CN202227703U - Braking system for operation machine - Google Patents
Braking system for operation machine Download PDFInfo
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- CN202227703U CN202227703U CN2011202981329U CN201120298132U CN202227703U CN 202227703 U CN202227703 U CN 202227703U CN 2011202981329 U CN2011202981329 U CN 2011202981329U CN 201120298132 U CN201120298132 U CN 201120298132U CN 202227703 U CN202227703 U CN 202227703U
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Abstract
The utility model discloses a braking system for an operation machine, which comprises an energy accumulator, a liquid charging oil circuit, a work oil circuit and a pressure detector, wherein the liquid charging oil circuit is connected with the energy accumulator; a first reversing valve as well as a non-return valve for preventing oil from flowing back is arranged on the liquid charging oil circuit; the work oil circuit is connected with the energy accumulator and a hydraulic brake; a second reversing valve is arranged on the work oil circuit; and the pressure detector is used for detecting the oil pressure of the energy accumulator. The utility model further discloses a hydraulic system with the brake valve group and a concrete spreader with the hydraulic system. The two independent working oil circuits (namely the liquid charging oil circuit and the work oil circuit), on which the valves are arranged, can be used for braking, clamping and the like.
Description
Technical field
The utility model relates to a kind of brakes that is used for Work machine.
Background technology
At present, the jib of concrete mixer, material distributing machine supports through hydraulic gyration reductor, revolution and carries out gyration.The hydraulic gyration reductor is by fluid motor-driven.The hydraulic gyration reductor self has brake.Whether brake is in on-position during according to shutdown, and brake can be divided into two types, promptly open in usual and normally closed type.
The operating principle of brake open in usual is that spring discharges and the hydraulic loaded braking.When machine is not worked, rely on spring force, brake discharges, and jib can freely rotate under the effect that external force is disturbed, and carries like wind.If the brake braking then needs hydraulic system to provide pressure oil to get into brake,, make the brake braking to overcome spring force.
The operating principle of normally closed brake is that spring-loaded braking and hydraulic pressure discharge.When machine is not worked, rely on spring force, brake is braked, and jib can not rotate, even feeding pushes back the hydraulic motor input pressure oil that changes in slowing down, as long as brake does not discharge, jib still can not rotate.If brake discharges, then need hydraulic system to provide pressure oil to get into brake, to overcome spring force, brake is discharged.
The hydraulic gyration reductor that concrete mixer is installed, its brake all is a normally closed type.The hydraulic gyration reductor braking device that most concrete spreaders use also is a normally closed type.But material distributing machine (like tower material distributing machine) for work high above the ground; Because the influence that wind-engaging carries is very big; Requirement according to safety standard; Must guarantee during shutdown that jib can freely rotate with the wind, this rotary reducer (for example the rotary decelerating of pillar crane for building, its brake all is open in usual) with regard to needs brake open in usual.Like this, when wind speed greatly to a certain degree the time, the jib of material distributing machine can rotate with the wind, avoid carrying because of wind the adverse effect of the moment of torsion that is produced with the body of the tower (or its column) of protection material distributing machine, otherwise body of the tower (perhaps column) can excessively damage because of torsional deflection.(as meeting with typhoon) may make material distributing machine slump from the high-altitude when serious, causes serious accident.
If material distributing machine is used hydraulic gyration reductor open in usual, during operation,, just need hydraulic system to provide pressure oil to brake so as long as the hydraulic gyration reductor does not turn round, Fig. 1 is the structural representation of the material distributing machine of prior art.As shown in Figure 1, on tower concrete spreader 10, hydraulic actuating mechanism comprises an oil cylinder 240 of climbing, hydraulic gyration reductor 250, three arm support oil cylinder 210,220,230.
Fig. 2 is the hydraulic schematic diagram of hydraulic system of the tower material distributing machine of prior art, has omitted some load maintenances and motion control valve (like equalizing valve, being installed on the in-line of oil cylinder and motor) and other hydraulic pressure auxiliary element among the figure.As shown in Figure 2, hydraulic gyration reductor 250 comprises hydraulic motor 253 and brake 251 open in usual.Because tower concrete spreader is a work high above the ground machinery, so disposed hydraulic gyration reductor open in usual, after shutting down like this, jib can rotate with the wind.
In Fig. 2, use an oil pump 260 to realize the rotation of the stretching motion of each oil cylinder of material distributing machine, rotary reducer hydraulic motor 253 and the braking of rotary reducer brake 251 open in usual.The back pressure that this solution relies on oil return line a choke valve 108 to be produced realizes that rotary reducer brakes needed oil liquid pressure.
During this material distributing machine work, following three kinds of operating modes are arranged:
(1) when all actuator (oil cylinder and hydraulic motor) of material distributing machine when not moving; Solenoid operated directional valve 101 and solenoid operated directional valve 102 outages flow back to fuel tank from the pressure oil of oil pump through solenoid operated directional valve 101, choke valve 108, regulate the size of choke valve 108 valve ports on the oil return line; Make choke valve 108 produce enough back pressures; This back pressure acts on the brake open in usual through solenoid operated directional valve 102 again, overcomes spring force, realizes braking.
(2) when the jib of material distributing machine needs stretching motion or material distributing machine to climb; Solenoid operated directional valve 101 and solenoid operated directional valve 102 get electric, and the hydraulic fluid port of brake is by solenoid operated directional valve 102 sealings, so that pin the pressure of fluid in the brake; Make brake continue to keep braking; Simultaneously in the solenoid operated directional valve 103,104,105,106 electric, move accordingly to realize each oil cylinder of material distributing machine, as material distributing machine climb or jib flexible.
(3) when the jib of material distributing machine need turn round, solenoid operated directional valve 101 gets electric, solenoid operated directional valve 102 outages; The hydraulic fluid port of brake is through solenoid operated directional valve 102 and choke valve 108; Be communicated with fuel tank, make the pressure oil off-load in the brake, brake discharges under the effect of spring force.Simultaneously solenoid operated directional valve 103 electric, the hydraulic motor in the rotary reducer is rotated, thus realize the material distributing machine jib about revolution.
There is following defective in prior art solutions: (a) braking of the stretching motion of each oil cylinder of material distributing machine and rotary reducer can interfere with each other, can not separate work, the brake that can not supply with each oil cylinder and rotary reducer from the pressure oil of oil pump simultaneously uses; (b) when arm support oil cylinder for a long time during stretching motion, because all can there be leakage in any Hydraulic Elements, the oil liquid pressure in the rotary reducer brake can slowly descend, and can not realize reliable braking, and there is potential potential safety hazard in this; (c) owing to the existence of choke valve back pressure, system capacity consumption is big, and the fluid calorific value is big, and this influences the life-span of Hydraulic Elements; (d) if also need braking after the machine down, this system can't provide braking needed pressure oil.
The utility model content
The purpose of the utility model is to provide a kind of brakes that is used for Work machine, and it not only can be used for the braking of brake open in usual, can also be used for other purposes such as clamping, pressure maintenance.
For this reason,, a kind of brakes that is used for Work machine is provided, has comprised: accumulator according to the one side of the utility model; The topping up oil circuit that links to each other with accumulator, topping up oil circuit are provided with first reversal valve and the one way valve that prevents that fluid from refluxing; The working oil path that links to each other with accumulator, working oil path are provided with second reversal valve, and wherein, working oil path links to each other with liquid braking device; And pressure detector, the oil pressure of detection accumulator.
Further, above-mentioned brakes comprises also and the off-load oil circuit that links to each other with accumulator that the off-load oil circuit is provided with the 3rd reversal valve.
Further, the above-mentioned brakes that is used for Work machine comprises that also the pressure with accumulator is controlled at the control module in the pressure setting range, and control module is electrically connected with pressure detector, first reversal valve, second reversal valve and the 3rd reversal valve.
Further, above-mentioned topping up oil circuit is provided with throttling arrangement.
Further, above-mentioned brakes also comprises the safety valve that links to each other with accumulator.
Further, above-mentioned second reversal valve and the 3rd reversal valve are solenoid operated directional valve open in usual.
Further, above-mentioned off-load oil circuit also comprises the manual unloader parallelly connected with the 3rd reversal valve.
Further, second reversal valve is solenoid operated directional valve open in usual or pilot operated directional control valve open in usual, and above-mentioned the 3rd reversal valve is the normally closed type solenoid operated directional valve.
Further, above-mentioned pressure detector comprises first pressure switch and second pressure switch, and wherein, the setting pressure of second pressure switch is greater than the setting pressure of first pressure switch.
Further, above-mentioned topping up oil circuit, off-load oil circuit and working oil path are integrated in the valve piece, and first reversal valve and the 3rd reversal valve are screw-in cartridge valve.
Compared with prior art; The oil circuit that has two separate work according to the brake valve group of the utility model; Be the topping up oil circuit and the working oil path of accumulator, when itself and load-sensitive multiple directional control valve are used, when some other valve block of handling the load-sensitive multiple directional control valve makes the action of other executing agency; The accumulator topping up is unaffected, and can guarantee that the accumulator topping up is preferential.
Accumulator can keep clamping or braking needed pressure for a long time; Make that the brake braking of rotary reducer is reliable; And solved the big problem of system's fluid calorific value that existence brought of choke valve back pressure in the prior art, and after machine down, can also provide braking required hydraulic oil.
According to the hydraulic system of the utility model, when the pressure in the accumulator maintained between low pressure and these two setting values of high pressure, system just can not give the accumulator topping up, and this has just been avoided the frequent movement of the valve on the topping up oil circuit.
Except top described purpose, characteristic and advantage, other purpose, characteristic and the advantage that the utlity model has are with combining accompanying drawing to do further detailed explanation.
Description of drawings
Constitute the preferred embodiment that the part of this manual, the accompanying drawing that is used for further understanding the utility model show the utility model, and be used for explaining the principle of the utility model with manual.Among the figure:
Fig. 1 is the structural representation of a kind of tower concrete spreader of prior art;
Fig. 2 is the hydraulic schematic diagram of hydraulic system of the tower concrete spreader of prior art;
Fig. 3 is the hydraulic schematic diagram according to first embodiment of the brake valve group of the utility model;
Fig. 4 is the hydraulic schematic diagram according to the hydraulic system of the brake valve group member of first embodiment of the utility model;
Fig. 5 is the hydraulic schematic diagram according to second embodiment of the brake valve group of the utility model;
Fig. 6 is the hydraulic schematic diagram according to the 3rd embodiment of the brake valve group of the utility model;
Fig. 7 is the schematic perspective view according to the brake valve group of the utility model;
Fig. 8 is the hydraulic schematic diagram according to the hydraulic system of first embodiment of the tower material distributing machine of the utility model; And
Fig. 9 is the hydraulic schematic diagram according to the hydraulic system of second embodiment of the tower material distributing machine of the utility model.
Description of reference numerals
100 brake valve groups
110 accumulators, 120 valve body pieces
130 topping up oil circuits, 131 first reversal valves
133 throttle orifices, 135 one way valves
150 off-load oil circuits 151 the 3rd reversal valve
161 safety valves, 163 manual unloaders
170 working oil path, 171 second reversal valves
191 first pressure switches, 193 second pressure switches
210,220,230 arm support oil cylinder 240 oil cylinder that climbs
250 hydraulic gyration reductors, 251 liquid braking devices
253 liquid braking devices, 260 oil pumps
270 load-sensitive multiple directional control valves, 280 controllers
290 remote controllers.
The specific embodiment
Embodiment to the utility model is elaborated below in conjunction with accompanying drawing, but the multitude of different ways that the utility model can be defined by the claims and cover is implemented.
Fig. 3 is the hydraulic schematic diagram according to first embodiment of the brake valve group of the utility model.As shown in Figure 3, the brake valve group 100 of present embodiment comprises: accumulator 110; The topping up oil circuit 130 that links to each other with accumulator 110, this topping up oil circuit 130 are provided with first reversal valve 131 of control oil channel break-make; The off-load oil circuit 150 that links to each other with accumulator 110, this off-load oil circuit 150 are provided with the 3rd reversal valve 151 of control oil channel break-make; The working oil path 170 that links to each other with accumulator 110, this working oil path 170 are provided with second reversal valve 171 of control oil channel break-make; And first pressure switch 191 and second pressure switch 193, be used to detect the oil pressure of accumulator, wherein, the setting pressure of second pressure switch is greater than the setting pressure of first pressure switch.
Rely on accumulator that the braking energy needed is provided, though machine down so, as long as the not off-load of pressure oil in the accumulator still can continue as the brake braking energy needed is provided.
There is a time interval in the topping up of accumulator, if the capacity of accumulator is big, it is just long then once to be full of the needed time of fluid, and the time of use is also long, and the time interval during so extremely next topping up is also long.The capacity of accumulator can be selected as required.
In the present embodiment, also be provided with throttle orifice 133 on the topping up oil circuit 130.This throttle orifice 133 is positioned at the oil inlet P place of first reversal valve 131, and the speed (perhaps flow) during with adjusting accumulator topping up makes topping up steady, prevents pressure overshoot and impact.Throttle orifice 133 is made removable form.Change the throttle orifice of different size, just can adjust the topping up time of accumulator, prevent compression shock, make the steady topping up of accumulator.
When being used for load sensitive system, according to the principle of load sensitive system, the maximum differential pressure before and after the throttle orifice is confirmed by the flow regulator of displacement control mechanism in the variable pump or load-sensitive multiple directional control valve.The big I of throttle orifice is confirmed according to the capacity of accumulator, maximum differential pressure, oil liquid temperature and the viscosity that the throttle orifice front and back produce.
In the present embodiment, also be provided with the one way valve 135 that is used for non-return on the topping up oil circuit 130.This one way valve 135 pins system pressure, prevents that the high-voltage oil liquid in the accumulator from flowing back to fuel tank from oil return opening R.First reversal valve 131 is a solenoid operated directional valve, and this solenoid operated directional valve is selected a ground and is communicated with oil inlet P or oil return opening R.Preferably also be provided with load-sensitive hydraulic fluid port LS on the topping up oil circuit 130, to be used, if not the load-sensitive multiple directional control valve then need be blocked this hydraulic fluid port LS with the load-sensitive multiple directional control valve.
In the present embodiment, off-load oil circuit 150 connects accumulator 110 and oil return opening R, and the 3rd reversal valve 151 is the bi-bit bi-pass solenoid operated directional valve, with the break-make of control off-load oil circuit 150.The oil port of accumulator 150 is preferably installed safety valve 161, for accumulator provides safeguard protection, when preventing the accumulator topping up, because of the fluid superpressure is blasted.
The oil port of accumulator is also preferably installed the automatic deloading valve of manual unloader 163 or band manual function, during with the air bag replacing, at first to make the pressure oil off-load in the accumulator in accumulator maintenance.
In the present embodiment; Second reversal valve 171 on the working oil path 170 is a solenoid operated directional valve; This solenoid operated directional valve makes working oil path C select a ground and accumulator 110 and oil return opening R conducting; When working oil path C passed through second reversal valve 171 with accumulator 110 conductings, C provided hydraulic oil to actuator port, is used for the braking or the clamping of hydraulic parts such as brake.When working oil path C passed through second reversal valve 171 with oil return opening R conducting, hydraulic part discharged braking or clamps.
Setting pressure one a low height of the first pressure relay and the second pressure relay; And make the setting pressure of the setting pressure of first pressure switch 191 greater than second pressure switch 193; So, first pressure switch 191 and second pressure switch 193 form a pressure setting range.
In Fig. 3, valve 100 also can comprise pressure measurement hydraulic fluid port M1 and the M2 that is used to detect energy storage pressure, and the pressure measurement hydraulic fluid port M3 and the M4 that are used for testing oil circuit pressure.
In the present embodiment, the 3rd reversal valve 151 adopts its advantage of normally closed type solenoid operated directional valve to be: just in case system's dead electricity, the solenoid operated directional valve of normally closed type can lock the pressure in the accumulator, prevents the high-voltage oil liquid off-load in the accumulator.Because second reversal valve 171 is open in usual, so behind the system blackout, working oil path and accumulator are communicated with through second reversal valve, the pressure of working oil path also can lock thereupon.So after present embodiment is applicable to system-down (perhaps having a power failure), need to keep the situation of operating pressure.
Made though it is pointed out that the valve of the utility model to be based on the braking of hydraulic gyration reductor open in usual, its purposes is not limited only to this, can also be used for other purposes such as clamping, pressure maintenance.
Whether topping up need realize that this control module can be not included in the brake valve group with a control module to accumulator 110, when making up the hydraulic control system of complete machine, can realize with the controller of complete machine.
Fig. 4 is the hydraulic schematic diagram according to the hydraulic system of the brake valve group member of first embodiment of the utility model.As shown in Figure 4; This hydraulic system that is used for hydraulic braking or clamping comprises liquid braking device 251 and hydraulic control system; This hydraulic control system comprises the brake valve group 100 and controller 280 of describing structure according to top; This controller 280 is used to receive the actuating signal of first pressure switch 191 and second pressure switch 193; According to the actuating signal of first pressure switch and the actuating signal of second pressure switch; Control first reversal valve 131, the 3rd reversal valve 151 and second reversal valve 171 break-make (first reversal valve, the 3rd reversal valve, second reversal valve are solenoid operated directional valve, can through electric or dead electricity is carried out break-make control), to select a ground accumulator 100 topping ups, off-load or braking are used.
When hydraulic work system, controller receives the signal of two pressure switches in the valve 100, and carries out logical operation and judgement, controls first reversal valve then and makes conducting of topping up oil circuit or disconnection, with control accumulator topping up whether.
When the oil liquid pressure in the accumulator was positioned at the setting pressure scope of two pressure switches, controller made the reversal valve of winning keep its original spool position constant, and even the accumulator topping up then continues topping up; If accumulator not topping up then continues not topping up.
When the oil liquid pressure in the accumulator is reduced to a certain limiting value (setup pressure value of first pressure switch); Controller detects the signal that first pressure switch triggers, and makes judgement, controls the first electromagnetic switch valve events; Pressure oil is communicated with accumulator, and accumulator begins topping up.
When the oil liquid pressure topping up in the accumulator to a certain limiting value (setup pressure value of second pressure switch); Controller receives the signal that second pressure switch triggers, and makes judgement, controls the action of first reversal valve; Pressure oil and accumulator are broken off, and accumulator stops topping up.
So as long as the pressure in the accumulator maintains between the setting pressure scope, first reversal valve is with regard to dead electricity, system just can not give the accumulator topping up, has so just avoided the frequent movement of first reversal valve.
Fig. 5 is the hydraulic schematic diagram according to second embodiment of the brake valve group of the utility model; Present embodiment and first embodiment difference are; The 3rd reversal valve 170 in the valve 100 in the present embodiment is solenoid operated directional valves open in usual, and second reversal valve 171 is solenoid operated directional valves of often opening.
The 3rd reversal valve 151 in the present embodiment is solenoid operated directional valves open in usual, and its advantage is: have a power failure in case system is unexpected, solenoid operated directional valve open in usual can be guaranteed the accumulator off-load.Because second reversal valve 171 is solenoid operated directional valves of often opening, so behind the system blackout, working oil path and accumulator are communicated with through second reversal valve 171, working oil path is off-load thereupon also.After so present embodiment is applicable to system-down (perhaps having a power failure), need be with the situation of accumulator and the off-load of working oil path pressure, like the brake open in usual of tower material distributing machine hydraulic gyration reductor.
Fig. 6 is the hydraulic schematic diagram according to the 3rd embodiment of the brake valve group of the utility model; As shown in Figure 6; The difference of the present embodiment and second embodiment is that second reversal valve 171 is replaced with pilot operated directional control valve, can be through control port X (external controlled pressure); Handle pilot operated directional control valve, whether work with the decision working oil path.
According to other embodiment of the utility model, a differential type pressure switch can replace above-mentioned two common pressure switches, just can realize the topping up of above-mentioned accumulator is controlled.In another other embodiment, replace two common pressure switches with pressure sensor, wherein according to the utility model; Pressure sensor is used for detecting in real time the oil pressure of accumulator, and sends controller to, and controller is compared with pressure setting range value to the detected fuel injection pressure signal of pressure sensor; If be lower than the lower limit of pressure setting range; Then make the accumulator topping up,, then make accumulator stop topping up if be higher than the higher limit of pressure setting range; If in pressure setting range value, it is constant then to make accumulator maintain original state.
Fig. 7 is the perspective view when specifically using according to the brake valve group of the utility model; In conjunction with reference to Fig. 3 and Fig. 7; Brake valve group 100 is configured to comprise the valve body piece 120 of accumulator 110 and first hydraulic fluid port (shown in label ACC among Fig. 3) with installation accumulator and be installed on the peripheral Hydraulic Elements on the valve body piece 20; For example, these peripheral Hydraulic Elements can be the 3rd reversal valve 151, the 3rd electromagnetic valve 171, first pressure switch 191, second pressure switch 192 and manual unloader 163.Valve piece, safety valve 161, the one way valve 135 of topping up oil circuit 130, off-load oil circuit 150, working oil path 170 and first reversal valve 131 thereof can be integrated on the valve body piece 120.
The 3rd reversal valve 151 (solenoid operated directional valve) and second reversal valve 171 (solenoid operated directional valve) all preferentially are chosen as screw-in cartridge valve (perhaps Sandwich plate valve); Solenoid operated directional valve plug-in opening size (perhaps installation dimension) with normally closed type open in usual is identical; Can be according to concrete instructions for use; Between open in usual or normally closed type solenoid operated directional valve, change easily, like this needs valve design piece 120 again not when implementing according to the utility model first embodiment and second embodiment.
In other concrete application, the brake valve group 100 of the utility model can be combined by two or more valve pieces, is perhaps assembled through pipeline by Hydraulic Elements.
Fig. 8 is the hydraulic schematic diagram according to the hydraulic system of first embodiment of the tower material distributing machine of the utility model, and Fig. 9 is the hydraulic schematic diagram according to the hydraulic system of second embodiment of the tower material distributing machine of the utility model.Fig. 8 and hydraulic system difference shown in Figure 9 are, in Fig. 8, have used quantitative oil pump, in Fig. 9, have used variable capacity oil pump.
Like Fig. 8 and shown in Figure 9, the hydraulic system of the tower material distributing machine of the utility model mainly comprises: be used for a plurality of arm support oil cylinder 210,220,230 that the cloth arm stretches; Be used for the oil cylinder 240 that climbs that material distributing machine is climbed; Be used for the rotating hydraulic gyration reductor of jib 250, the oil pump 260 of hydraulic oil be provided, the load-sensitive multiple directional control valve 270 that is connected with hydraulic motor 253 oil circuits of said a plurality of arm support oil cylinder 210,220,230, climb oil cylinder 240 and said hydraulic gyration reductor 250, brake valve group 100, controller 280 and the remote controller 290 that is connected through radiofrequency signal with controller of liquid braking device 251 that be used for hydraulic gyration reductor 250; Wherein, brake valve group 100 is connected with controller 280 signals with load-sensitive multiple directional control valve 270.
Because first embodiment and the brake valve group 100 among second embodiment according to the tower material distributing machine of the utility model are used for the rotating braking of jib, below are referred to as Rotatary brake valve.This Rotatary brake valve and load-sensitive multiple directional control valve (maneuverability pattern of valve block is an electric-hydraulic proportion) are used.
The load-sensitive multiple directional control valve has two types: LS type and LUDV type.The difference of LS type and LUDV type load-sensitive multiple directional control valve is: (1) LS type load-sensitive multiple directional control valve is to carry out pressure compensation before the throttling, and LUDV type load-sensitive multiple directional control valve is to carry out pressure compensation after the throttling; (2) during underfed, the irrelevant metering characteristics of LS type load-sensitive multiple directional control valve and load lost efficacy, and LUDV type load-sensitive multiple directional control valve then can not.
At present, concrete mixer and material distributing machine are mainly used LS type load-sensitive multiple directional control valve.LS type load-sensitive multiple directional control valve both can be used for the quantitative oil pump oil supply system, also can be used for the variable capacity oil pump oil supply system, and the oil-feed connected mode of LS type load-sensitive multiple directional control valve that is used for quantitative oil pump and variable capacity oil pump oil supply system is different.
LUDV type load-sensitive multiple directional control valve then is usually used in the variable capacity oil pump oil supply system.So the hydraulic system of the utility model has three kinds of schemes available, that is: (1) quantitative oil pump+LS load-sensitive multiple directional control valve+Rotatary brake valve; (2) variable capacity oil pump+LS load-sensitive multiple directional control valve+Rotatary brake valve; (3) variable pump+LUDV load-sensitive multiple directional control valve+Rotatary brake valve.
In first embodiment and second embodiment according to the hydraulic system of the tower material distributing machine of the utility model; The load-sensitive multiple directional control valve has five valve blocks; Wherein, valve block one is used to climb, valve block two is used for revolution, and valve block three is used for the flexible of jib one arm oil cylinder; The valve block four-function is flexible in jib two arm oil cylinders, and valve block five is used for the flexible of jib three arm oil cylinders.
In other embodiments, also can use load-sensitive multiple directional control valve, with four executive components in the controlled hydraulic system with four valve blocks.
When the needs jib turned round, the operator can handle the corresponding rocking bar of remote controller, and second reversal valve 171 in Rotatary brake valve sends a signal; It is electric that second reversal valve 171 is got, and working oil path is communicated with fuel tank then, the brake pressure off-load; Rely on spring force then, brake discharges; The revolution valve block of load-sensitive multiple directional control valve also can be according to the size at rocking bar angle of inclination simultaneously; Obtain an electric-hydraulic proportion signal, make the valve block action, the hydraulic motor of rotary reducer rotates; Then support through rotary reducer, revolution; Jib is rotated, and can realize the stepless speed regulation of gyration according to the size of electric-hydraulic proportion signal code.
If do not need the jib revolution, the tractor driver unclamps the corresponding rocking bar of remote controller, and then the second reversal valve dead electricity in the Rotatary brake valve makes accumulator be communicated with working oil path, under the effect of pressure oil liquid, overcomes spring force, makes the brake braking, and jib can not rotate; The revolution valve block of load-sensitive multiple directional control valve is also got back to meta simultaneously, and valve port does not have fluid and flows out, and the hydraulic motor of rotary reducer stops operating.
Like this, when Rotatary brake valve and load-sensitive multiple directional control valve were used, on the one hand, the action of the topping up of accumulator and other valve block of load-sensitive multiple directional control valve (for example tower material distributing machine respectively saves the expansion and the contraction of arm) mutually noninterfere can be carried out simultaneously.According to the operating principle of load-sensitive multiple directional control valve, if accumulator topping up and other valve block of load-sensitive multiple directional control valve move simultaneously, system can preferentially give the accumulator topping up.
On the other hand; The Rotatary brake valve height of the utility model is integrated, when being used with the load-sensitive multiple directional control valve, only needs (quantitative or variable) oil pump; Pressure oil is provided for load-sensitive multiple directional control valve and hydraulic brake system simultaneously; With a spot of Hydraulic Elements, can make up complicated hydraulic system like this, be convenient to fluid pressure line and arrange.In addition, owing to adopt the responsive control of hydraulic load system, this has reduced the power consumption of complete machine, and separate between the topping up of accumulator in motion of each actuator (oil cylinder and motor) and the hydraulic brake system, concurrently-acting.Because the brake braking only relies on accumulator that pressure oil is provided, thus also separate between the stretching motion of brake braking and each oil cylinder, do not disturb mutually.Typical application is the hydraulic system (its rotary reducer brake is open in usual) of apparatus for distributing such as tower material distributing machine, concrete mixer.
The preferred embodiment that the above is merely the utility model is not limited to the utility model, and for a person skilled in the art, the utility model can have various changes and variation.All within the spirit and principle of the utility model, any modification of being done, be equal to replacement, improvement etc., all should be included within the protection domain of the utility model.
Claims (10)
1. a brakes that is used for Work machine is characterized in that, comprising:
Accumulator;
The topping up oil circuit that links to each other with said accumulator, said topping up oil circuit are provided with first reversal valve and the one way valve that prevents that fluid from refluxing;
With the working oil path that said accumulator links to each other, said working oil path is provided with second reversal valve, and wherein, said working oil path links to each other with liquid braking device; And
Pressure detector detects the oil pressure of said accumulator.
2. the brakes that is used for Work machine according to claim 1 is characterized in that, also comprises the off-load oil circuit that links to each other with said accumulator, and said off-load oil circuit is provided with the 3rd reversal valve.
3. the brakes that is used for Work machine according to claim 2; Comprise that also the pressure with said accumulator is controlled at the control module in the pressure setting range, said control module is electrically connected with said pressure detector, first reversal valve, second reversal valve and the 3rd reversal valve.
4. the brakes that is used for Work machine according to claim 1 is characterized in that, said topping up oil circuit is provided with throttling arrangement.
5. according to each described brakes that is used for Work machine in the claim 2 to 4, it is characterized in that, also comprise the safety valve that links to each other with said accumulator.
6. according to each described brakes that is used for Work machine in the claim 2 to 4, it is characterized in that said second reversal valve and the 3rd reversal valve are solenoid operated directional valve open in usual.
7. according to each described brakes that is used for Work machine in the claim 2 to 4, it is characterized in that said off-load oil circuit also comprises the manual unloader parallelly connected with said the 3rd reversal valve.
8. according to each described brakes that is used for Work machine in the claim 2 to 4, it is characterized in that second reversal valve is solenoid operated directional valve open in usual or pilot operated directional control valve open in usual, said the 3rd reversal valve is the normally closed type solenoid operated directional valve.
9. according to each described brakes that is used for Work machine in the claim 2 to 4; It is characterized in that; Said pressure detector comprises first pressure switch and second pressure switch; Wherein, the setting pressure of said second pressure switch is greater than the setting pressure of said first pressure switch.
10. according to each described brakes that is used for Work machine in the claim 2 to 4, it is characterized in that said topping up oil circuit, off-load oil circuit and working oil path are integrated in the valve piece, said first reversal valve and the 3rd reversal valve are screw-in cartridge valve.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2011202981329U CN202227703U (en) | 2011-08-16 | 2011-08-16 | Braking system for operation machine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2011202981329U CN202227703U (en) | 2011-08-16 | 2011-08-16 | Braking system for operation machine |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN202227703U true CN202227703U (en) | 2012-05-23 |
Family
ID=46078292
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2011202981329U Expired - Fee Related CN202227703U (en) | 2011-08-16 | 2011-08-16 | Braking system for operation machine |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN202227703U (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105217508A (en) * | 2014-10-30 | 2016-01-06 | 徐州重型机械有限公司 | A kind of hoist brake control system, method and hoisting crane |
-
2011
- 2011-08-16 CN CN2011202981329U patent/CN202227703U/en not_active Expired - Fee Related
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105217508A (en) * | 2014-10-30 | 2016-01-06 | 徐州重型机械有限公司 | A kind of hoist brake control system, method and hoisting crane |
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| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20120523 Termination date: 20160816 |