CN201866000U - High-integration threaded cartridge valve of large-tonnage off-load dump truck - Google Patents
High-integration threaded cartridge valve of large-tonnage off-load dump truck Download PDFInfo
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- CN201866000U CN201866000U CN2010205894277U CN201020589427U CN201866000U CN 201866000 U CN201866000 U CN 201866000U CN 2010205894277 U CN2010205894277 U CN 2010205894277U CN 201020589427 U CN201020589427 U CN 201020589427U CN 201866000 U CN201866000 U CN 201866000U
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Abstract
The utility model discloses a high-integration threaded cartridge valve of a large-tonnage off-load dump truck, which comprises a steering brake valve block and a lift control valve block. A steering brake hydraulic loop system and a lift control hydraulic loop system are respectively disposed in the steering brake valve block and the lift control valve block, and are respectively communicated with joints on the steering brake valve block and the lift control valve block, and the brake valve block and the lift control valve block are connected to each other through joints. The high-integration threaded cartridge valve of a large-tonnage off-load dump truck can realize fully hydraulic power steering, emergency steering, running rim brake, parking brake, auxiliary brake, emergency brake and container lifting control. As pipeline connection for the high-integration threaded cartridge valve unit is reduced, a hydraulic device with potential defectives of leakage and energy loss is omitted, performance is improved, and maintenance cost of users is reduced.
Description
Technical field
The utility model relates to a kind of hydrovalve, be the high integrated screw-in cartridge valve of the non-highway dump truck of a kind of large-tonnage specifically, be mainly used in the all-hydraulic servosteering of the control non-highway dump truck of large-tonnage, emergently turn to, take turns limit service brake, emergency brake, parking braking, auxiliary braking, container lifting control.
Background technique
What the non-highway dump truck of current domestic large-tonnage was mainly used is quantitative meta closed system, quantitative meta open system or the responsive variable system of partial load, open or the meta closed system of meta wherein, adopted the gear pump of fixed displacement, constant flow is provided, and system pressure is to be determined by the load that acts on the working medium.Maximum operating pressure for restriction system, a high-pressure overflow valve must be set, and when system works pressure reaches setting value, oil hydraulic pump is close to whole flows will flow back to fuel tank by relief valve, thereby cause high power loss, and a large amount of heat loss of generation causes system effectiveness extremely low in system.
Summary of the invention
In view of above-mentioned present situation, the utility model provides the non-highway dump truck of a kind of large-tonnage high integrated screw-in cartridge valve, can significantly improve system reliability, Security, energy saving, the high integration of system.The high integrated screw-in cartridge valve of the non-highway dump truck of large-tonnage, by utilizing the combination of valve piece and some screw-in cartridge valves, and can design flexible valve piece profile according to the different integral valve group of line arrangement, perhaps be decomposed into two or more valve pieces, realize all-hydraulic servosteering, emergent turn to, take turns limit service brake, emergency brake, parking braking, auxiliary braking, container lifting control function.
Technical solution of the present utility model is: the high integrated screw-in cartridge valve of the non-highway dump truck of large-tonnage comprises braking in a turn valve piece and hoist control valve piece two-part composition; In described braking in a turn valve piece, hoist control valve piece, be respectively equipped with braking in a turn hydraulic circuit system and lifting control hydraulic circuit system, this braking in a turn hydraulic circuit system, lifting control hydraulic circuit system is communicated with interface on braking in a turn valve piece, the hoist control valve piece, and described interface to brake valve piece and hoist control valve piece is connected to each other.
In this is novel, the interface of related each end face of braking in a turn valve piece comprises: connect the emergent accumulator pressurising interface M2 that turns to of test, connect emergency brake energy storage pressure remote alarm interface K4, connect emergency brake energy storage pressure remote alarm interface K2, connect ransaxle wheel limit service brake interface D2, connect and show gearbox fluid power jogging state interface M6, the interface B that connects two-way braking treadle valve output B2, connect brake lamp pilot pressure relay interface K5, connect Parking state pressure relay interface K3, interface Z, connect the valve group and leak interface Y, connect two-way braking treadle valve C2, connect the emergent accumulator interface XNQ1 that turns to, connect gearbox fluid power jogging control interface BS, the interface LSS that connects commutator LS connects load-sensitive variable displacement pump interface LS, connect test load feedback pressure interface M3; Connect load-sensitive variable displacement pump interface LS, connect emergency brake accumulator interface XNQ3, connect valve group leakage interface Y; Connect test pumping hole working pressure interface M1, connect the emergent energy storage pressure remote alarm interface K1 that turns to; Connect the first load-sensitive variable displacement pump interface P1, connect the second load-sensitive variable displacement pump interface P2, connect guide's control interface Pi; The interface T that connects commutator pressure hydraulic fluid port interface S, the oil return of valve group; Connection Parking Brake interface BP, the interface A that connects standby emergency brake accumulator interface XNQ2, connection emergency brake accumulator interface XNQ4, the interface C1 that connects two-way braking treadle valve P1, connection steering axle wheel limit service brake interface D1, connection two-way braking treadle valve output B1, connection valve group oil return interface T.
In this was novel, each end face interface of described hoist control valve piece comprised: the interface Z, the interface L that connect test guide pilot pressure interface M4, interface R, connection braking in a turn valve piece; Connect emergent accumulator punching press interface M2, test load feedback pressure interface M3, the connection load-sensitive variable displacement pump interface LS of turning to of test; The interface P that connects valve group oil return interface T, connection braking in a turn valve piece hydraulic circuit system; Four interface CT46 that connect guide's equilibrium valve; Connect the valve group and leak interface Y, interface M5.
In this was novel, the interface Z of hydraulic circuit system on the described braking in a turn valve piece was connected by pipeline with the interface Z of hydraulic circuit system on the described hoist control valve piece; The interface P of the hydraulic circuit system on the described braking in a turn valve piece on the interface P of hydraulic circuit system and the described hoist control valve piece is connected by pipeline; On the described braking in a turn valve piece on the interface LSH of hydraulic circuit system and the described hoist control valve piece interface LS of hydraulic circuit system be connected by pipeline; On the described braking in a turn valve piece on the interface Y of hydraulic circuit system and the described hoist control valve piece interface Y of hydraulic circuit system be connected by pipeline; On the described braking in a turn valve piece on the interface T of hydraulic circuit system and the described hoist control valve piece hydraulic oil container interface T of hydraulic circuit system be connected.
In this was novel, related braking in a turn valve piece hydraulic circuit system comprised: emergent accumulator topping up loop, emergency brake accumulator topping up loop, hydraulic pressure cold start-up functional loop, preferential dynamic steering loop, wet brake jogging control loop, gearbox fluid power jogging guide control, vehicle locking brake servo circuit, Parking brake off and guide's control loop, the container lifting control loop of turning to.
Further, described meeting an urgent need turns to accumulator topping up loop, is made up of damping CT25, damping CT26, one-way valve CT29, unloading valve CT36, telecontrolled sequence valve CT30, one-way valve CT31, damping CT34, solenoid directional control valve CT35; Variable displacement pump interface P1, P2 connect two load-sensitive variable displacement pump CT19, CT22 respectively by pipeline; Accumulator interface XNQ1 connects accumulator by pipeline; Turn to dynamic socket LS to connect two load sensitive pumps by pipeline; The valve group is leaked interface Y, valve group oil return interface T and is connected hydraulic oil container by pipeline; Commutator pressure hydraulic fluid port interface S connects hydraulic steering gear by pipeline, and the interface LSS that connects commutator LS connects the hydraulic steering gear feedback port by pipeline, when realizing the operation commutator steering load signal is passed to the interface LSS that connects commutator LS.
Further, described emergency brake accumulator topping up loop is made up of damping CT23, damping CT17, one-way valve CT16, unloading valve CT18; Interface XNQ2 connects accumulator by pipeline, interface BP connects the Parking clipper disk brake by pipeline, interface XNQ3 respectively is connected an accumulator with interface XNQ4 by pipeline, interface Pi connects the pilot control opening of two-way braking treadle valve by pipeline, interface C1, C2 connects two inlet openings of two-way braking treadle valve by pipeline, interface A, B connects two delivery outlets of two-way braking treadle valve by pipeline, interface D1 connects the clipper disk brake of Vehicular turn wheels by pipeline, interface D2 is by the clipper disk brake of pipeline connection vehicle drive axle wheels, and interface BS is connected to the fluid power jogging control mouth of vehicle gear box by pipeline.Realization is to the braking control of gearbox, and interface K3, K4, K5 connect pressure switch.Realization is to the Pressure testing and the warning function of motor vehicle braking system.
Further, described hydraulic pressure cold start-up functional loop is made up of shuttle valve CT20, solenoid directional control valve CT21; The feedback signal of hydraulic system during to accumulator XNQ1 and accumulator XNQ2 topping up all can enter into shuttle valve CT28, CT33 by shuttle valve CT20 output and flow to interface LS control pump delivery, and pressure oil liquid can be branched off into solenoid directional control valve CT21 between shuttle valve CT20 and shuttle valve CT28.If solenoid directional control valve gets, can flow to interface Y by solenoid directional control valve CT21 from the pressure oil liquid of shuttle valve CT20 output, interface Y is connected to hydraulic oil container by pipeline, this moment is from the oil liquid pressure vanishing of shuttle valve CT20 output like this, the pressure that promptly is transferred to interface LS is zero, the flow of air pump inoperative output is zero, and solenoid directional control valve CT21 has played the effect of intervening the accumulator topping up like this, and this effect is named as the cold start-up function.
Further, described preferential dynamic steering loop is made up of priority valve CT24, damping CT27, shuttle valve CT28, damping CT37; Interface LSS connects the feedback port of commutator by pipeline, interface S connects the filler opening of commutator by pipeline, the feedback port of commutator and the return opening of commutator are connected when the meta of commutator inside, the fluid of pumping hole output is branched off into two-way after by damping CT27, and the road binders liquid damping CT37 that flows through enters into the feedback port of commutator by interface LSS; Another road binders liquid by damping CT27 output enters into shuttle valve CT28.
Further, described wet brake jogging control loop is made up of shuttle valve CT7, solenoid directional control valve CT39, decompression relief valve CT40; Interface B connects the pressure hydraulic fluid port of wet brake by pipeline; The pressure oil-source of reduction valve CT40 comes from accumulator XNQ2, flow to solenoid directional control valve CT39 by the post-decompression fluid of reduction valve CT40, if solenoid directional control valve CT39 gets electric commutation, pressure oil liquid enters into shuttle valve CT7 after by solenoid directional control valve CT39, outputs to interface B from shuttle valve CT7 and enters into wet brake.
Further, described gearbox fluid power jogging guide control is made up of decompression relief valve CT41, damping CT42, one-way valve CT43, solenoid directional control valve CT44; The BS mouth connects the hydraulic changeover control mouth of gearbox by pipeline; Come from flow through after the decompression of pressure oil liquid of accumulator XNQ2 damping CT42, one-way valve CT43 and flow to solenoid directional control valve CT44 by reduction valve CT41.
Further, described vehicle locking brake servo circuit is made up of solenoid directional control valve CT3, CT4, CT5, CT6; Interface C1, C2 connect the inlet opening of two-way braking treadle valve by pipeline, interface A, B connect the delivery outlet of two-way braking treadle valve by pipeline, interface D1 connects the front steering axle clipper disk brake by pipeline, and interface D2 connects the wet multi-disk brake of rear drive sprocket by pipeline.
Further, described Parking brake off and guide's control loop are made up of one-way valve CT12, solenoid directional control valve CT8; By guide's control loop that decompression relief valve CT2, solenoid directional control valve CT1 form, interface P connects the vehicle Parking Brake by pipeline, and interface Pi connects extraneous assist control executive component by pipeline.
In this was novel, the hydraulic circuit system of establishing in the described hoist control valve piece comprised container lifting control loop; Described container lifting control loop by proportional pressure valve CT45, shuttle valve CT47, pilot operated directional control valve CT51, guide control equilibrium valve CT46, shuttle valve CT48, unidirectional relief valve CT49, solenoid directional control valve CT50 form; Interface R is by the rodless cavity of pipeline connection container elevating ram, and interface L connects the container elevating ram by pipeline.
In a word, the high integrated screw-in cartridge valve of the non-highway dump truck of the large-tonnage that the utility model provides, at above homemade large-tonnage mine non-highway dump truck development industry situation and the urgent automobile energy-savingization that realizes, adopt load-sensitive variable system principle, the responsive control of matched load (LS control) pump provides and irrelevant matching pressure and the flow of real work load for system, be that how many flows are system need, how many flows pump just provides, the output flow of pump just was not zero when system did not need flow, can not occur non-acting energy loss like this.Therefore the characteristics that have are:
1, high integrated circuit screw-in cartridge valve is simplified hydraulic pressure and is installed.Reduce installation pipeline quantity, reduce potential leakage point.Reduce overall cost.2, adopt load-transducing control valve and variable displacement pump, reduce the pressure loss and advance the middle heat that produces.Overall energy consumption is more economical.For transmission provides more multipotency.Reduce installation pipeline quantity, reduce potential leakage point.High integrated valve group is for hydraulic system provides all functional and Securities.Program control.Simplify fault diagnosis.Reduce user's maintenance cost.2, the responsive Variable Control technology of application load adopts and turns to dynamic LS signal feed back, turns to damping function between S and LSS, makes flow signals be in state of activation.The load-sensitive steering system is vulnerable to the influence of LS feedback channel length and oil temperature, and moment turns to the startup hard spot, and promptly the fluid that flows in load signal LS oil circuit transmits load signal, makes the guide control oil and flows to commutator from pressure-gradient control valve.Still have a small amount of control fluid of 1L/min to continue to flow during meta to the commutator preheating, thereby can be so that commutator and fluid have temperature much at one, avoided the temperature great change, made that preferential steering reaction speed is fast, usually imperceptible hard spot when turning to beginning and during cold start-up.It is stable particularly can to adapt to the low-temperature operation steering behaviour at severe cold area.3, Safety performance height, the Safety performance of hydraulic steering system have influence on and reduce the probability that breaks down or lost efficacy, yet must possess from comfortable precision contact, even the driver of lack of skill also can guarantee steering safety between man-machine.The working pressure of the oil circuit each several part of hydraulic pressure original paper must be retained in the safety margins, so require whole system is chosen the safety coefficient of suitable size.4, emergent turning to satisfied performance requirement, enough provides two to turn to the circuit emergency power source from left to right.With reference to the emergent performance requirement that turns to of ISO_5010_1992 quarry tipper, stipulated mining dump truck when motor or steering power source random failure, the emergent minimum performance requirement that turns to.Emergent slew test: during the fault of the normal servosteering of requirement of experiment vehicle source, realize with the vehicle minimum turning radius that vehicle can be met an urgent need continuously and turn to 3 90 degree.The wherein emergent selection that turns to telecontrolled sequence valve in the loop is fallen coupling by its spring setting with commutator pressure and can be realized emergency turn under normal circumstances, and this telecontrolled sequence valve can play the flow-compensated control of steering procedure.5, the designing requirement of braking system guarantees that safety first is a main principle, and performance is followed braking system standard ISO 3450:1996 simultaneously.Adopt all-hydraulic braking, improve the brake of the speed of response of system.Significantly improve reliability, responsiveness, handling and servicing ease, reduced constituent elements on the whole.6, the emergent accumulator topping up loop that turns to, limit LS feedback flow by damping, unloading valve is set the accumulator supercharging pressure, reaches the supercharging pressure of setting when accumulator, the LS model off-load that unloading valve transmits damping, load-sensitive variable displacement pump discharge capacity vanishing simultaneously is in holding state.When energy storage pressure be reduced to set supercharging pressure 85% the time, unloading valve cuts out, the signal that damping is transmitted by shuttle valve relatively the flow of the responsive pump of back control load be output as the accumulator topping up and reach the setting supercharging pressure.7, hydraulic pressure cold start-up functional loop can turn to the load LS signal off-load of controlling with emergency brake accumulator topping up with meeting an urgent need by the commutation of control solenoid directional control valve, and the uncontrolled output flow of pump is zero like this, carries a responsive variable displacement pump and is in holding state.Hydraulic system was not carried out topping up work when hydraulic pressure cold start-up function was used for engine start, can realize that the motor no-load starts.8, wet brake jogging control/gearbox fluid power jogging control loop as oil sources, is set the pilot pressure that need by the decompression relief valve with the emergency brake accumulator.9, vehicle locking brake servo circuit, form logical relation by solenoid directional control valve and shuttle valve, when solenoid directional control valve all when electric, the pressure oil-source of emergent accumulator is crossed duplex brake petal valve and is acted directly on the Service Brake of wheel, can save unnecessary parking brake like this.Parking reliably when vehicle loading and unloading.10, Parking brake off and guide's control loop, one-way valve and solenoid directional control valve composite control Parking pincers dish brake off, one-way valve play pressure and keep function.11, hydraulic accumulator, moving system is equipped with main accumulator and auxiliary energy-storage device.Under situation about breaking down, can also carry out standby braking.Emergent accumulator satisfies the maximum effectively braking of service brake more than 5 times.Need be furnished with warning device in the system, when energy stored is lower than the peaked 50% time of regulation, inferior warning device is just reported to the police automatically.12, emergency braking control, in case of emergency, stopping brake can be used as emergency braking.If the voltage supply ability has all been lost in former and later two loops, can be by pressure relay control so that stopping brake should come into operation automatically.13, the pressure oil that the hoist control valve group provides with the public load-sensitive variable displacement pump of other control valve group is controlled in the container lifting in host computer system, realizes proportional control container lifting and container power decline function.14, the load-sensitive control loop of forming by proportional pressure valve, shuttle valve, guide's equilibrium valve, shuttle valve, unidirectional relief valve magnetic selector valve.Proportional control pilot pressure valve delivery pressure control equilibrium valve is opened, can proportional control flow by equilibrium valve, advantage is that the both proportional commutation function of this combinational logic relation also has bidirectional balanced function, make that container control is more reliable and comfortable, eliminated the terminal impact of container decline, can behind the mobile recoil acceleration of lifting end materials container, turn over by the balance container simultaneously the chassis.15, float function: in transportation process, carry out float function, prevent that oil cylinder load-bearing chamber is subjected to load shock, emergent container gravity descends if engine failure also can be controlled float function.
Description of drawings
The plan view of Fig. 1 braking in a turn valve piece;
Fig. 2 is the right elevation of Fig. 1;
Fig. 3 is the left view of Fig. 1;
Fig. 4 is the worm's eye view of Fig. 1;
Fig. 5 is the plan view of Fig. 1;
Fig. 6 is the rear view of Fig. 1;
Fig. 7 is the loop hydraulic control system figure of Fig. 1-Fig. 6;
Fig. 8 is the plan view of lifting valve piece;
Fig. 9 is the right elevation of Fig. 8;
Figure 10 is the left view of Fig. 8;
Figure 11 is the worm's eye view of Fig. 8;
Figure 12 is the rear view of Fig. 8;
Figure 13 is the loop hydraulic control system figure of Fig. 8-Figure 12.
Embodiment
The utility model is further described below in conjunction with accompanying drawing embodiment.
See that Fig. 1 has provided the plan view of braking in a turn valve piece.Interface on this braking in a turn valve piece end face comprises: connect the emergent accumulator pressurising interface M2 that turns to of test, connect emergency brake energy storage pressure remote alarm interface K4, connect emergency brake energy storage pressure remote alarm interface K2, connect ransaxle wheel limit service brake interface D2, connect and show gearbox fluid power jogging state interface M6, the interface B that connects two-way braking treadle valve output B2, connect brake lamp pilot pressure relay interface K5, connect Parking state pressure relay interface K3, interface Z, connect the valve group and leak interface Y, connect two-way braking treadle valve C2, connect the emergent accumulator interface XNQ1 that turns to, connect gearbox fluid power jogging control interface BS, the interface LSS that connects commutator LS connects load-sensitive variable displacement pump interface LS, connect test load feedback pressure interface M3.
See that Fig. 2 has provided the right elevation of braking in a turn valve piece.Interface on this braking in a turn valve piece end face comprises: connect load-sensitive variable displacement pump interface LS, connect emergency brake accumulator interface XNQ3, connect valve group leakage interface Y.
See that Fig. 3 has gone out the left view of braking in a turn valve piece.Interface on this braking in a turn valve piece end face comprises: connect test pumping hole working pressure interface M1, connect the emergent energy storage pressure remote alarm interface K1 that turns to.
See that Fig. 4 has gone out the worm's eye view of braking in a turn valve piece.Interface on this braking in a turn valve piece end face comprises: connect the first load-sensitive variable displacement pump interface P1, connect the second load-sensitive variable displacement pump interface P2, connect guide's control interface Pi.
See that Fig. 5 has gone out the plan view of braking in a turn valve piece.Interface on this braking in a turn valve piece end face comprises: the interface T that connects commutator pressure hydraulic fluid port interface S, the oil return of valve group.
See that Fig. 6 has gone out the rear view of braking in a turn valve piece.Interface on this braking in a turn valve piece end face comprises: connection Parking Brake interface BP, the interface A that connects standby emergency brake accumulator interface XNQ2, connection emergency brake accumulator interface XNQ4, the interface C1 that connects two-way braking treadle valve P1, connection steering axle wheel limit service brake interface D1, connection two-way braking treadle valve output B1, connection valve group oil return interface T.
See that Fig. 7 has provided the loop hydraulic control system figure of Fig. 1 to Fig. 6.Described braking in a turn valve piece hydraulic circuit system comprises: emergent accumulator topping up loop, emergency brake accumulator topping up loop, hydraulic pressure cold start-up functional loop, preferential dynamic steering loop, wet brake jogging control loop, gearbox fluid power jogging guide control, vehicle locking brake servo circuit, Parking brake off and guide's control loop, the container lifting control loop of turning to.In this was novel, described meeting an urgent need turned to accumulator topping up loop, is made up of damping CT25, damping CT26, one-way valve CT29, unloading valve CT36, telecontrolled sequence valve CT30, one-way valve CT31, damping CT34, solenoid directional control valve CT35; Variable displacement pump interface P1, P2 connect two load-sensitive variable displacement pump CT19, CT22 respectively by pipeline and realize the double pump interflow; Accumulator interface XNQ1 connects accumulator by pipeline; Turn to dynamic socket LS to connect two load sensitive pumps by pipeline; The valve group is leaked interface Y, valve group oil return interface T and is connected hydraulic oil container by pipeline; Commutator pressure hydraulic fluid port interface S connects hydraulic steering gear by pipeline, and the interface LSS that connects commutator LS connects the hydraulic steering gear feedback port by pipeline, when realizing the operation commutator steering load signal is passed to the interface LSS that connects commutator LS.In this was novel, described emergency brake accumulator topping up loop was made up of damping CT23, damping CT17, one-way valve CT16, unloading valve CT18; The XNQ2 mouth connects accumulator by pipeline, the BP mouth connects the Parking clipper disk brake by pipeline, the XNQ3 mouth respectively is connected an accumulator with the XNQ4 mouth by pipeline, the Pi mouth connects the pilot control opening of two-way braking treadle valve by pipeline, C1, the C2 mouth connects two inlet openings of two-way braking treadle valve by pipeline, A, the B mouth connects two delivery outlets of two-way braking treadle valve by pipeline, the D1 mouth connects the clipper disk brake of Vehicular turn wheels by pipeline, the D2 mouth is by the clipper disk brake of pipeline connection vehicle drive axle wheels, and the BS mouth is connected to the fluid power jogging control mouth of vehicle gear box by pipeline.Realization is to the braking control of gearbox, and K3, K4, K5 mouth connect pressure switch.Realization is to the Pressure testing and the warning function of motor vehicle braking system.In this was novel, described hydraulic pressure cold start-up functional loop was made up of shuttle valve CT20, solenoid directional control valve CT21; The feedback signal of hydraulic system during to accumulator XNQ1 and accumulator XNQ2 topping up all can enter into shuttle valve CT28, CT33 by shuttle valve CT20 output and flow to LS mouth control pump delivery, and pressure oil liquid can be branched off into solenoid directional control valve CT21 between shuttle valve CT20 and shuttle valve CT28.If solenoid directional control valve gets, can flow to the Y mouth by solenoid directional control valve CT21 from the pressure oil liquid of shuttle valve CT20 output, the Y mouth is connected to hydraulic oil container by pipeline, this moment is from the oil liquid pressure vanishing of shuttle valve CT20 output like this, the pressure that promptly is transferred to the LS mouth is zero, the flow of air pump inoperative output is zero, and solenoid directional control valve CT21 has played the effect of intervening the accumulator topping up like this, and this effect is named as the cold start-up function.In this was novel, described preferential dynamic steering loop was made up of priority valve CT24, damping CT27, shuttle valve CT28, damping CT37; The LSS mouth connects the feedback port of commutator by pipeline, the S mouth connects the filler opening of commutator by pipeline, the feedback port of commutator and the return opening of commutator are connected when the meta of commutator inside, the fluid of pumping hole output is branched off into two-way after by damping CT27, and the road binders liquid damping CT37 that flows through enters into the feedback port of commutator by the LSS mouth; Another road binders liquid by damping CT27 output enters into shuttle valve CT28.In this was novel, described wet brake jogging control loop was made up of shuttle valve CT7, solenoid directional control valve CT39, decompression relief valve CT40; The B mouth connects the pressure hydraulic fluid port of wet brake by pipeline; The pressure oil-source of reduction valve CT40 comes from accumulator XNQ2, flow to solenoid directional control valve CT39 by the post-decompression fluid of reduction valve CT40, if solenoid directional control valve CT39 gets electric commutation, pressure oil liquid enters into shuttle valve CT7 after by solenoid directional control valve CT39, outputs to the B mouth from shuttle valve CT7 and enters into wet brake.In this was novel, described gearbox fluid power jogging guide control was made up of decompression relief valve CT41, damping CT42, one-way valve CT43, solenoid directional control valve CT44; The BS mouth connects the hydraulic changeover control mouth of gearbox by pipeline; Come from flow through after the decompression of pressure oil liquid of accumulator XNQ2 damping CT42, one-way valve CT43 and flow to solenoid directional control valve CT44 by reduction valve CT41.In this was novel, described vehicle locking brake servo circuit was made up of solenoid directional control valve CT3, CT4, CT5, CT6; C1, C2 mouth connect the inlet opening of two-way braking treadle valve by pipeline, A, B mouth connect the delivery outlet of two-way braking treadle valve by pipeline, the D1 mouth connects the front steering axle clipper disk brake by pipeline, and the D2 mouth connects the wet multi-disk brake of rear drive sprocket by pipeline.In this was novel, described Parking brake off and guide's control loop were made up of one-way valve CT12, solenoid directional control valve CT8; By guide's control loop that decompression relief valve CT2, solenoid directional control valve CT1 form, the P mouth connects the vehicle Parking Brake by pipeline, and the Pi mouth connects extraneous assist control executive component by pipeline.
See that Fig. 8 has provided the plan view of hoist control valve piece.Interface on this hoist control valve piece end face comprises: connect Z interface, L interface that test guide pilot pressure meets M4, interface R, connects braking in a turn valve piece Z interface.
See that Fig. 9 has provided the right elevation of hoist control valve piece.Interface on this hoist control valve piece end face comprises: connect emergent accumulator punching press interface M2, test load feedback pressure interface M3, the connection load-sensitive variable displacement pump interface LS of turning to of test.
See that Figure 10 has provided the left view of hoist control valve piece.Interface on this hoist control valve piece end face comprises: the interface P that connects valve group oil return interface T, connection braking in a turn valve piece hydraulic circuit system interface P.
See that Figure 11 has provided the worm's eye view of hoist control valve piece.Interface on this hoist control valve piece end face comprises: four interface CT46 that connect guide's equilibrium valve.
See that Figure 12 has provided the plan view of hoist control valve piece.Interface on this hoist control valve piece end face comprises: connect the valve group and leak interface Y, interface M5.
See that Figure 13 has provided the loop hydraulic control system figure of Fig. 8-Figure 12.The hydraulic circuit system of described hoist control valve piece, by proportional pressure valve CT45, shuttle valve CT47, pilot operated directional control valve CT51, guide control equilibrium valve CT46, shuttle valve CT48, unidirectional relief valve CT49, solenoid directional control valve CT50 form; Interface R is by the rodless cavity of pipeline connection container elevating ram, and interface L connects the container elevating ram by pipeline.
In this was novel, the high integrated screw-in cartridge valve of the non-highway dump truck of described large-tonnage was made up of braking in a turn valve piece and hoist control valve piece two-part; In described braking in a turn valve piece, hoist control valve piece, be respectively equipped with braking in a turn hydraulic circuit system and lifting control hydraulic circuit system, this braking in a turn hydraulic circuit system, lifting control hydraulic circuit system is communicated with interface on braking in a turn valve piece, the hoist control valve piece, and described interface to brake valve piece and hoist control valve piece is connected to each other.
In this was novel, the interface Z of hydraulic circuit system on the described braking in a turn valve piece was connected by pipeline with the interface Z of hydraulic circuit system on the described hoist control valve piece; The interface P of the hydraulic circuit system on the described braking in a turn valve piece on the interface P of hydraulic circuit system and the described hoist control valve piece is connected by pipeline; On the described braking in a turn valve piece on the interface LSH of hydraulic circuit system and the described hoist control valve piece interface LS of hydraulic circuit system be connected by pipeline; On the described braking in a turn valve piece on the interface Y of hydraulic circuit system and the described hoist control valve piece interface Y of hydraulic circuit system be connected by pipeline; On the described braking in a turn valve piece on the interface T of hydraulic circuit system and the described hoist control valve piece hydraulic oil container interface T of hydraulic circuit system be connected.
In this was novel, not marking interface in described braking in a turn valve piece, the hoist control valve piece accompanying drawing was auxiliary hole.
The braking in a turn valve piece hydraulic circuit system working principle that this is novel:
Meet an urgent need and turn to accumulator topping up loop: form by damping CT25, damping CT26, one-way valve CT29, unloading valve CT36, telecontrolled sequence valve CT30, one-way valve CT31, damping CT34, solenoid directional control valve CT35.Variable displacement pump interface P1, P2 connect two load-sensitive variable displacement pump CT19, CT22 respectively by pipeline and realize the double pump interflow; Accumulator interface XNQ1 connects accumulator by pipeline; Turn to dynamic socket LS to control, be used for the output discharge capacity of control pump by the pressure compensation that pipeline connects two load sensitive pumps; The valve group is leaked interface Y, valve group oil return interface T and is connected hydraulic oil container by pipeline; Commutator pressure hydraulic fluid port interface S connects hydraulic steering gear by pipeline, for hydraulic steering gear provides oil sources; The interface LSS that connects commutator LS connects the hydraulic steering gear feedback port by pipeline, when realizing the operation commutator steering load signal is passed to the interface LSS that connects commutator LS.During application, double pump interflow CT19, CT22 output flow flow to guide's control, damping CT23, damping CT27, the one-way valve CT32 of relief valve CT15, pressure tap M1, damping CT25, telecontrolled sequence valve CT30 on the way simultaneously, wherein flow to the fluid shunting of damping CT25, the one-way valve CT29 of leading up to enters into accumulator interface XNQ1 and carries out topping up, solenoid directional control valve CT35 got the electric fluid that makes among the accumulator XNQ1 of closing and can not lay down this moment, was in closed condition owing to be subjected to the control telecontrolled sequence valve CT30 of interface P1, P2 pressure oil; Another road binders liquid is gone to unloading valve CT36 and shuttle valve CT20 simultaneously by damping CT26, flow to the pressure compensation control mouthful control pump delivery that interface LS enters two load-sensitive variable displacement pumps through the pressure ratio of shuttle valve CT28 and CT33 after, the suitable flow of output is an accumulator XNQ1 topping up, unloading valve CT36 opens reach the pressure of setting when the accumulator supercharging pressure after, the fluid zero pressure off-load that flow to interface LS, the control of the pressure compensation of pump does not have pilot pressure like this, pump delivery vanishing not output flow is ready, if the supercharging pressure of accumulator XNQ1 drops at 85% o'clock that sets supercharging pressure, unloading valve CT36 closes, the fluid that flow to interface LS is in pressure state, and pump delivery becomes big output flow and replenishes fluid for accumulator XNQ1 to reach setting pressure always like this.Emergency brake accumulator topping up loop: form by damping CT23, damping CT17, one-way valve CT16, unloading valve CT18.The XNQ2 mouth connects accumulator by pipeline, interface BP connects the Parking clipper disk brake by pipeline, interface XNQ3 respectively is connected an accumulator with interface XNQ4 by pipeline, interface Pi connects the pilot control opening of two-way braking treadle valve by pipeline, interface C1, C2 connects two inlet openings of two-way braking treadle valve by pipeline, interface A, B connects two delivery outlets of two-way braking treadle valve by pipeline, interface D1 connects the clipper disk brake of Vehicular turn wheels by pipeline, interface D2 connects the clipper disk brake of vehicle drive axle wheels by pipeline, interface BS controls interface K3 by the existing braking to gearbox of fluid power jogging control cause for gossip that pipeline is connected to vehicle gear box, K4, the pressure switch that connects K5 realizes Pressure testing and the warning function to motor vehicle braking system.During application, the fluid of pump output enters one-way valve CT16 by damping CT23 and enters into accumulator XNQ2, by flowing to the XNQ3 of subordinate simultaneously after the reduction valve CT13 decompression and XNQ4 carries out the pressure deposit.Fluid flows through damping CT17 arrival unloading valve CT18 and passes through shuttle valve CT20 simultaneously, CT28, after the comparison of CT33 by the responsive variable pump delivery of interface LS control load, the flow that output suits is to accumulator XNQ2, XNQ3, XNQ4 carries out topping up, unloading valve CT18 has set the supercharging pressure of accumulator, when the supercharging pressure that detects accumulator XNQ2 as unloading valve CT18 reaches setting pressure, unloading valve CT18 opens the pressure signal zero pressure off-load by damping CT17, the pressure that is delivered to interface LS like this is zero, pump delivery vanishing this moment not output flow is ready, when the pressure of accumulator XNQ2 drop to that unloading valve CT18 pressure sets 85% the time, unloading valve CT18 closes again the change of control pump discharge capacity and reaches 100% of setting up to supercharging pressure greatly, unloading valve was opened after topping up finished, and the pump delivery vanishing is ready.Hydraulic pressure cold start-up functional loop: form hydraulic pressure cold start-up loop by shuttle valve CT20, solenoid directional control valve CT21, be used to realize motor no-load start-up control.The feedback signal of hydraulic system during to accumulator XNQ1 and accumulator XNQ2 topping up all can enter into shuttle valve CT28 by shuttle valve CT20 output, CT33 flows to LS mouth control pump delivery, pressure oil liquid can be branched off into solenoid directional control valve CT21 between shuttle valve CT20 and shuttle valve CT28, if solenoid directional control valve gets, can flow to interface Y by solenoid directional control valve CT21 from the pressure oil liquid of shuttle valve CT20 output, interface Y is connected to hydraulic oil container by pipeline, this moment is from the oil liquid pressure vanishing of shuttle valve CT20 output like this, the pressure that promptly is transferred to interface LS is zero, the flow of air pump inoperative output is zero, solenoid directional control valve CT21 has played the effect of intervening the accumulator topping up like this, and this effect is named as the cold start-up function.The preferential dynamic steering loop that present embodiment has: form preferential dynamic steering loop by priority valve CT24, damping CT27, shuttle valve CT28, damping CT37, by realizing preferential dynamic steering, improve the responsiveness and the reliability that turn to the responsive commutator coupling of dynamic load.Interface LSS is by the feedback port of pipeline connection commutator, and interface S is by the filler opening of pipeline connection commutator, and the feedback port of commutator and the return opening of commutator link together when the meta of commutator inside.During application, the fluid of pumping hole output is branched off into two-way after by damping CT27, the one road binders liquid damping CT37 that flows through enters into the feedback port of commutator by interface LSS, because meta feedback port and return opening did not link together when commutator was not worked, get back to fuel tank from the commutator of flowing through of the fluid of damping CT27 output like this, be in state of activation, this phenomenon is named as and turns to dynamical feedback.Enter into shuttle valve CT28 from another road binders liquid of damping CT27 output, the pressure oil of shuttle valve CT28 output removes to control priority valve CT24 and is in closed condition, make the fluid of pump output preferentially satisfy to turn to and brake, simultaneously also go to control pump delivery, this combination phenomenon to be named as and preferentially turn to the loop.Wet brake jogging control loop: form wet brake jogging control loop by shuttle valve CT7, solenoid directional control valve CT39, decompression relief valve CT40, descending relies on wet brake pressure control braking jogging in the time of can realizing vehicle length.Interface B connects the pressure hydraulic fluid port of wet brake by pipeline.The pressure oil-source of reduction valve CT40 comes from accumulator XNQ2, flow to solenoid directional control valve CT39 by the post-decompression fluid of reduction valve CT40, if solenoid directional control valve CT39 gets electric commutation, pressure oil liquid enters into shuttle valve CT7 after by solenoid directional control valve CT39, output to interface B from shuttle valve CT7 and enter into wet brake, make the oil liquid pressure of wet brake keep a definite value, play a definite value brake phenomenon, this combined loop called after wet brake jogging control loop.The gearbox fluid power jogging guide control that present embodiment has: form gearbox fluid power jogging guide control loop by decompression relief valve CT41, damping CT42, one-way valve CT43, solenoid directional control valve CT44, be used to control gearbox fluid power jogging auxiliary braking.Interface BS connects the hydraulic changeover control mouth of gearbox by pipeline.Come from flow through after the decompression of pressure oil liquid of accumulator XNQ2 damping CT42, one-way valve CT43 and flow to solenoid directional control valve CT44 by reduction valve CT41, can export the pressure state of fluid by control interface BS by must cutting off the power supply of solenoid directional control valve CT44, thereby control the fluid power jogging operation of gearbox.Vehicle locking brake servo circuit: by the loop that solenoid directional control valve CT3, CT4, CT5, CT6 form, the control wheel limit service brake that realizes bypassing the immediate leadership can be so that vehicle relies on service brake locking vehicle when unloading or loading.Interface C1, C2 connect the inlet opening of two-way braking treadle valve by pipeline, interface A, B connect the delivery outlet of two-way braking treadle valve by pipeline, interface D1 connects the front steering axle clipper disk brake by pipeline, and interface D2 connects the wet multi-disk brake of rear drive sprocket by pipeline.During driver operation two-way treadle valve, the pressure oil of two-way treadle valve output is by interface A, B is through solenoid directional control valve CT3, CT6 enters into interface D1, D2 controls the break of front and back wheels respectively, when implementing the locking braking, solenoid directional control valve CT3, CT4, CT5, CT6 simultaneously, solenoid directional control valve CT3, CT6 closes, CT4, CT5 is open-minded, accumulator XNQ3, pressure oil among the XNQ4 can be by the solenoid directional control valve CT4 that opens, CT5 directly enters into interface D1, clipper disk brake before and after the D2 control, this locking brake operating driver only need operate an Electromagnetic push-button and get final product, and need not to step for a long time the two-way braking footrest.The Parking brake off that present embodiment has and guide's control loop: the loop of being made up of one-way valve CT12, solenoid directional control valve CT8 is used for the freeing vehicle parking braking; By guide's control loop that decompression relief valve CT2, solenoid directional control valve CT1 form, can realize auxiliary braking or standby guide control etc.Interface BP connects the vehicle Parking Brake by pipeline, and interface Pi connects extraneous assist control executive component by pipeline.Arrive solenoid directional control valve CT8 by flow through one-way valve CT9, CT12 of the post-decompression pressure oil of reduction valve CT13, control solenoid directional control valve CT8 electrical interface BP pressure oil output is removed Parking Brake.Arrive solenoid directional control valve CT1 by the post-decompression pressure oil of reduction valve CT13 one-way valve CT9, the reduction valve CT2 secondary decompression back of flowing through equally, the extraneous assist control executive component that the power on/off state of control solenoid directional control valve CT1 can control interface Pi connects.
The hoist control valve piece hydraulic circuit system working principle that this is novel:
Container lifting control loop: control equilibrium valve CT46, shuttle valve CT48, unidirectional relief valve CT49, solenoid directional control valve CT50 by proportional pressure valve CT45, shuttle valve CT47, pilot operated directional control valve CT51, guide and form container lifting control, can realize container lifting and decline ratio Balance Control, and container floats and elevating ram anti-cavitation function.Interface R is by the rodless cavity of pipeline connection container elevating ram, and interface L connects the rod chamber of container elevating ram by pipeline.Provide pressure oil-source by reduction valve CT14 for proportional pressure-reducing valve CT45, two guide's equilibrium valve ratios in the middle of the proportional pressure-reducing valve CT45 control of 1PWM control are opened, and R provides pressure oil-source for interface.Proportional pressure-reducing valve CT45 control two guide's equilibrium valve CT46 ratios up and down of 2PWM control are opened, and L provides pressure oil-source for interface.Any one proportional pressure-reducing valve CT45 get electric in, control the commutation of pilot operated directional control valve CT51 by shuttle valve CT47 by the pressure oil of proportional pressure-reducing valve CT45 output, can export the load pressure signal that passes out from shuttle valve CT48 to shuttle valve CT33 by pilot operated directional control valve CT51, provide required flow for the container elevating ram by two load-sensitive variable pump deliveries of interface LS control.The effect of solenoid directional control valve CT50 is electricly can be communicated to fuel tank to the fluid of interface R when solenoid directional control valve CT50 gets, and the oil cylinder that makes interface R connect does not like this stress, and plays floating action.The effect of unidirectional relief valve CT49 is the working pressure that restriction interface L connects oil cylinder, protects.One-way valve in parallel plays the effect of repairing, promptly when interface L produces vacuum, can be the oil cylinder repairing of interface L connection by one-way valve.
Annotate: double dot dash line
The border in expression loop; Dotted line--------control oil channel in----expression loop or leakage oil circuit;
Solid line---pressure or oil return circuit in the expression loop;
Represent that two oil circuits intersect but do not link to each other;
Claims (14)
1. the high integrated screw-in cartridge valve of the non-highway dump truck of large-tonnage is characterized in that, comprises braking in a turn valve piece and hoist control valve piece two-part composition; In described braking in a turn valve piece, hoist control valve piece, be respectively equipped with braking in a turn hydraulic circuit system and lifting control hydraulic circuit system, this braking in a turn hydraulic circuit system, lifting control hydraulic circuit system is communicated with interface on braking in a turn valve piece, the hoist control valve piece, and described brake valve piece and hoist control valve piece are connected to each other by interface.
2. the high integrated screw-in cartridge valve of the non-highway dump truck of large-tonnage according to claim 1, it is characterized in that, described each end face interface of braking in a turn valve piece comprises: connect the emergent accumulator pressurising M2 interface that turns to of test, connect emergency brake energy storage pressure remote alarm interface K4, connect emergency brake energy storage pressure remote alarm interface K2, connect ransaxle wheel limit service brake interface D2, connect and show gearbox fluid power jogging state interface M6, the interface B that connects two-way braking treadle valve output B2, connect brake lamp pilot pressure relay interface K5, connect Parking state pressure relay interface K3, interface Z, connect the valve group and leak interface Y, connect two-way braking treadle valve C2, connect the emergent accumulator interface XNQ1 that turns to, connect gearbox fluid power jogging control interface BS, the interface LSS that connects commutator LS connects load-sensitive variable displacement pump interface LS, connect test load feedback pressure interface M3; Connect load-sensitive variable displacement pump interface LS, connect emergency brake accumulator interface XNQ3, connect valve group leakage interface Y; C, connection test pumping hole working pressure interface M1, the emergent energy storage pressure remote alarm interface K1 that turns to of connection; Connect the first load-sensitive variable displacement pump interface P1, connect the second load-sensitive variable displacement pump interface P2, connect guide's control interface Pi; The interface T that connects commutator pressure hydraulic fluid port interface S, the oil return of valve group; Connection Parking Brake interface BP, the interface A that connects standby emergency brake accumulator interface XNQ2, connection emergency brake accumulator interface XNQ4, the interface C1 that connects two-way braking treadle valve P1, connection steering axle wheel limit service brake interface D1, connection two-way braking treadle valve output B1, connection valve group oil return interface T.
3. the high integrated screw-in cartridge valve of the non-highway dump truck of large-tonnage according to claim 1, it is characterized in that each end face interface of described hoist control valve piece comprises: the Z interface, the L interface that connect test guide pilot pressure interface M4, interface R, connection braking in a turn valve piece; Connect emergent accumulator punching press interface M2, test load feedback pressure interface M3, the connection load-sensitive variable displacement pump interface LS of turning to of test; The interface P that connects valve group oil return interface T, connection braking in a turn valve piece hydraulic circuit system; Four interface CT46 that connect guide's equilibrium valve; Connect the valve group and leak interface Y, interface M5.
4. the high integrated screw-in cartridge valve of the non-highway dump truck of large-tonnage according to claim 1, it is characterized in that, the interface Z of hydraulic circuit system on the described braking in a turn valve piece is connected by pipeline with the interface Z of hydraulic circuit system on the described hoist control valve piece; On the described braking in a turn valve piece on the interface P of hydraulic circuit system and the described hoist control valve piece interface P of hydraulic circuit system be connected by pipeline; On the described braking in a turn valve piece on the LSH interface of hydraulic circuit system and the described hoist control valve piece interface LS of hydraulic circuit system be connected by pipeline; On the described braking in a turn valve piece on the interface Y of hydraulic circuit system and the described hoist control valve piece interface Y of hydraulic circuit system be connected by pipeline; On the described braking in a turn valve piece on the interface T of hydraulic circuit system and the described hoist control valve piece hydraulic oil container interface T of hydraulic circuit system be connected.
5. the high integrated screw-in cartridge valve of the non-highway dump truck of large-tonnage according to claim 1, it is characterized in that described braking in a turn valve piece hydraulic circuit system comprises: turn to accumulator topping up loop, emergency brake accumulator topping up loop, hydraulic pressure cold start-up functional loop, preferential dynamic steering loop, wet brake jogging control loop, gearbox fluid power jogging guide control, vehicle locking brake servo circuit, Parking brake off and guide's control loop.
6. the high integrated screw-in cartridge valve of the non-highway dump truck of large-tonnage according to claim 5, it is characterized in that, described meeting an urgent need turns to accumulator topping up loop, is made up of damping CT25, damping CT26, one-way valve CT29, unloading valve CT36, telecontrolled sequence valve CT30, one-way valve CT31, damping CT34, solenoid directional control valve CT35; Variable displacement pump interface P1, P2 connect one-way valve CT19, the CT22 of two load-sensitive variable displacement pumps respectively by pipeline; Accumulator interface XNQ1 connects accumulator by pipeline; Interface LS connects two load sensitive pumps by pipeline; The valve group is leaked interface Y, valve group oil return interface T and is connected hydraulic oil container by pipeline; Commutator pressure hydraulic fluid port interface S connects hydraulic steering gear by pipeline, and the interface LSS that connects commutator LS connects the hydraulic steering gear feedback port by pipeline, makes the steering load signal pass to the interface LSS that connects commutator LS by commutator.
7. the high integrated screw-in cartridge valve of the non-highway dump truck of large-tonnage according to claim 5 is characterized in that described emergency brake accumulator topping up loop is made up of damping CT23, damping CT17, one-way valve CT16, unloading valve CT18; Interface XNQ2 connects accumulator by pipeline, interface BP connects the Parking clipper disk brake by pipeline, interface XNQ3 respectively is connected an accumulator with XNQ4 by pipeline, interface Pi connects guide's control interface of two-way braking treadle valve by pipeline, interface C1, C2 connects two inlet openings of two-way braking treadle valve by pipeline, interface A, B connects the clipper disk brake of two delivery outlet interface D1 of two-way braking treadle valve by pipeline connection Vehicular turn wheels by pipeline, interface D2 is by the clipper disk brake of pipeline connection vehicle drive axle wheels, and interface BS is connected to the fluid power jogging control interface of vehicle gear box by pipeline.
8. the high integrated screw-in cartridge valve of the non-highway dump truck of large-tonnage according to claim 5 is characterized in that described hydraulic pressure cold start-up functional loop is made up of shuttle valve CT20, solenoid directional control valve CT21; The feedback signal of hydraulic system during to accumulator XNQ1 and accumulator XNQ2 topping up all can enter into shuttle valve CT28, CT33 by shuttle valve CT20 output and flow to LS mouth control pump delivery, pressure oil liquid can be branched off into solenoid directional control valve CT21 between shuttle valve CT20 and shuttle valve CT28, get by solenoid directional control valve, can flow to interface Y by solenoid directional control valve CT21 from the pressure oil liquid of shuttle valve CT20 output, interface Y is connected to hydraulic oil container by pipeline.
9. the high integrated screw-in cartridge valve of the non-highway dump truck of large-tonnage according to claim 5 is characterized in that described preferential dynamic steering loop is made up of priority valve CT24, damping CT27, shuttle valve CT28, damping CT37; Interface LSS connects the feedback port of commutator by pipeline, interface S connects the filler opening of commutator by pipeline, the feedback port of commutator and the return opening of commutator are connected when the meta of commutator inside, the fluid of pumping hole output is branched off into two-way after by damping CT27, and the road binders liquid damping CT37 that flows through enters into the feedback port of commutator by interface LSS; Another road binders liquid by damping CT27 output enters into shuttle valve CT28.
10. the high integrated screw-in cartridge valve of the non-highway dump truck of large-tonnage according to claim 5 is characterized in that, described wet brake jogging control loop is made up of shuttle valve CT7, solenoid directional control valve CT39, decompression relief valve CT40; Interface B connects the pressure hydraulic fluid port of wet brake by pipeline; The pressure oil-source of reduction valve CT40 comes from accumulator XNQ2, flow to solenoid directional control valve CT39 by the post-decompression fluid of reduction valve CT40, if solenoid directional control valve CT39 gets electric commutation, pressure oil liquid enters into shuttle valve CT7 after by solenoid directional control valve CT39, outputs to interface B from shuttle valve CT7 and enters into wet brake.
11. the high integrated screw-in cartridge valve of the non-highway dump truck of large-tonnage according to claim 5 is characterized in that, described gearbox fluid power jogging guide control is made up of decompression relief valve CT41, damping CT42, one-way valve CT43, solenoid directional control valve CT44; The BS mouth connects the hydraulic changeover control mouth of gearbox by pipeline; Come from flow through after the decompression of pressure oil liquid of accumulator XNQ2 damping CT42, one-way valve CT43 and flow to solenoid directional control valve CT44 by reduction valve CT41.
12. the high integrated screw-in cartridge valve of the non-highway dump truck of large-tonnage according to claim 5 is characterized in that described vehicle locking brake servo circuit is made up of solenoid directional control valve CT3, CT4, CT5, CT6; Interface C1, C2 connect the inlet opening of two-way braking treadle valve by pipeline, interface A, B connect the delivery outlet of two-way braking treadle valve by pipeline, interface D 1 connects the front steering axle clipper disk brake by pipeline, and interface D2 connects the wet multi-disk brake of rear drive sprocket by pipeline.
13. the high integrated screw-in cartridge valve of the non-highway dump truck of large-tonnage according to claim 5 is characterized in that described Parking brake off and guide's control loop are made up of one-way valve CT12, solenoid directional control valve CT8; By guide's control loop that decompression relief valve CT2, solenoid directional control valve CT1 form, interface P connects the vehicle Parking Brake by pipeline, and interface Pi connects extraneous assist control executive component by pipeline.
14. the high integrated screw-in cartridge valve of the non-highway dump truck of large-tonnage according to claim 1, it is characterized in that, described hoist control valve piece hydraulic circuit system, by proportional pressure valve CT45, shuttle valve CT47, pilot operated directional control valve CT51, guide control equilibrium valve CT46, shuttle valve CT48, unidirectional relief valve CT49, solenoid directional control valve CT50 form; Interface R is by the rodless cavity of pipeline connection container elevating ram, and interface L connects the container elevating ram by pipeline.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2010205894277U CN201866000U (en) | 2010-11-03 | 2010-11-03 | High-integration threaded cartridge valve of large-tonnage off-load dump truck |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2010205894277U CN201866000U (en) | 2010-11-03 | 2010-11-03 | High-integration threaded cartridge valve of large-tonnage off-load dump truck |
Publications (1)
| Publication Number | Publication Date |
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| CN201866000U true CN201866000U (en) | 2011-06-15 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2010205894277U Expired - Fee Related CN201866000U (en) | 2010-11-03 | 2010-11-03 | High-integration threaded cartridge valve of large-tonnage off-load dump truck |
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| Country | Link |
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| CN (1) | CN201866000U (en) |
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102815335A (en) * | 2012-09-06 | 2012-12-12 | 三一矿机有限公司 | Steering and braking integrated control system and mineral dumper |
| CN106402058A (en) * | 2016-10-28 | 2017-02-15 | 北京科技大学 | Valve block assembly of pure electric dump truck hydraulic lifting system |
| CN108240366A (en) * | 2018-01-25 | 2018-07-03 | 陈艳艳 | A kind of flow divider valve for excavator hydraulic pressure accessory |
| CN109139740A (en) * | 2017-06-13 | 2019-01-04 | 朱圣明 | Novel 2AT, 3AT hydraulic valve plate assembly for new-energy automobile |
| CN109555747A (en) * | 2019-02-01 | 2019-04-02 | 杭叉集团股份有限公司 | A kind of forklift hydraulic system and fork truck pile-up valve |
| CN110566521A (en) * | 2019-08-23 | 2019-12-13 | 安徽合力股份有限公司 | automatic explosion-proof fork truck hydraulic system of control |
| CN111043090A (en) * | 2019-10-14 | 2020-04-21 | 武汉船用机械有限责任公司 | Hydraulic control system for a water jet propulsion device |
| CN115339511A (en) * | 2022-09-02 | 2022-11-15 | 厦门威迪思汽车设计服务有限公司 | Electrohydraulic control steering system |
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- 2010-11-03 CN CN2010205894277U patent/CN201866000U/en not_active Expired - Fee Related
Cited By (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102815335A (en) * | 2012-09-06 | 2012-12-12 | 三一矿机有限公司 | Steering and braking integrated control system and mineral dumper |
| CN102815335B (en) * | 2012-09-06 | 2015-06-10 | 三一矿机有限公司 | Steering and braking integrated control system and mineral dumper |
| CN106402058A (en) * | 2016-10-28 | 2017-02-15 | 北京科技大学 | Valve block assembly of pure electric dump truck hydraulic lifting system |
| CN109139740A (en) * | 2017-06-13 | 2019-01-04 | 朱圣明 | Novel 2AT, 3AT hydraulic valve plate assembly for new-energy automobile |
| CN108240366A (en) * | 2018-01-25 | 2018-07-03 | 陈艳艳 | A kind of flow divider valve for excavator hydraulic pressure accessory |
| CN109555747A (en) * | 2019-02-01 | 2019-04-02 | 杭叉集团股份有限公司 | A kind of forklift hydraulic system and fork truck pile-up valve |
| CN109555747B (en) * | 2019-02-01 | 2023-08-25 | 杭叉集团股份有限公司 | Fork truck hydraulic system and fork truck integrated valve |
| CN110566521A (en) * | 2019-08-23 | 2019-12-13 | 安徽合力股份有限公司 | automatic explosion-proof fork truck hydraulic system of control |
| CN110566521B (en) * | 2019-08-23 | 2024-05-10 | 安徽合力股份有限公司 | Automatic explosion-proof fork truck hydraulic system of control |
| CN111043090A (en) * | 2019-10-14 | 2020-04-21 | 武汉船用机械有限责任公司 | Hydraulic control system for a water jet propulsion device |
| CN115339511A (en) * | 2022-09-02 | 2022-11-15 | 厦门威迪思汽车设计服务有限公司 | Electrohydraulic control steering system |
| CN115339511B (en) * | 2022-09-02 | 2024-02-27 | 厦门威迪思汽车设计服务有限公司 | Electrohydraulic control steering system |
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