CN104061193B - The drum brake hydraulic system of multi-axle heavy type engineering machinery - Google Patents
The drum brake hydraulic system of multi-axle heavy type engineering machinery Download PDFInfo
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Abstract
The present invention provides the drum brake hydraulic system of a kind of multi-axle heavy type engineering machinery, including entering oil control valve group, electrohydraulic proportional control valve group, switching ball and filter assembly, and the first oil circuit, the second oil circuit, the 3rd oil circuit, the 4th oil circuit and the 5th oil circuit.This drum brake hydraulic system, adopts accumulator can meet low discharge and inputs the output of big flow, it is achieved that the braking of multi-axle heavy type engineering machinery and responding rapidly to of brake release, save the cost adopting high-volume hydraulic pump simultaneously；The electric ratio input adopting brake-cylinder pressure controls, it is achieved that the big braking moment output of drum brake, makes the braking axle quantity of multi-axle heavy type engineering machinery to reduce, shortens overall dimensions of a car accordingly, reduces vehicle turn radius.
Description
Technical field
The present invention relates to the Hydraulic Field of construction machinery industry, be specifically related to the drum brake hydraulic system of a kind of multi-axle heavy type engineering machinery.
Background technology
The brake actuator of existing multi-axle heavy type engineering machinery is generally divided into caliper disc and drum-type two kinds.
Caliper disc braking adopts hydraulic braking, and brake force is bigger, it is necessary to arrangement space little, but relatively costly, so using less in multi-axle heavy type engineering machinery.
The commonly used air braking system of drum brake, but owing to air pressure is less and air cell size restriction, the brake force that air braking system finally produces at wheel place is generally less than normal, therefore generally requires the function of car load service brake and parking braking when more braking axle could meet heavy haul transport for multi-axle heavy type engineering machinery air braking system.Add product cost so on the one hand, limit the min. turning radius of vehicle shortest length and vehicle on the other hand.
Summary of the invention
It is an object of the invention to solve prior art Problems existing, the drum brake hydraulic system of a kind of multi-axle heavy type engineering machinery is provided, adopt the electric ratio input control design case of accumulator and brake-cylinder pressure, not only achieve the braking of multi-axle heavy type engineering machinery and responding rapidly to of brake release, save the cost adopting high-volume hydraulic pump simultaneously, owing to this hydraulic system can input the output of big flow by low discharge, achieve the big braking moment output of drum brake, the braking axle quantity making multi-axle heavy type engineering machinery can reduce, shorten overall dimensions of a car accordingly, reduce turn inside diameter, save cost.
In order to reach above-mentioned technical purpose, the present invention by the following technical solutions:
A kind of drum brake hydraulic system of multi-axle heavy type engineering machinery, including:
Enter oil control valve group, electrohydraulic proportional control valve group, switching ball and filter assembly, the first oil circuit, the second oil circuit, the 3rd oil circuit, the 4th oil circuit and the 5th oil circuit,
The first described oil circuit as described enter oil control valve group oil supply gallery, the second described oil circuit as by described enter the passage that connects with the oil-in of described electrohydraulic proportional control valve group of the actuator port of oil control valve group, the 3rd described oil circuit as the control port of described electrohydraulic proportional control valve group to the oil supply gallery of checking cylinder, the 4th described oil circuit as the emptying passage of described electrohydraulic proportional control valve group, the 5th described oil circuit as described enter oil control valve group drainback passage；
Described oil control valve group of entering includes the first check valve, air relief valve, choke valve, accumulator and parking electromagnetic valve, described the first check valve, the oil inlet P mouth of air relief valve are sequentially connected in series on the first described oil circuit with oil-out A mouth, choke valve, described accumulator parallel connection accesses described first oil circuit, the oil-in of described parking electromagnetic valve accesses described first oil circuit, oil return opening accesses described 5th oil circuit, second state of the first state that described parking electromagnetic valve realizes electric and dead electricity, in the first state, hydraulic oil enters the second oil circuit from the first oil circuit；In the second state, hydraulic oil enters the 5th oil circuit from the first oil circuit, and the hydraulic fluid port L mouth of described air relief valve accesses described 5th oil circuit；
Described electrohydraulic proportional control valve group includes electricity proportional pressure-reducing valve, second check valve, the two-way plug-in valve of electricity proportional pressure-relief valve control, electricity proportional pressure control valve, the two-way plug-in valve that first safety overflow valve and electricity proportional pressure control valve and the first safety overflow valve control, the oil-in A mouth of the two-way plug-in valve of described electricity proportional pressure-relief valve control is all connected and accesses described second oil circuit with the oil inlet P mouth of described electricity proportional pressure-reducing valve with Stress control mouth F mouth, it is connected to described second check valve between oil-out B mouth and the work oil-in A mouth of described electricity proportional pressure-reducing valve of the two-way plug-in valve of described electricity proportional pressure-relief valve control；The described electricity oil inlet P mouth of proportional pressure control valve, the oil inlet P mouth of described first safety overflow valve are connected with work oil-in A mouth and the Stress control mouth F mouth of described electricity proportional pressure control valve and the two-way plug-in valve of the first safety overflow valve control, and are connected with the oil-out B mouth of the two-way plug-in valve of electricity proportional pressure-relief valve control；The oil return inlet T mouth of described electricity proportional pressure control valve, the oil return inlet T mouth of described first safety overflow valve is connected with the oil return inlet T mouth of described electricity proportional pressure-reducing valve, and access described 4th oil circuit, electrohydraulic proportional control valve group can realize the first state of vehicle driving brake release and the second state of vehicle driving braking, first state of vehicle driving brake release, the pressure of the control port of described electrohydraulic proportional control valve group is identical with the work oil-in A mouth pressure of described electricity proportional pressure-reducing valve, second state of vehicle driving braking, the pressure of the control port of described electrohydraulic proportional control valve group is identical with the oil inlet P mouth pressure of described electricity proportional pressure control valve；
Described switching ball is connected with filter assembly and is accessed described 3rd oil circuit, and described filter assembly is near checking cylinder.
Preferred as such scheme, described filter assembly includes filter and 4 check valves, realize the bi-directional filtered of described 3rd oil circuit, the oil-out of two of which check valve is connected with the oil-in of filter, the oil-in of two check valves is connected into described 3rd oil circuit, and the oil-in of two other check valve is connected with the oil-out of filter, the oil-out of two other check valve is connected into described 3rd oil circuit.
Preferred as such scheme, also includes manual parking ball valve, and the oil-in of described manual parking ball valve accesses on described first oil circuit between described air relief valve and choke valve, and the oil return opening of described manual parking ball valve accesses described 5th oil circuit.
Preferred as such scheme, also includes manual pump, and described manual pump accesses between described switching ball and filter assembly on described 3rd oil circuit.
Preferred as such scheme, also include the first pressure switch and the second pressure switch, the first described pressure switch parallel connection accesses between described accumulator and the described parking electromagnetic valve on described first oil circuit, on the second described pressure switch parallel connection described 3rd oil circuit of access between described filter assembly and checking cylinder.
Preferred as such scheme, also include the second safety overflow valve, the oil-in of described second safety overflow valve access the described accumulator on described first oil circuit and described enter oil control valve group actuator port between, the oil return opening of described second safety overflow valve accesses described 5th oil circuit.
Preferred as such scheme, also includes pressure transducer, and described pressure transducer parallel connection accesses on the oil circuit that described manual pump is connected with described 3rd oil circuit.
Preferred as such scheme, the maximum pressure of described air relief valve restriction hydraulic oil is 200bar.
Preferred as such scheme, described first pressure switch, produce the signal of telecommunication, described second pressure switch when the input pressure of electrohydraulic proportional control valve group is lower than 170bar, produce the signal of telecommunication when the input pressure of checking cylinder is lower than 160bar.
The drum brake hydraulic system of a kind of multi-axle heavy type engineering machinery provided by the invention has the advantage that compared to existing technology
1, the electric ratio input control design case of accumulator and brake-cylinder pressure is adopted, not only achieve the startup of multi-axle heavy type engineering machinery and responding rapidly to of service brake, save the cost adopting high-volume hydraulic pump simultaneously, owing to this hydraulic system can input the output of big flow by low discharge, achieve the big braking moment output of drum brake, make the braking axle quantity of multi-axle heavy type engineering machinery to reduce, shorten overall dimensions of a car accordingly, reduce turn inside diameter, save cost.
2, filter assembly realizes brake circuit is carried out the effect of forward and reverse filtration, and 4 check valves realize the function of Fixed-Filter oil-in and oil-out, and filter realizes the function that brake circuit is filtered.
3, manually parking ball valve can realize the parking braking of vehicle.
4, manually pump realizes emergency vehicle and releases the function of parking braking.
5, by the input pressure of the first pressure switch monitor in real time electrohydraulic proportional control valve group, pressure lower than or produce the signal of telecommunication control signal lamp when exceeding certain threshold values and open or close, it is achieved monitoring the Realtime Alerts to input pressure；By the pressure of the second pressure switch monitor in real time checking cylinder, pressure lower than or produce the signal of telecommunication when exceeding certain threshold values and control Brake lamp and open or close.
6, this hydraulic braking system pressure security defencive function is realized by safety overflow valve.
7, the function of monitor in real time vehicle brake pressure is realized by pressure transducer.
Accompanying drawing explanation
In order to be illustrated more clearly that the embodiment of the present invention or technical scheme of the prior art, the accompanying drawing used required in embodiment or description of the prior art will be briefly described below, apparently, accompanying drawing in the following describes is only some embodiments of the present invention, for those of ordinary skill in the art, under the premise not paying creative work, it is also possible to obtain other accompanying drawing according to these accompanying drawings.
Fig. 1 is the hydraulic schematic diagram of the drum brake hydraulic system of multi-axle heavy type engineering machinery of the present invention；
Fig. 2 is the hydraulic schematic diagram entering oil control valve group in Fig. 1；
Fig. 3 is the hydraulic schematic diagram of electrohydraulic proportional control valve group in Fig. 1；
Fig. 4 is the structural representation of Fig. 1 middle filtrator assembly.
Detailed description of the invention
Below in conjunction with the accompanying drawing of the present invention, technical scheme is clearly and completely described, it is clear that described embodiment is only a part of embodiment of the present invention, rather than whole embodiments.Based on the embodiment in the present invention, the every other embodiment that those of ordinary skill in the art obtain under not making creative work premise, broadly fall into the scope of protection of the invention.
As it is shown in figure 1, the present invention provides the drum brake hydraulic system of a kind of multi-axle heavy type engineering machinery, including:
Enter oil control valve group 1, electrohydraulic proportional control valve group 2, manual parking ball valve 3, switching ball 4, filter assembly 5, manual pump 6, the first oil circuit the 7, second oil circuit the 8, the 3rd oil circuit the 9, the 4th oil circuit 10 and the 5th oil circuit 11,
The first described oil circuit 7 as described enter oil control valve group 1 oil supply gallery, the second described oil circuit 8 as by described enter the passage that connects with the oil inlet P mouth of described electrohydraulic proportional control valve group 2 of the actuator port A mouth of oil control valve group 1, the 3rd described oil circuit 9 as the control port Z mouth of described electrohydraulic proportional control valve group 2 to the oil supply gallery of checking cylinder 12, the 4th described oil circuit 10 as the emptying passage of described electrohydraulic proportional control valve group 2, the 5th described oil circuit 11 as described enter oil control valve group 1 drainback passage；
As shown in Figure 2, described oil control valve group 1 of entering includes the first check valve 13, air relief valve 14, choke valve 15, accumulator the 16, first pressure switch the 17, second safety overflow valve 18 and parking electromagnetic valve 19, described the first check valve 13, the oil inlet P mouth of air relief valve 14 and oil-out A mouth, choke valve 15 are sequentially connected in series on the first described oil circuit 7, and it is 200bar that described air relief valve 14 limits the maximum pressure of hydraulic oil；Described accumulator 16 is in parallel accesses described first oil circuit 7, the oil-in of the second safety overflow valve 18 access the described accumulator 16 on described first oil circuit 7 and described enter oil control valve group 1 actuator port A between, the oil return opening of described second safety overflow valve 18 access described 5th oil circuit 11；Between the first described pressure switch 17 described accumulator 16 and described parking electromagnetic valve 19 accessed on described first oil circuit 7 in parallel, produce the signal of telecommunication when the input pressure of electrohydraulic proportional control valve group 2 is lower than 170bar；The oil-in of described parking electromagnetic valve 19 accesses described first oil circuit 7, oil return opening accesses described 5th oil circuit 11, second state of the first state that described parking electromagnetic valve 19 realizes electric and dead electricity, in the first state, hydraulic oil enters the second oil circuit 8 from the first oil circuit 7；In the second state, hydraulic oil enters the 5th oil circuit 11 from the first oil circuit 7, and the hydraulic fluid port L mouth of described air relief valve 14 accesses described 5th oil circuit 11；
As shown in Figure 3, described electrohydraulic proportional control valve group 2 includes electricity proportional pressure-reducing valve 20, second check valve 21, the two-way plug-in valve 22 of electricity proportional pressure-relief valve control, electricity proportional pressure control valve 23, the two-way plug-in valve 25 that first safety overflow valve 24 and electricity proportional pressure control valve and the first safety overflow valve control, the oil-in A mouth of the two-way plug-in valve 22 of described electricity proportional pressure-relief valve control is all connected and accesses described second oil circuit 8 with the oil inlet P mouth of described electricity proportional pressure-reducing valve 20 with Stress control mouth F mouth, it is connected to described second check valve 21 between oil-out B mouth and the work oil-in A mouth of described electricity proportional pressure-reducing valve 20 of the two-way plug-in valve 22 of described electricity proportional pressure-relief valve control；The described electricity oil inlet P mouth of proportional pressure control valve 23, the oil inlet P mouth of described first safety overflow valve 24 are connected with work oil-in A mouth and the Stress control mouth F mouth of described electricity proportional pressure control valve and the two-way plug-in valve 25 of the first safety overflow valve control, and are connected with the oil-out B mouth of the two-way plug-in valve 22 of electricity proportional pressure-relief valve control；The oil return inlet T mouth of described electricity proportional pressure control valve 23, the oil return inlet T mouth of described first safety overflow valve 24 is connected with the oil return inlet T mouth of described electricity proportional pressure-reducing valve 20, and access described 4th oil circuit 10, electrohydraulic proportional control valve group 2 can realize the first state of vehicle driving brake release and the second state of vehicle driving braking, first state of vehicle driving brake release, the pressure of the control port Z of described electrohydraulic proportional control valve group 2 is identical with the work oil-in A mouth pressure of described electricity proportional pressure-reducing valve 20, second state of vehicle driving braking, the pressure of the control port Z of described electrohydraulic proportional control valve group 2 is identical with the oil inlet P mouth pressure of described electricity proportional pressure control valve 23；
As it is shown in figure 1, the oil-in of described manual parking ball valve 3 accesses on described first oil circuit 7 between described air relief valve 14 and choke valve 15, the oil return opening of described manual parking ball valve 3 accesses described 5th oil circuit 11.
Described switching ball 4 is connected with filter assembly 5 and is accessed described 3rd oil circuit 9, and described filter 9 assembly is near checking cylinder 12.Described filter assembly 5 includes filter 26 and 4 check valves 27, realize the bi-directional filtered of described 3rd oil circuit 9, the oil-out of two of which check valve 27 is connected with the oil-in Fe of filter 26, the oil-in of two check valves 27 is connected into described 3rd oil circuit 9, and the oil-in of two other check valve 27 is connected with the oil-out Fa of filter 26, the oil-out of two other check valve 27 is connected into described 3rd oil circuit 9.
Described manual pump 6 accesses between described switching ball 4 and filter assembly 5 on described 3rd oil circuit 9.
Preferably, also including the second pressure switch 28, the second described pressure switch 28 is in parallel to be accessed on described 3rd oil circuit 9 between described filter assembly 5 and checking cylinder 12, produces the signal of telecommunication when the input pressure of checking cylinder 12 is lower than 160bar.
Preferably, also including pressure transducer 29, described pressure transducer 29 is in parallel to be accessed on the oil circuit that described manual pump 6 is connected with described 3rd oil circuit 9.
The drum brake hydraulic system of a kind of multi-axle heavy type engineering machinery provided by the invention, adopt the electric ratio input control design case of accumulator and brake-cylinder pressure, not only achieve the braking of multi-axle heavy type engineering machinery and responding rapidly to of brake release, save the cost adopting high-volume hydraulic pump simultaneously, owing to this hydraulic system can input the output of big flow by low discharge, achieve the big braking moment output of drum brake, the braking axle quantity making multi-axle heavy type engineering machinery can reduce, shorten overall dimensions of a car accordingly, reduce vehicle turn radius；Filter assembly realizes brake circuit is carried out the effect of forward and reverse filtration, and 4 check valves realize the function of Fixed-Filter oil-in and oil-out, and filter realizes the function that brake circuit is filtered；Manually parking ball valve can realize the parking braking of vehicle；Manually pump realizes emergency vehicle and releases the function of parking braking；By the input pressure of the first pressure switch monitor in real time electrohydraulic proportional control valve group, pressure lower than or produce the signal of telecommunication control signal lamp when exceeding certain threshold values and open or close, it is achieved monitoring the Realtime Alerts to input pressure；By the pressure of the second pressure switch monitor in real time checking cylinder, pressure lower than or produce the signal of telecommunication when exceeding certain threshold values and control Brake lamp and open or close；This hydraulic braking system pressure security defencive function is realized by safety overflow valve；The function of monitor in real time vehicle brake pressure is realized by pressure transducer.
The operation principle of the drum brake hydraulic system of a kind of multi-axle heavy type engineering machinery provided by the invention is:
When vehicle is in parked state, hydraulic power source is to entering oil control valve group output pressure, so this drum-type hydraulic brakes and checking cylinder are in pressure-less state, now the plunger rod extension elongation of checking cylinder is the shortest, the brake force of drum brake is maximum, and car load is in parked state.
After vehicle launch, hydraulic power source starts to entering the flow that oil control valve group 1 provides stable.Hydraulic oil through entering the first check valve 13 of being internally integrated of oil control valve group 1, air relief valve 14 and after choke valve 15, provide flow, accumulator 16 to start topping up to accumulator 16, simultaneously parking electromagnetic valve 19 electric so that the pressure releasing braking can normally be set up.Hydraulic oil enters the oil inlet P mouth of electrohydraulic proportional control valve group 2 through the actuator port A mouth entering oil control valve group 1.Hydraulic oil from P mouth realizes exporting to the big flow of checking cylinder by the two-way plug-in valve 22 of electricity proportional pressure-reducing valve 20 and electricity proportional pressure-relief valve control, controls output pressure simultaneously.Electricity proportional pressure-reducing valve 20 is the pilot control element of the two-way plug-in valve 22 of electricity proportional pressure-relief valve control, the size of electricity proportional pressure-reducing valve 20 output pressure is controlled by the size of external control electric current, the pressure of two-way plug-in valve 22 output of final restriction electricity proportional pressure-relief valve control, and according to the flow of pressure flow curve output correspondence, after opening car releasing braking, the external control electric current of electricity proportional pressure-reducing valve 20 and electricity proportional pressure control valve reaches maximum, namely the output pressure of electricity proportional pressure-reducing valve 20 reaches maximum, the oil pressure relief of electricity proportional pressure control valve 23 reaches maximum, now the pressure of the control port Z mouth of described electrohydraulic proportional control valve group 2 is identical with the work oil-in A mouth pressure of described electricity proportional pressure-reducing valve 20, namely the output pressure of electrohydraulic proportional control valve group 2 reaches maximum.Hydraulic oil enters the 3rd oil circuit 9 by the control port Z mouth of described electrohydraulic proportional control valve group 2 after first oil circuit the 7, second oil circuit 8, switching ball 4 is in opening, checking cylinder is entered by switching ball 4 and filter assembly 5, checking cylinder is made to be in maximum pressure state, now the plunger rod extension elongation of checking cylinder is the longest, the brake force of drum brake is minimum, and car load is in releasing braking (releasing parking) state.
Cargo driving process carries out service brake, now the external control electric current of electricity proportional pressure-reducing valve 20 and electricity proportional pressure control valve 23 reduces, then the oil pressure relief of electricity proportional pressure control valve 23 reduces, compartmentation due to the second check valve 21, the two-way plug-in valve 25 that the pressure at checking cylinder place only controls by electricity proportional pressure control valve 23 and electricity proportional pressure control valve and the first safety overflow valve is controlled, now the pressure of the control port Z mouth of described electrohydraulic proportional control valve group 2 is identical with the oil inlet P mouth pressure of described electricity proportional pressure control valve 23, hydraulic oil after electrohydraulic proportional control valve group 2 release flows back to fuel tank through the 4th oil circuit 10.When electric current is minimized, the output pressure of electrohydraulic proportional control valve group 2 is 0, and checking cylinder is in pressure-less state, and the plunger rod extension elongation of checking cylinder is the shortest, and the brake force of drum brake is maximum.
Parking braking, closes manual parking ball valve 3, and hydraulic oil is directly entered the 5th oil circuit 11 after the first oil circuit 7, and vehicle can realize manual parking operation.
Emergent releasing parking braking, opens manual pump 6, closing switch ball valve 4, and the hydraulic oil that manual pump is got is directly entered the 3rd oil circuit 9 and controls checking cylinder 12, and vehicle can realize meeting an urgent need and manually release parking.
The above; being only the specific embodiment of the present invention, but protection scope of the present invention is not limited thereto, any those familiar with the art is in the technical scope that the invention discloses; change can be readily occurred in or replace, all should be encompassed within protection scope of the present invention.Therefore, protection scope of the present invention should be as the criterion with described scope of the claims.
Claims (9)
1. the drum brake hydraulic system of a multi-axle heavy type engineering machinery, it is characterised in that including:
Enter oil control valve group, electrohydraulic proportional control valve group, switching ball and filter assembly, the first oil circuit, the second oil circuit, the 3rd oil circuit, the 4th oil circuit and the 5th oil circuit,
The first described oil circuit as described enter oil control valve group oil supply gallery, the second described oil circuit as by described enter the passage that connects with the oil-in of described electrohydraulic proportional control valve group of the actuator port of oil control valve group, the 3rd described oil circuit as the control port of described electrohydraulic proportional control valve group to the oil supply gallery of checking cylinder, the 4th described oil circuit as the emptying passage of described electrohydraulic proportional control valve group, the 5th described oil circuit as described enter oil control valve group drainback passage；
Described oil control valve group of entering includes the first check valve, air relief valve, choke valve, accumulator and parking electromagnetic valve, described the first check valve, the oil inlet P mouth of air relief valve are sequentially connected in series on the first described oil circuit with oil-out A mouth, choke valve, described accumulator parallel connection accesses described first oil circuit, the oil-in of described parking electromagnetic valve accesses described first oil circuit, oil return opening accesses described 5th oil circuit, second state of the first state that described parking electromagnetic valve realizes electric and dead electricity, in the first state, hydraulic oil enters the second oil circuit from the first oil circuit；In the second state, hydraulic oil enters the 5th oil circuit from the first oil circuit, and the hydraulic fluid port L mouth of described air relief valve accesses described 5th oil circuit；
Described electrohydraulic proportional control valve group includes electricity proportional pressure-reducing valve, second check valve, the two-way plug-in valve of electricity proportional pressure-relief valve control, electricity proportional pressure control valve, the two-way plug-in valve that first safety overflow valve and electricity proportional pressure control valve and the first safety overflow valve control, the oil-in A mouth of the two-way plug-in valve of described electricity proportional pressure-relief valve control is all connected and accesses described second oil circuit with the oil inlet P mouth of described electricity proportional pressure-reducing valve with Stress control mouth F mouth, it is connected to described second check valve between oil-out B mouth and the work oil-in A mouth of described electricity proportional pressure-reducing valve of the two-way plug-in valve of described electricity proportional pressure-relief valve control；The described electricity oil inlet P mouth of proportional pressure control valve, the oil inlet P mouth of described first safety overflow valve are connected with work oil-in A mouth and the Stress control mouth F mouth of described electricity proportional pressure control valve and the two-way plug-in valve of the first safety overflow valve control, and are connected with the oil-out B mouth of the two-way plug-in valve of electricity proportional pressure-relief valve control；The oil return inlet T mouth of described electricity proportional pressure control valve, the oil return inlet T mouth of described first safety overflow valve is connected with the oil return inlet T mouth of described electricity proportional pressure-reducing valve, and access described 4th oil circuit, electrohydraulic proportional control valve group can realize the first state of vehicle driving brake release and the second state of vehicle driving braking, first state of vehicle driving brake release, the pressure of the control port of described electrohydraulic proportional control valve group is identical with the work oil-in A mouth pressure of described electricity proportional pressure-reducing valve, second state of vehicle driving braking, the pressure of the control port of described electrohydraulic proportional control valve group is identical with the oil inlet P mouth pressure of described electricity proportional pressure control valve；
Described switching ball is connected with filter assembly and is accessed described 3rd oil circuit, and described filter assembly is near checking cylinder.
2. the drum brake hydraulic system of multi-axle heavy type engineering machinery according to claim 1, it is characterized in that, described filter assembly includes filter and 4 check valves, realize the bi-directional filtered of described 3rd oil circuit, the oil-out of two of which check valve is connected with the oil-in of filter, the oil-in of two check valves is connected into described 3rd oil circuit, and the oil-in of two other check valve is connected with the oil-out of filter, the oil-out of two other check valve is connected into described 3rd oil circuit.
3. the drum brake hydraulic system of multi-axle heavy type engineering machinery according to claim 1, it is characterized in that, also include manual parking ball valve, the oil-in of described manual parking ball valve accesses on described first oil circuit between described air relief valve and choke valve, and the oil return opening of described manual parking ball valve accesses described 5th oil circuit.
4. the drum brake hydraulic system of multi-axle heavy type engineering machinery according to claim 1, it is characterised in that also including manual pump, described manual pump accesses between described switching ball and filter assembly on described 3rd oil circuit.
5. the drum brake hydraulic system of multi-axle heavy type engineering machinery according to claim 1, it is characterized in that, also include the first pressure switch and the second pressure switch, the first described pressure switch parallel connection accesses between described accumulator and the described parking electromagnetic valve on described first oil circuit, on the second described pressure switch parallel connection described 3rd oil circuit of access between described filter assembly and checking cylinder.
6. the drum brake hydraulic system of multi-axle heavy type engineering machinery according to claim 1, it is characterized in that, also include the second safety overflow valve, the oil-in of described second safety overflow valve access the described accumulator on described first oil circuit and described enter oil control valve group actuator port between, the oil return opening of described second safety overflow valve accesses described 5th oil circuit.
7. the drum brake hydraulic system of multi-axle heavy type engineering machinery according to claim 4, it is characterised in that also including pressure transducer, described pressure transducer parallel connection accesses on the oil circuit that described manual pump is connected with described 3rd oil circuit.
8. the drum brake hydraulic system of multi-axle heavy type engineering machinery according to claim 1, it is characterised in that the maximum pressure of described air relief valve restriction hydraulic oil is 200bar.
9. the drum brake hydraulic system of multi-axle heavy type engineering machinery according to claim 5, it is characterized in that, described first pressure switch, the signal of telecommunication is produced when the input pressure of electrohydraulic proportional control valve group is lower than 170bar, described second pressure switch, produces the signal of telecommunication when the input pressure of checking cylinder is lower than 160bar.
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| WO2012056489A1 (en) * | 2010-10-25 | 2012-05-03 | トヨタ自動車株式会社 | Brake control device |
| CN202557520U (en) * | 2012-04-01 | 2012-11-28 | 徐州徐工铁路装备有限公司 | Two-way brake control system of beam transportation vehicle |
| CN102720711B (en) * | 2012-06-29 | 2015-05-20 | 武汉船用机械有限责任公司 | Automatic-switch type load sensing hydraulic system |
| CN202863430U (en) * | 2012-09-21 | 2013-04-10 | 秦皇岛天业通联重工股份有限公司 | Hydraulic braking control system for mining dump-truck |
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2013
- 2013-06-27 CN CN201310263268.XA patent/CN104061193B/en active Active
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