cylinder 1 and 13, the rodless cavity of lift cylinder 1 and 13 by the second one-way valve 10 and the second selector valve 8 to oil return circuit T oil return, second one-way valve 10 is provided with certain back pressure, ensures that lift cylinder 1 and 13 steadily shrinks;
Lift cylinder 1 and 13 be in stretch out state time, oil inlet P 2 and the 3rd actuator port A2 of the second selector valve 8 communicate, oil return inlet T 2 and the 4th actuator port B2 communicate, pressure oil circuit P is by the second selector valve 8 and the reduction valve 9 rodless cavity fuel feeding to lift cylinder 1 and 13, the rod chamber of lift cylinder 1 and 13 by the throttle valve 11-2 in electronic one-way valve 2 and 12, one-way throttle valve 11 and the second selector valve 8 to oil return circuit T oil return, throttle valve 11-2 forms certain back pressure, ensures that lift cylinder 1 and 13 steadily stretches out;
When lift cylinder 1 and 13 is in blocking, pressure oil circuit P is by the second selector valve 8 and the reduction valve 9 rodless cavity fuel feeding to lift cylinder 1 and 13, the rodless cavity of lift cylinder 1 and 13 keeps certain pressure value, rodless cavity is locked, lift cylinder 1 and 13 is avoided to shrink, the rod chamber of the unidirectional locked lift cylinder 1 and 13 of electronic one-way valve 2 and 12, prevents lift cylinder 1 and 13 from stretching out.
The embodiment of this hydraulic control system is not setting up under the prerequisite of establishing new oil circuit, by arranging reduction valve 9 and the second one-way valve 10 on the oil circuit be connected with lift cylinder rodless cavity in parallel, just can realize lift cylinder 1 and 13 rodless cavity oil return when shrinking, when stretching out rodless cavity repairing and in locking time rodless cavity locked, make hydraulic control system structure simple, compact further.
The utility model still further provides a kind of paver, and it has the hydraulic control system of above-described embodiment.Due to the proportional pressure-reducing valve in the utility model hydraulic control system performance element float and hydraulic booster operating mode under play repairing and ratio pressure regulation effect respectively, achieve a valve dual-purpose, simplify hydraulic system, correspondingly, the utility model paver also has above-mentioned useful technique effect.
Specifically, paver has large arm and screed, as shown in Figure 1, performance element comprises lift cylinder 1 and 13, the rod chamber of lift cylinder 1 and 13 and rodless cavity communicate with the first actuator port A1 and the second actuator port B1 respectively as two working oil chambers of performance element, lift cylinder 1 with 13 piston rod be connected paver large arm to promote or to reduce the screed of paver, when the piston rod of lift cylinder 1 and 13 upwards shrinks, screed promotes; When the piston rod of lift cylinder 1 and 13 stretches out downwards, screed declines.
Thus, the working principle of hydraulic control system under different operating mode of the utility model paver one embodiment is as follows:
When paver screed promotes, the electromagnet Y1.1 of the second selector valve 8 is energized, Y1.2 no electric circuit, electromagnet Y2.1 and Y2.2 of electronic one-way valve 2 and 12, the electromagnet m1 of proportional pressure-reducing valve 4, the equal no electric circuit of electromagnet Y3 of the first selector valve 7, the high pressure oil of oil feeding line P by oil inlet P 2 to the four actuator port B2 of the second selector valve 8 through one-way valve 11-1, electronic one-way valve 2 and 12 enters the rod chamber of lift cylinder 1 and 13 respectively, lift cylinder 1 with 13 rodless cavity be connected with the 3rd actuator port A2 of the second selector valve 8 by one-way valve 10, 3rd actuator port A2 of the second selector valve 8 is communicated with oil return circuit T-phase through oil return inlet T 2, the rod chamber of lift cylinder 1 and 13 is high pressure oil, rodless cavity is low pressure oil, screed upwards promotes, wherein one-way valve 10 sets certain back pressure, ensure that screed steadily upwards promotes.
When paver screed declines, the electromagnet Y1.2 of the second selector valve 8 is energized, Y1.1 no electric circuit, electromagnet Y2.1 and Y2.2 of electronic one-way valve 2 and 12 is energized, the electromagnet m1 of proportional pressure-reducing valve 4 and the equal no electric circuit of electromagnet Y3 of the first selector valve 7, lift cylinder 1 with 13 rod chamber be connected with throttle valve 11-2 with 12 by electronic one-way valve 2, throttle valve 11-2 is connected through oil return inlet T 2 and oil return circuit T-phase by the 4th actuator port B2 of the second selector valve 8, screed declines under Gravitative Loads, throttle valve 11-2 forms certain back pressure, control screed steadily to decline, the pressure oil of oil feeding line P is through oil inlet P 2 to the three actuator port A2 of the second selector valve 8, again by the rodless cavity repairing of reduction valve 9 to lift cylinder 1 and 13.
When paver normal operation, screed is in quick condition, the equal no electric circuit of electromagnet Y1.1 and Y1.2 of the second selector valve 8, electromagnet Y2.1 and Y2.2 of electronic one-way valve 2 and 12, the electromagnet Y3 of the first selector valve 7 is all energized, the electromagnet m1 of proportional pressure-reducing valve 4 is according to the given corresponding current value of the pressure requirements of being monitored by pressure transducer 6, first selector valve 7 by lift cylinder 1 with 13 rod chamber be connected with rodless cavity, and be communicated with oil return circuit T-phase by throttle grverning unit 3, the pressure oil of oil feeding line P is through proportional pressure-reducing valve 4 and the first one-way valve 5, communicate with the rod chamber of lift cylinder 1 and 13 and rodless cavity respectively under the effect of electronic one-way valve 2 and 12, in ironing-board float process, proportional pressure-reducing valve 4 can with certain pressure value to the rod chamber of lift cylinder 1 and 13 and rodless cavity repairing, throttle grverning unit 3 sets up certain back pressure, prevent lift cylinder in ironing-board float process from going out 1 and 13 and occur that emptying phenomenon produces negative pressure, reduce or eliminate lift cylinder 1 and 13 in paver stop-start process produce displacement and cause impression and the arch camber on road surface.
When paver screed needs to provide hydraulic booster, the electromagnet Y3 of the first selector valve 7, the equal no electric circuit of electromagnet Y1.1 and Y1.2 of the second selector valve 8, electromagnet Y2.1 and Y2.2 of electronic one-way valve 2 and 12 is energized, the electromagnet m1 of proportional pressure-reducing valve 4 is according to the given corresponding current value of the pressure requirements of being monitored by pressure transducer 6, the pressure oil of oil feeding line P regulates after pressure by the first one-way valve 5 through proportional pressure-reducing valve 4, electronic one-way valve 2 and 12 enters the rod chamber of lift cylinder 1 and 13, the rod chamber of lift cylinder 1 and 13 remains the force value adapted with laminated material, the rodless cavity of lift cylinder 1 and lift cylinder 13 is by the second one-way valve 10, 3rd actuator port A2 of the second selector valve 8 is communicated with to oil return inlet T 2 mouthfuls with oil return circuit T-phase, the power that lift cylinder 1 and 13 makes screed be subject to upwards, alleviate screed weight, ensure paving thickness.
When paver screed locking, the electromagnet Y1.1 no electric circuit of the second selector valve 8, Y1.2 energising, electromagnet Y2.1 and Y2.2 of the electromagnet Y3 of the first selector valve 7, electronic one-way valve 2 and 12, the equal no electric circuit of electromagnet m1 of proportional pressure-reducing valve 4, electronic one-way valve 2 and 12 is by locked for the fluid of the rod chamber of lift cylinder 1 and 13, prevent screed from declining, the pressure oil of oil feeding line P after the second selector valve 8 reduces pressure with reduction valve 9 with lift cylinder 1 with 13 rodless cavity be connected, lift cylinder 1 and 13 rodless cavity keeps certain pressure value, avoids screed upwards to promote.
The embodiment more than combined is described in detail for mode of execution of the present utility model, but the utility model is not limited to described mode of execution.Such as electronic one-way valve 2 and 12 also can replace with Pilot operated check valve.For a person skilled in the art, when not departing from principle of the present utility model and connotation, multiple change, amendment are carried out to these mode of executions, equivalence is replaced and modification still falls within protection domain of the present utility model.
Claims (9)
1. a hydraulic control system, for controlling floating and hydraulic booster of performance element, it is characterized in that, comprise proportional pressure-reducing valve (4), throttle grverning unit (3) and the first selector valve (7), first actuator port (A1) of described first selector valve (7) and the second actuator port (B1) communicate with two working oil chambers of described performance element respectively, the filler opening (P1) of described first selector valve (7) and return opening (T1) are communicated and are communicated with oil return circuit (T) by described throttle grverning unit (3), the filler opening of described proportional pressure-reducing valve (4) is communicated with pressure oil circuit (P), oil outlet communicates with first actuator port (A1) of described first selector valve (7),
When described performance element is in quick condition, two working oil chambers of described performance element are connected by described first selector valve (7), and described pressure oil circuit (P) passing ratio reduction valve (4) is to two working oil chamber repairings of described performance element;
When described performance element needs hydraulic booster, two working oil chambers of described performance element are disconnected mutually by described first selector valve (7), described pressure oil circuit (P) by described proportional pressure-reducing valve (4) to the working oil chamber fuel feeding communicated with described first actuator port (A1).
2. hydraulic control system according to claim 1, is characterized in that, throttle grverning unit (3) is throttle orifice or series flow control valve.
3. hydraulic control system according to claim 1, it is characterized in that, also comprise the first one-way valve (5) between oil outlet and described first actuator port (A1) being connected on described proportional pressure-reducing valve (4), the filler opening of described first one-way valve (5) communicates with the oil outlet of described proportional pressure-reducing valve (4), and oil outlet communicates with described first actuator port (A1).
4. hydraulic control system according to claim 3, it is characterized in that, also comprise pressure transducer (6), the pressure-measuring point of described pressure transducer (6) is arranged on the oil circuit between the oil outlet of described first one-way valve (5) and described first actuator port (A1), and the force value that described proportional pressure-reducing valve (4) can detect according to described pressure transducer (6) changes delivery pressure.
5. the hydraulic control system according to any one of Claims 1 to 4, it is characterized in that, described performance element comprises lift cylinder (1,13), and the rod chamber of described lift cylinder (1,13) and rodless cavity communicate with described first actuator port (A1) and described second actuator port (B1) respectively as two working oil chambers of described performance element.
6. hydraulic control system according to claim 5, it is characterized in that, also comprise electronic one-way valve (2, 12), second selector valve (8), reduction valve (9), one-way throttle valve (11) and there is second one-way valve (10) of back pressure, the filler opening (P2) of described second selector valve (8) and return opening (T2) communicate with described pressure oil circuit (P) and described oil return circuit (T) respectively, 3rd actuator port (A2) of described second selector valve (8) all communicates with the filler opening of described reduction valve (9) and the oil outlet of described second one-way valve (10), the oil outlet of described reduction valve (9) and the filler opening of described second one-way valve (10) all with described lift cylinder (1, 13) rodless cavity communicates, 4th actuator port (B2) of described second selector valve (8) communicates with the first hydraulic fluid port of described one-way throttle valve (11), second hydraulic fluid port of described one-way throttle valve (11) and described electronic one-way valve (2, 12) filler opening communicates, described electronic one-way valve (2, 12) oil outlet and described lift cylinder (1, 13) rod chamber communicates,
When described lift cylinder (1,13) is in contraction state, described pressure oil circuit (P) by described second selector valve (8) and described one-way throttle valve (11) the rod chamber fuel feeding to described lift cylinder (1,13), the rodless cavity of described lift cylinder (1,13) by described second one-way valve (10) and described second selector valve (8) to described oil return circuit (T) oil return;
Described lift cylinder (1,13) be in stretch out state time, described pressure oil circuit (P) by described second selector valve (8) and described reduction valve (9) the rodless cavity fuel feeding to described lift cylinder (1,13), the rod chamber of described lift cylinder (1,13) by described electronic one-way valve (2,12), described one-way throttle valve (11) and described second selector valve (8) to described oil return circuit (T) oil return;
When described lift cylinder (1,13) is in blocking, described pressure oil circuit (P) by described second selector valve (8) and described reduction valve (9) the rodless cavity fuel feeding to described lift cylinder (1,13), the rod chamber of the unidirectional locked described lift cylinder (1,13) of described electronic one-way valve (2,12).
7. hydraulic control system according to claim 6, is characterized in that, the three-position four-way electromagnetic directional valve that described second selector valve (8) is meta N-type function or 3-position 4-way hydraulicchange-over valve.
8. a paver, is characterized in that, has the hydraulic control system described in any one of claim 1 ~ 7.
9. paver according to claim 8, it is characterized in that, described performance element comprises lift cylinder (1,13), the rod chamber of described lift cylinder (1,13) and rodless cavity communicate with described first actuator port (A1) and described second actuator port (B1) respectively as two working oil chambers of described performance element, and the piston rod of described lift cylinder (1,13) connects the large arm of described paver to promote or to reduce the screed of described paver.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201520699858.1U CN205047552U (en) | 2015-09-11 | 2015-09-11 | Hydraulic control system and paver |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201520699858.1U CN205047552U (en) | 2015-09-11 | 2015-09-11 | Hydraulic control system and paver |
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| CN205047552U true CN205047552U (en) | 2016-02-24 |
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| CN201520699858.1U Expired - Fee Related CN205047552U (en) | 2015-09-11 | 2015-09-11 | Hydraulic control system and paver |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106523446A (en) * | 2015-09-11 | 2017-03-22 | 徐工集团工程机械股份有限公司 | Hydraulic control system and paver |
| CN107120326A (en) * | 2017-07-10 | 2017-09-01 | 南京英达公路养护车制造有限公司 | A kind of levelling oil cylinder hydraulic control system of loading head |
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2015
- 2015-09-11 CN CN201520699858.1U patent/CN205047552U/en not_active Expired - Fee Related
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN106523446A (en) * | 2015-09-11 | 2017-03-22 | 徐工集团工程机械股份有限公司 | Hydraulic control system and paver |
| CN107120326A (en) * | 2017-07-10 | 2017-09-01 | 南京英达公路养护车制造有限公司 | A kind of levelling oil cylinder hydraulic control system of loading head |
| CN107120326B (en) * | 2017-07-10 | 2018-06-15 | 南京英达公路养护车制造有限公司 | A kind of levelling oil cylinder hydraulic control system of loading head |
| WO2018137723A1 (en) * | 2017-07-10 | 2018-08-02 | 南京英达公路养护车制造有限公司 | Material collector leveling cylinder hydraulic control system |
| US10590627B2 (en) | 2017-07-10 | 2020-03-17 | Nanjing Freetech Road Maintenance Vehicle Manufacturing Corporation | Hydraulic control system of leveling oil cylinder of loading head |
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