CN104061193A - Drum brake hydraulic system for multi-shaft heavy engineering machinery - Google Patents
Drum brake hydraulic system for multi-shaft heavy engineering machinery Download PDFInfo
- Publication number
- CN104061193A CN104061193A CN201310263268.XA CN201310263268A CN104061193A CN 104061193 A CN104061193 A CN 104061193A CN 201310263268 A CN201310263268 A CN 201310263268A CN 104061193 A CN104061193 A CN 104061193A
- Authority
- CN
- China
- Prior art keywords
- valve
- oil
- oil circuit
- pressure
- mouth
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Landscapes
- Valves And Accessory Devices For Braking Systems (AREA)
- Braking Systems And Boosters (AREA)
Abstract
The invention provides a drum brake hydraulic system for a multi-shaft heavy engineering machinery, which comprises an oil inlet control valve bank, an electro-hydraulic proportional control valve bank, a switch ball valve, a filter assembly, a first oil way, a second oil way, a third oil way, a fourth oil way and a fifth oil way. Through the adoption of an energy accumulator, the drum brake hydraulic system can meet the requirements for small-flow input and large-flow output, implements rapid response to brake and brake-off of the multi-shaft heavy engineering machinery and simultaneously saves cost generated by adopting a large-flow hydraulic pump; due to adoption of electric proportional input control of the pressure of a brake cylinder, the drum brake hydraulic system implements large-braking-torque output of the drum brake, enables the number of brake axles of the multi-shaft heavy engineering machinery to be decreased, correspondingly shortens the size of a finished automobile and reduces a turning radius of a vehicle.
Description
Technical field
The present invention relates to the Hydraulic Field of construction machinery industry, be specifically related to a kind of drum brake hydraulic system of multi-axle heavy type engineering machinery.
Background technique
The brake actuator of existing multi-axle heavy type engineering machinery is generally divided into two kinds of caliper disc and drum-types.
Caliper disc braking adopts hydraulic braking, and braking force is larger, and the arrangement space needing is little, but cost is higher, so use less in multi-axle heavy type engineering machinery.
Drum brake generally adopts air braking system, but because air pressure is less and air cell size restriction, the braking force that air braking system finally produces at wheel place is generally less than normal, the function of car load service brake and parking braking while therefore often needing more braking axle to meet heavy haul transport for multi-axle heavy type engineering machinery air braking system.Increase product cost so on the one hand, limited on the other hand the min. turning radius of vehicle shortest length and vehicle.
Summary of the invention
The object of the invention is to solve the problem that prior art exists, a kind of drum brake hydraulic system of multi-axle heavy type engineering machinery is provided, adopt the electric ratio input control design of accumulator and brake-cylinder pressure, the braking of multi-axle heavy type engineering machinery and the rapid response that braking is removed are not only realized, saved the cost that adopts high-volume hydraulic pump simultaneously, because this hydraulic system can be inputted large flow output by small flow, realize the large braking moment output of drum brake, the braking axle quantity of multi-axle heavy type engineering machinery can be reduced, corresponding shortening overall dimensions of a car, reduce turn inside diameter, save cost.
In order to reach above-mentioned technical purpose, the present invention by the following technical solutions:
A drum brake hydraulic system for multi-axle heavy type engineering machinery, comprising:
Oil-feed 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 is as the oil supply gallery of described oil-feed control valve group, the second described oil circuit is as the passage that the actuator port of described oil-feed control valve group is communicated with the filler opening of described electrohydraulic proportional control valve group, the 3rd described oil circuit arrives the oil supply gallery of master cylinder as the control port of described electrohydraulic proportional control valve group, the 4th described oil circuit is as the emptying passage of described electrohydraulic proportional control valve group, and the 5th described oil circuit is as the drainback passage of described oil-feed control valve group;
Described oil-feed control valve group comprises the first one-way valve, reduction valve, throttle valve, accumulator and parking solenoid valve, the first described one-way valve, the oil inlet P mouth of reduction valve and oil outlet A mouth, throttle valve are connected on the first described oil circuit successively, described the first oil circuit of described accumulator access in parallel, the filler opening of described parking solenoid valve accesses described the first oil circuit, return opening accesses described the 5th oil circuit, the first state that described parking solenoid valve is realized electricly and the second state of dead electricity, at the first state, hydraulic oil enters the second oil circuit from the first oil circuit; At the second state, hydraulic oil enters the 5th oil circuit from the first oil circuit, and unloading port's L mouth of described reduction valve accesses described the 5th oil circuit;
Described electrohydraulic proportional control valve group comprises electric proportional pressure-reducing valve, the second one-way 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 of the first safety overflow valve and electric proportional pressure control valve and the first safety overflow valve control, the filler opening A mouth of the two-way plug-in valve of described electric proportional pressure-relief valve control is all connected with the oil inlet P mouth of described electric proportional pressure-reducing valve and accesses described the second oil circuit with pressure control mouth F mouth, between the work filler opening A mouth of the oil outlet B mouth of the two-way plug-in valve of described electric proportional pressure-relief valve control and described electric proportional pressure-reducing valve, be connected with described the second one-way valve, the oil inlet P mouth of described electric proportional pressure control valve, the oil inlet P mouth of described the first safety overflow valve are connected with work filler opening A mouth and the pressure control mouth F mouth of the two-way plug-in valve of the first safety overflow valve control with described electric proportional pressure control valve, and are connected with the oil outlet B mouth of the two-way plug-in valve of electric proportional pressure-relief valve control, the oil return inlet T mouth of described electric proportional pressure control valve, the oil return inlet T mouth of described the first safety overflow valve is connected with the oil return inlet T mouth of described electric proportional pressure-reducing valve, and access described the 4th oil circuit, electrohydraulic proportional control valve group can realize the first state of vehicle driving braking releasing and the second state of vehicle driving braking, the first state that vehicle driving braking is removed, the pressure of the control port of described electrohydraulic proportional control valve group is identical with the filler opening A mouth pressure of described electric proportional pressure-reducing valve, the 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 electric proportional pressure control valve,
Described switching ball is connected with filter assembly and is accessed described the 3rd oil circuit, and described filter assembly is near master cylinder.
As such scheme preferably, described filter assembly comprises filter and 4 one-way valves, realize the bi-directional filtered of described the 3rd oil circuit, the wherein oil outlet of two one-way valves and the filler opening of filter is connected, the filler opening of two one-way valves is connected into described the 3rd oil circuit, the filler opening of two other one-way valve is connected with the oil outlet of filter, the oil outlet of two other one-way valve is connected into described the 3rd oil circuit.
As such scheme preferably, also comprise manual parking ball valve, the filler opening of described manual parking ball valve accesses between described the above reduction valve of the first oil circuit and throttle valve, the return opening of described manual parking ball valve accesses described the 5th oil circuit.
As such scheme preferably, also comprise hand pump, described hand pump accesses between the described switching ball and filter assembly on described the 3rd oil circuit.
As such scheme preferably, also comprise the first pressure switch and the second pressure switch, between described accumulator and described parking solenoid valve on described described the first oil circuit of the first pressure switch access in parallel, between described the second pressure switch described the 3rd the above filter assembly of oil circuit of access in parallel and master cylinder.
As such scheme preferably, also comprise the second safety overflow valve, the filler opening of described the second safety overflow valve accesses between the described accumulator and the actuator port of described oil-feed control valve group on described the first oil circuit, and the return opening of described the second safety overflow valve accesses described the 5th oil circuit.
As such scheme preferably, also comprise pressure transducer, on the oil circuit that the described described hand pump of pressure transducer access in parallel is connected with described the 3rd oil circuit.
As such scheme preferably, the pressure maximum of described reduction valve restriction hydraulic oil is 200bar.
As such scheme preferably, described the first pressure switch, produces electrical signal at the incoming pressure of electrohydraulic proportional control valve group during lower than 170bar, described the second pressure switch produces electrical signal during lower than 160bar at the incoming pressure of master cylinder.
The drum brake hydraulic system of a kind of multi-axle heavy type engineering machinery provided by the invention has the following advantages compared to existing technology:
1, adopt the electric ratio input control design of accumulator and brake-cylinder pressure, the startup of multi-axle heavy type engineering machinery and the rapid response of service brake are not only realized, saved the cost that adopts high-volume hydraulic pump simultaneously, because this hydraulic system can be inputted large flow output by small flow, realize the large braking moment output of drum brake, the braking axle quantity of multi-axle heavy type engineering machinery can have been reduced, corresponding shortening overall dimensions of a car, reduce turn inside diameter, save cost.
2, filter assembly is realized the effect of brake circuit being carried out to forward and reverse filtration, and 4 one-way valves are realized the function of Fixed-Filter filler opening and oil outlet, and filter is realized the function that brake circuit is filtered.
3, can realize the parking braking of vehicle by manual parking ball valve.
4, realize the function of emergency vehicle releasing parking braking by hand pump.
5, monitor in real time the incoming pressure of electrohydraulic proportional control valve group by the first pressure switch, pressure lower than or produce electrical signal control signal lamp while exceeding certain threshold values and open or close, realize monitoring Realtime Alerts to incoming pressure; Monitor in real time the pressure of master cylinder by the second pressure switch, pressure lower than or produce electrical signal control Stop Lamp while exceeding certain threshold values and open or close.
6, realize this hydraulic braking system pressure security protective function by safety overflow valve.
7, realize the function of real-time monitoring vehicle retardation pressure by pressure transducer.
Brief description of the drawings
In order to be illustrated more clearly in the embodiment of the present invention or technological scheme of the prior art, to the accompanying drawing of required use in embodiment or description of the Prior Art 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, do not paying under the prerequisite of creative work, can also obtain according to these accompanying drawings other accompanying drawing.
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 of oil-feed 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.
Embodiment
Below in conjunction with accompanying drawing of the present invention, technological scheme of the present invention is clearly and completely described, obviously, described embodiment is only the present invention's part embodiment, instead of whole embodiments.Based on the embodiment in the present invention, those of ordinary skill in the art, not making the every other embodiment who obtains under creative work prerequisite, belong to the scope of protection of the invention.
As shown in Figure 1, the invention provides a kind of drum brake hydraulic system of multi-axle heavy type engineering machinery, comprising:
Oil-feed control valve group 1, electrohydraulic proportional control valve group 2, manual parking ball valve 3, switching ball 4, filter assembly 5, hand pump 6, the first oil circuits 7, the second oil circuit 8, the 3rd oil circuit 9, the 4th oil circuit 10 and the 5th oil circuit 11,
The first described oil circuit 7 is as the oil supply gallery of described oil-feed control valve group 1, the second described oil circuit 8 is as the passage that the actuator port A mouth of described oil-feed control valve group 1 is communicated with the oil inlet P mouth of described electrohydraulic proportional control valve group 2, the 3rd described oil circuit 9 is the oil supply gallery to master cylinder 12 as the control port Z mouth of described electrohydraulic proportional control valve group 2, the 4th described oil circuit 10 is as the emptying passage of described electrohydraulic proportional control valve group 2, and the 5th described oil circuit 11 is as the drainback passage of described oil-feed control valve group 1;
As shown in Figure 2, described oil-feed control valve group 1 comprises the first one-way valve 13, reduction valve 14, throttle valve 15, accumulator 16, the first pressure switch 17, the second safety overflow valve 18 and parking solenoid valve 19, the first described one-way valve 13, the oil inlet P mouth of reduction valve 14 and oil outlet A mouth, throttle valve 15 are connected on the first described oil circuit 7 successively, and the pressure maximum that described reduction valve 14 limits hydraulic oil is 200bar; The filler opening of described the first oil circuit 7, the second safety overflow valves 18 of described accumulator 16 access in parallel accesses between the described accumulator 16 and the actuator port A of described oil-feed control valve group 1 on described the first oil circuit 7, the return opening of described the second safety overflow valve 18 accesses described the 5th oil circuit 11; Between described accumulator 16 and described parking solenoid valve 19 on described the first oil circuit 7 of described the first pressure switch 17 access in parallel, produce electrical signal during lower than 170bar at the incoming pressure of electrohydraulic proportional control valve group 2; The filler opening of described parking solenoid valve 19 accesses described the first oil circuit 7, return opening accesses described the 5th oil circuit 11, the first state that described parking solenoid valve 19 is realized electricly and the second state of dead electricity, at the first state, hydraulic oil enters the second oil circuit 8 from the first oil circuit 7; At the second state, hydraulic oil enters the 5th oil circuit 11 from the first oil circuit 7, and unloading port's L mouth of described reduction valve 14 accesses described the 5th oil circuit 11;
As shown in Figure 3, described electrohydraulic proportional control valve group 2 comprises electric proportional pressure-reducing valve 20, the second one-way 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 of the first safety overflow valve 24 and electric proportional pressure control valve and the first safety overflow valve control, the filler opening A mouth of the two-way plug-in valve 22 of described electric proportional pressure-relief valve control is all connected with the oil inlet P mouth of described electric proportional pressure-reducing valve 20 and accesses described the second oil circuit 8 with pressure control mouth F mouth, between the work filler opening A mouth of the oil outlet B mouth of the two-way plug-in valve 22 of described electric proportional pressure-relief valve control and described electric proportional pressure-reducing valve 20, be connected with described the second one-way valve 21, the oil inlet P mouth of described electric proportional pressure control valve 23, the oil inlet P mouth of described the first safety overflow valve 24 are connected with work filler opening A mouth and the pressure control mouth F mouth of the two-way plug-in valve 25 of the first safety overflow valve control with described electric proportional pressure control valve, and are connected with the oil outlet B mouth of the two-way plug-in valve 22 of electric proportional pressure-relief valve control, the oil return inlet T mouth of described electric proportional pressure control valve 23, the oil return inlet T mouth of described the first safety overflow valve 24 is connected with the oil return inlet T mouth of described electric proportional pressure-reducing valve 20, and access described the 4th oil circuit 10, electrohydraulic proportional control valve group 2 can realize the first state of vehicle driving braking releasing and the second state of vehicle driving braking, the first state that vehicle driving braking is removed, the pressure of the control port Z of described electrohydraulic proportional control valve group 2 is identical with the filler opening A mouth pressure of described electric proportional pressure-reducing valve 20, the 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 electric proportional pressure control valve 23,
As shown in Figure 1, the filler opening of described manual parking ball valve 3 accesses between described first oil circuit 7 the above reduction valve 14 and throttle valve 15, and the return opening of described manual parking ball valve 3 accesses described the 5th oil circuit 11.
Described switching ball 4 is connected with filter assembly 5 and is accessed described the 3rd oil circuit 9, and described filter 9 assemblies are near master cylinder 12.Described filter assembly 5 comprises 26 and 4 one-way valves 27 of filter, realizes the bi-directional filtered of described the 3rd oil circuit 9, wherein the filler opening F of the oil outlet of two one-way valves 27 and filter 26
efiller openings connected, two one-way valves 27 are connected into described the 3rd oil circuit 9, the oil outlet F of the filler opening of two other one-way valve 27 and filter 26
aoil outlet connected, two other one-way valve 27 is connected into described the 3rd oil circuit 9.
Described hand pump 6 accesses between the described switching ball 4 and filter assembly 5 on described the 3rd oil circuit 9.
Preferably, also comprise the second pressure switch 28, between described second pressure switch 28 described the 3rd oil circuit 9 the above filter assembly 5 of access in parallel and master cylinder 12, produce electrical signal during lower than 160bar at the incoming pressure of master cylinder 12.
Preferably, also comprise pressure transducer 29, on the oil circuit that the described described hand pump 6 of pressure transducer 29 access in parallel is connected with described the 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 of accumulator and brake-cylinder pressure, the braking of multi-axle heavy type engineering machinery and the rapid response that braking is removed are not only realized, saved the cost that adopts high-volume hydraulic pump simultaneously, because this hydraulic system can be inputted large flow output by small flow, realize the large braking moment output of drum brake, the braking axle quantity of multi-axle heavy type engineering machinery can be reduced, corresponding shortening overall dimensions of a car, reduces turn inside diameter radius; Filter assembly is realized the effect of brake circuit being carried out to forward and reverse filtration, and 4 one-way valves are realized the function of Fixed-Filter filler opening and oil outlet, and filter is realized the function that brake circuit is filtered; Can realize the parking braking of vehicle by manual parking ball valve; Realize the function of emergency vehicle releasing parking braking by hand pump; Monitor in real time the incoming pressure of electrohydraulic proportional control valve group by the first pressure switch, pressure lower than or produce electrical signal control signal lamp while exceeding certain threshold values and open or close, realize monitoring Realtime Alerts to incoming pressure; Monitor in real time the pressure of master cylinder by the second pressure switch, pressure lower than or produce electrical signal control Stop Lamp while exceeding certain threshold values and open or close; Realize this hydraulic braking system pressure security protective function by safety overflow valve; Realize the function of real-time monitoring vehicle retardation pressure by pressure transducer.
The working principle of the drum brake hydraulic system of a kind of multi-axle heavy type engineering machinery provided by the invention is:
Vehicle is in the time of parking state, hydraulic power is to oil-feed control valve group delivery pressure, thus this drum-type hydraulic braking system and master cylinder in pressure-less state, now the plunger rod extrusion of master cylinder is the shortest, the braking force maximum of drum brake, car load is in parking state.
After vehicle launch, hydraulic power starts to provide stable flow to oil-feed control valve group 1.Hydraulic oil, through the first inner integrated one-way valve 13 of oil-feed control valve group 1, after reduction valve 14 and throttle valve 15, provides flow to accumulator 16, and accumulator 16 starts topping up, and the solenoid valve of parking simultaneously 19 obtains electric, and the pressure of brake off 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 of oil-feed control valve group 1.Hydraulic oil from P mouth is realized the large flow output to master cylinder by the two-way plug-in valve 22 of electric proportional pressure-reducing valve 20 and electric proportional pressure-relief valve control, controls delivery pressure simultaneously.Electricity proportional pressure-reducing valve 20 is pilot control elements of the two-way plug-in valve 22 of electric proportional pressure-relief valve control, control the size of electric proportional pressure-reducing valve 20 delivery pressures by the size of external control electric current, the pressure that the two-way plug-in valve 22 of the electric proportional pressure-relief valve control of final restriction is exported, and export corresponding flow according to pressure flow curve, opening after car brake off, it is maximum that the external control electric current of electricity proportional pressure-reducing valve 20 and electric proportional pressure control valve reaches, the delivery pressure that is electric 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 filler opening A mouth pressure of described electric proportional pressure-reducing valve 20, the delivery pressure that is 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 the first oil circuit 7, the second oil circuit 8, switching ball 4 is in opening state, enter master cylinder by switching ball 4 and filter assembly 5, make master cylinder in pressure maximum state, now the plunger rod extrusion of master cylinder is the longest, the braking force minimum of drum brake, car load is in brake off (releasing parking) state.
In cargo running process, carry out service brake, now the external control electric current of electric proportional pressure-reducing valve 20 and electric proportional pressure control valve 23 reduces, the oil pressure relief of electric proportional pressure control valve 23 reduces, due to the compartmentation of the second one-way valve 21, the pressure at master cylinder place only depends on the two-way plug-in valve 25 of electric proportional pressure control valve 23 and electric proportional pressure control valve and the first safety overflow valve control to control, now the pressure of control port Z mouth of described electrohydraulic proportional control valve group 2 is identical with the oil inlet P mouth pressure of described electric proportional pressure control valve 23, hydraulic oil after 2 releases of electrohydraulic proportional control valve group flows back to fuel tank through the 4th oil circuit 10.When electric current reduces to hour, the delivery pressure of electrohydraulic proportional control valve group 2 is 0, and master cylinder is in pressure-less state, and the plunger rod extrusion of master cylinder is the shortest, the braking force maximum of drum brake.
Parking braking, closes manual parking ball valve 3, and hydraulic oil directly enters the 5th oil circuit 11 after the first oil circuit 7, and vehicle can be realized manual parking operation.
Emergent releasing parking braking, opens hand pump 6, closing switch ball valve 4, and the hydraulic oil that hand pump is got directly enters the 3rd oil circuit 9 and controls master cylinder 12, and vehicle can be realized the emergent parking of manually removing.
The above; be only the specific embodiment of the present invention, but protection scope of the present invention is not limited to this, any be familiar with those skilled in the art the present invention disclose technical scope in; can expect easily changing or replacing, within all should being encompassed in protection scope of the present invention.Therefore, protection scope of the present invention should be as the criterion with the protection domain of described claim.
Claims (9)
1. a drum brake hydraulic system for multi-axle heavy type engineering machinery, is characterized in that, comprising:
Oil-feed 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 is as the oil supply gallery of described oil-feed control valve group, the second described oil circuit is as the passage that the actuator port of described oil-feed control valve group is communicated with the filler opening of described electrohydraulic proportional control valve group, the 3rd described oil circuit arrives the oil supply gallery of master cylinder as the control port of described electrohydraulic proportional control valve group, the 4th described oil circuit is as the emptying passage of described electrohydraulic proportional control valve group, and the 5th described oil circuit is as the drainback passage of described oil-feed control valve group;
Described oil-feed control valve group comprises the first one-way valve, reduction valve, throttle valve, accumulator and parking solenoid valve, the first described one-way valve, the oil inlet P mouth of reduction valve and oil outlet A mouth, throttle valve are connected on the first described oil circuit successively, described the first oil circuit of described accumulator access in parallel, the filler opening of described parking solenoid valve accesses described the first oil circuit, return opening accesses described the 5th oil circuit, the first state that described parking solenoid valve is realized electricly and the second state of dead electricity, at the first state, hydraulic oil enters the second oil circuit from the first oil circuit; At the second state, hydraulic oil enters the 5th oil circuit from the first oil circuit, and unloading port's L mouth of described reduction valve accesses described the 5th oil circuit;
Described electrohydraulic proportional control valve group comprises electric proportional pressure-reducing valve, the second one-way 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 of the first safety overflow valve and electric proportional pressure control valve and the first safety overflow valve control, the filler opening A mouth of the two-way plug-in valve of described electric proportional pressure-relief valve control is all connected with the oil inlet P mouth of described electric proportional pressure-reducing valve and accesses described the second oil circuit with pressure control mouth F mouth, between the work filler opening A mouth of the oil outlet B mouth of the two-way plug-in valve of described electric proportional pressure-relief valve control and described electric proportional pressure-reducing valve, be connected with described the second one-way valve, the oil inlet P mouth of described electric proportional pressure control valve, the oil inlet P mouth of described the first safety overflow valve are connected with work filler opening A mouth and the pressure control mouth F mouth of the two-way plug-in valve of the first safety overflow valve control with described electric proportional pressure control valve, and are connected with the oil outlet B mouth of the two-way plug-in valve of electric proportional pressure-relief valve control, the oil return inlet T mouth of described electric proportional pressure control valve, the oil return inlet T mouth of described the first safety overflow valve is connected with the oil return inlet T mouth of described electric proportional pressure-reducing valve, and access described the 4th oil circuit, electrohydraulic proportional control valve group can realize the first state of vehicle driving braking releasing and the second state of vehicle driving braking, the first state that vehicle driving braking is removed, the pressure of the control port of described electrohydraulic proportional control valve group is identical with the filler opening A mouth pressure of described electric proportional pressure-reducing valve, the 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 electric proportional pressure control valve,
Described switching ball is connected with filter assembly and is accessed described the 3rd oil circuit, and described filter assembly is near master 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 comprises filter and 4 one-way valves, realize the bi-directional filtered of described the 3rd oil circuit, the wherein oil outlet of two one-way valves and the filler opening of filter is connected, the filler opening of two one-way valves is connected into described the 3rd oil circuit, the filler opening of two other one-way valve is connected with the oil outlet of filter, the oil outlet of two other one-way valve is connected into described the 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 comprise manual parking ball valve, the filler opening of described manual parking ball valve accesses between described the above reduction valve of the first oil circuit and throttle valve, and the return opening of described manual parking ball valve accesses described the 5th oil circuit.
4. the drum brake hydraulic system of multi-axle heavy type engineering machinery according to claim 1, is characterized in that, also comprises hand pump, and described hand pump accesses between the described switching ball and filter assembly on described the 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 comprise the first pressure switch and the second pressure switch, between described accumulator and described parking solenoid valve on described described the first oil circuit of the first pressure switch access in parallel, between described the second pressure switch described the 3rd the above filter assembly of oil circuit of access in parallel and master cylinder.
6. the drum brake hydraulic system of multi-axle heavy type engineering machinery according to claim 1, it is characterized in that, also comprise the second safety overflow valve, the filler opening of described the second safety overflow valve accesses between the described accumulator and the actuator port of described oil-feed control valve group on described the first oil circuit, and the return opening of described the second safety overflow valve accesses described the 5th oil circuit.
7. the drum brake hydraulic system of multi-axle heavy type engineering machinery according to claim 4, is characterized in that, also comprises pressure transducer, on the oil circuit that the described described hand pump of pressure transducer access in parallel is connected with described the 3rd oil circuit.
8. the drum brake hydraulic system of multi-axle heavy type engineering machinery according to claim 1, is characterized in that, the pressure maximum of described reduction 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 the first pressure switch, produce electrical signal during lower than 170bar at the incoming pressure of electrohydraulic proportional control valve group, described the second pressure switch, produces electrical signal during lower than 160bar at the incoming pressure of master cylinder.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201310263268.XA CN104061193B (en) | 2013-06-27 | 2013-06-27 | The drum brake hydraulic system of multi-axle heavy type engineering machinery |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201310263268.XA CN104061193B (en) | 2013-06-27 | 2013-06-27 | The drum brake hydraulic system of multi-axle heavy type engineering machinery |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN104061193A true CN104061193A (en) | 2014-09-24 |
| CN104061193B CN104061193B (en) | 2016-07-06 |
Family
ID=51549065
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201310263268.XA Active CN104061193B (en) | 2013-06-27 | 2013-06-27 | The drum brake hydraulic system of multi-axle heavy type engineering machinery |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN104061193B (en) |
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106337848A (en) * | 2016-09-26 | 2017-01-18 | 东洋重工机（大连）有限公司 | Hydraulic power unit |
| CN106402207A (en) * | 2016-09-27 | 2017-02-15 | 北京理工大学 | Hydraulic control system with quick effect and precise braking torque control and for hydraulic retarder |
| CN107269607A (en) * | 2017-06-01 | 2017-10-20 | 凯盛重工有限公司 | A kind of brake fluid system of mine shuttle car |
| CN108302079A (en) * | 2018-04-04 | 2018-07-20 | 徐工集团工程机械股份有限公司科技分公司 | A kind of gearbox dynamic output control system and control method |
| CN110486348A (en) * | 2019-09-24 | 2019-11-22 | 洛阳智能农业装备研究院有限公司 | A kind of electromagnetic valve group in current of unmanned agricultural machinery |
| CN112173088A (en) * | 2020-09-25 | 2021-01-05 | 中国直升机设计研究所 | Combined pressure accumulator with flow rate control function and hydraulic brake system |
| CN112762037A (en) * | 2020-11-27 | 2021-05-07 | 徐工集团工程机械股份有限公司 | Quick-insertion valve group, remote hydraulic control system and engineering vehicle |
Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN201144909Y (en) * | 2007-12-29 | 2008-11-05 | 江苏国力锻压机床有限公司 | Hydraulic control system of hydraulic machine |
| CN102114833A (en) * | 2009-12-31 | 2011-07-06 | 中国神华能源股份有限公司 | Hydraulic control system for brakes |
| JP2012086619A (en) * | 2010-10-18 | 2012-05-10 | Caterpillar Japan Ltd | Small-radius turning control device of articulated vehicle |
| CN102720711A (en) * | 2012-06-29 | 2012-10-10 | 武汉船用机械有限责任公司 | Automatic-switch type load sensing hydraulic system |
| 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 |
| 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 |
| US20130218435A1 (en) * | 2010-10-25 | 2013-08-22 | Toyota Jidosha Kabushiki Kaisha | Brake control apparatus |
-
2013
- 2013-06-27 CN CN201310263268.XA patent/CN104061193B/en active Active
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN201144909Y (en) * | 2007-12-29 | 2008-11-05 | 江苏国力锻压机床有限公司 | Hydraulic control system of hydraulic machine |
| CN102114833A (en) * | 2009-12-31 | 2011-07-06 | 中国神华能源股份有限公司 | Hydraulic control system for brakes |
| JP2012086619A (en) * | 2010-10-18 | 2012-05-10 | Caterpillar Japan Ltd | Small-radius turning control device of articulated vehicle |
| US20130218435A1 (en) * | 2010-10-25 | 2013-08-22 | Toyota Jidosha Kabushiki Kaisha | Brake control apparatus |
| 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 |
| CN102720711A (en) * | 2012-06-29 | 2012-10-10 | 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 |
Cited By (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106337848A (en) * | 2016-09-26 | 2017-01-18 | 东洋重工机（大连）有限公司 | Hydraulic power unit |
| CN106402207A (en) * | 2016-09-27 | 2017-02-15 | 北京理工大学 | Hydraulic control system with quick effect and precise braking torque control and for hydraulic retarder |
| CN106402207B (en) * | 2016-09-27 | 2019-09-10 | 北京理工大学 | The Retarder hydraulic control system that quick acting and braking moment accurately control |
| CN107269607A (en) * | 2017-06-01 | 2017-10-20 | 凯盛重工有限公司 | A kind of brake fluid system of mine shuttle car |
| CN107269607B (en) * | 2017-06-01 | 2019-09-27 | 凯盛重工有限公司 | A kind of brake fluid system of mine shuttle car |
| CN108302079A (en) * | 2018-04-04 | 2018-07-20 | 徐工集团工程机械股份有限公司科技分公司 | A kind of gearbox dynamic output control system and control method |
| CN108302079B (en) * | 2018-04-04 | 2023-08-11 | 徐工集团工程机械股份有限公司科技分公司 | Gearbox power output control system and control method |
| CN110486348A (en) * | 2019-09-24 | 2019-11-22 | 洛阳智能农业装备研究院有限公司 | A kind of electromagnetic valve group in current of unmanned agricultural machinery |
| CN110486348B (en) * | 2019-09-24 | 2023-09-05 | 洛阳智能农业装备研究院有限公司 | Electrohydraulic valve group of unmanned agricultural machinery |
| CN112173088A (en) * | 2020-09-25 | 2021-01-05 | 中国直升机设计研究所 | Combined pressure accumulator with flow rate control function and hydraulic brake system |
| CN112762037A (en) * | 2020-11-27 | 2021-05-07 | 徐工集团工程机械股份有限公司 | Quick-insertion valve group, remote hydraulic control system and engineering vehicle |
Also Published As
| Publication number | Publication date |
|---|---|
| CN104061193B (en) | 2016-07-06 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN104061193A (en) | Drum brake hydraulic system for multi-shaft heavy engineering machinery | |
| CN203739871U (en) | Electrical control air pressure service brake device of heavy-duty truck | |
| CN110588617B (en) | Control system for realizing driving and emergency parking braking functions of front wheels and rear wheels of explosion-proof vehicle | |
| CN105501200A (en) | Vehicle gear selection and parking brake joint control system | |
| CN203496984U (en) | Underground wheeled vehicle emergency steering system | |
| CN102785652B (en) | Integrated control system of wheel type engineering machine | |
| CN201745568U (en) | Heavy mineral dump truck brake control system | |
| CN201866000U (en) | High-integration threaded cartridge valve of large-tonnage off-load dump truck | |
| CN104129428A (en) | Emergency steering control system and method | |
| CN104401306B (en) | A kind of Large Electric wheel quarry tipper hydraulic braking controls integrated system | |
| CN202764956U (en) | Wheel type engineering machinery integrated control system | |
| CN102717788A (en) | Braking device of heavy-duty mining dump truck | |
| CN104943669A (en) | Passive type tramcar hydraulic brake system provided with high-speed switch valves | |
| CN106627541B (en) | Active hydraulic braking system of automobile | |
| US20110018338A1 (en) | Hydraulic break system | |
| CN207128878U (en) | A kind of quarry tipper air-operated hydraulic brake system | |
| CN205524208U (en) | Electronic round of hydraulic pressure of drive -by -wire for car parking braking system of all wheel steering | |
| CN107472226B (en) | Gas cap oil braking system of mining dump truck | |
| CN212222224U (en) | Monorail crane car and hydraulic system thereof | |
| CN102616125A (en) | System and method for providing hydraulic energy-accumulation hybrid power | |
| CN111775913B (en) | Hydraulic emergency braking system of mining dump truck | |
| CN111891924A (en) | Monorail crane car and hydraulic system thereof | |
| CN210618109U (en) | Electronic hydraulic parking system | |
| CN202608756U (en) | Hydraulic brake control system of mine dump truck | |
| CN107813809B (en) | Hydraulic system for reducing service braking stroke of mining dump truck and braking method |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant |