CN100362247C - Double pump confluence type multi-way ratio control valve with load sensitivity information circuit - Google Patents

Double pump confluence type multi-way ratio control valve with load sensitivity information circuit Download PDF

Info

Publication number
CN100362247C
CN100362247C CNB2004100932229A CN200410093222A CN100362247C CN 100362247 C CN100362247 C CN 100362247C CN B2004100932229 A CNB2004100932229 A CN B2004100932229A CN 200410093222 A CN200410093222 A CN 200410093222A CN 100362247 C CN100362247 C CN 100362247C
Authority
CN
China
Prior art keywords
control valve
valve
flow control
series flow
pump
Prior art date
Application number
CNB2004100932229A
Other languages
Chinese (zh)
Other versions
CN1789733A (en
Inventor
刘富良
卢永松
东权
Original Assignee
卢永松
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 卢永松 filed Critical 卢永松
Priority to CNB2004100932229A priority Critical patent/CN100362247C/en
Publication of CN1789733A publication Critical patent/CN1789733A/en
Application granted granted Critical
Publication of CN100362247C publication Critical patent/CN100362247C/en

Links

Abstract

The present invention relates to a double pump confluence type multi-way ratio control valve with load sensitivity information circuits, which comprises an inlet (P1) of a pump (1), an inlet (P2) of a pump (2), an oil return port (T) of an oil tank, a telescopic mechanism ratio control valve (10), a derricking mechanism ratio control valve (20), an auxiliary roll mechanism ratio control valve (30), a primary volume mechanism ratio control valve (40), flow dividing valves (PC1), (PC2) and safety valves (R1), (R2), wherein the telescopic mechanism ratio control valve (10), the derricking mechanism ratio control valve (20), the auxiliary roll mechanism ratio control valve (30) and the primary volume mechanism ratio control valve (40) are connected in parallel with the inlets; the flow dividing valves (PC1), (PC2) and the safety valves (R1), (R2) are connected with outlets of the pumps; the load sensitivity information circuit is arranged among the telescopic mechanism ratio control valve, the derricking mechanism ratio control valve, the auxiliary roll mechanism ratio control valve and the primary volume mechanism ratio control valve; a circuit arranged between the pump (1) and the pump (2) is provided with a single/double pump automatic switching valve (PS) and a one-way valve (S), for automatically selecting the simple pump or the double pumps for oil supply. The invention has the advantages that the control performance is greatly enhanced; the invention can realize the stepless speed regulation of the ratios of a plurality of operating mechanisms under different load thereof; the output flow of valve interfaces connected to the telescopic mechanism ratio control valve, the derricking mechanism ratio control valve, the auxiliary roll mechanism ratio control valve and the primary volume mechanism ratio control valve is only in proportion to input commands, and has the price only 1/3 to 1/4 of the inlets.

Description

The responsive double pump confluent type of on-load multi-channel proportional control valve

Technical field

The present invention relates to a kind of hydraulic drive control device field.Particularly relate to and a kind ofly be widely used in, pay the on-load sensitivity double pump confluent type multi-channel proportional control valve of the control technique of volume four big actuators flexible, luffing, master file on the hydraulic mobile crane.The present invention equally also is applicable to all kinds of hydraulic construction machines, Hydraulic Drive in Vessel hoist, hydraulic wireline winch and engineering ship hydraulic pressure hoisting equipment.

Background technique

The main control valve of existing traditional type only is an on-off type reverser valve, can only handle actuator's action merely, valve itself can not stepless speed regulation, can not carry out two or two above actuators are handled simultaneously, the manoeuvring performance of hydraulic mobile crane is greatly affected, main control valve hydraulic schematic diagram as Figure 12 and manual control mode shown in Figure 13, be installed on the QY50 hydraulic mobile crane, the function that the double pump interflow is arranged, but maximum shortcoming is the hydraulic control master control valve of traditional type outside hydraulic control instruction is arranged, but belong to direction switching valve, can't realize proportionality velocity modulation, from A, the flow of B mouth output is subjected to the very big influence of load variations, handles work when can not carry out moving more than two and two.Manipulation can only be carried out, two or the work of two above actuators can not be handled simultaneously an actuator, and can not stepless speed regulation.

Figure 13 is the main control valve hydraulic schematic diagram of the outside maneuverability pattern that surges, and its shortcoming is the same with Figure 12, be the maneuverability pattern difference, and the volumetric efficiency of this valve is lower, has influenced the master file lifting velocity.

At present, the main control valve of external hoist complete machine and engineering machinery has developed into valve control and the pump control multi-channel proportional valve that electricity consumption liquid is handled, and can realization the outer wired remote of machine handle, and there is very big gap in the technical merit of the homemade above-mentioned main control valve of China with external.

Summary of the invention

Purpose of the present invention is exactly in order to overcome above-mentioned deficiency of the prior art, and a kind of responsive double pump confluent type of the on-load multi-channel proportional control valve that can realize the ratio stepless speed regulation of several actuators under different load separately is provided.

The objective of the invention is by providing a kind of responsive double pump confluent type of on-load multi-channel proportional control valve to realize with following structure:

The responsive double pump confluent type of a kind of on-load multi-channel proportional control valve comprises it is characterized in that input interface P1, P2, tank drainback interface T and the hydraulic system of pump 1 and pump 2:

Hydraulic system is provided with extending means proportional control valve, jib lubbing mechanism proportional control valve, pays volume mechanism proportional control valve, master file mechanism proportional control valve;

The inlet opening of commutation series flow control valve DV1 in the extending means proportional control valve, commutation series flow control valve DV2, diverter valve PC1 in the jib lubbing mechanism proportional control valve, safety valve R1 is connected in parallel on the P1 interface of pump 1; Commutation series flow control valve DV1 in the extending means proportional control valve, the delivery outlet of the commutation series flow control valve DV2 in the jib lubbing mechanism proportional control valve are connected respectively on extending means and the jib lubbing mechanism; The delivery outlet of diverter valve PC1, safety valve R1 is connected on the tank drainback interface T;

The inlet opening of paying commutation series flow control valve DV3 in the volume mechanism proportional control valve, commutation series flow control valve DV4, diverter valve PC2 in the master file mechanism proportional control valve, safety valve R2 is connected in parallel on the P2 interface of pump 2; The delivery outlet of paying commutation series flow control valve DV3, the commutation series flow control valve DV4 in the master file mechanism proportional control valve in the volume mechanism proportional control valve is connected respectively to be paid in volume mechanism and the master file mechanism; The delivery outlet of diverter valve PC2, safety valve R2 is connected on the tank drainback interface T;

Be provided with single double pump automatic transfer valve PS and one-way valve S between pump 1 and pump 2 series loops;

Extending means proportional control valve, jib lubbing mechanism proportional control valve, commutation series flow control valve DV1~DV4 one end of paying in volume mechanism proportional control valve, the master file mechanism proportional control valve are connected with hydraulic control instruction inlet opening Y1, Y3, Y5, Y7, and the other end is connected with hydraulic control instruction inlet opening Y2, Y4, Y6, Y8;

Be provided with load-sensitive information circuits LS between commutation series flow control valve DV1~DV4, load-sensitive information circuits LS has selected three logical valve SV1~SV3 combined, select the maximum load pressure of commutation series flow control valve DV1~DV4 feedback, be passed to that diverter valve PC1 and diverter valve PC2 carry out pressure and flow compensates automatically; Load-sensitive information circuits LS has also adopted logical valve SV4, only select the maximum load pressure of commutation series flow control valve DV1~DV2 feedback, be passed to single double pump automatic transfer valve PS, single double pump automatic transfer valve PS is switched to single pump input interface P1 fuel feeding to DV1 commutation series flow control valve and the work of DV2 commutation series flow control valve.

Described extending means proportional control valve comprises the extending means commutation series flow control valve DV1 that is connected in parallel with described diverter valve PC1, the commutation series flow control valve DV1 decompression recuperation valve SC1 that is connected in series; Commutation series flow control valve DV1 is provided with the A1 and the B1 of two interfaces of extending means, is connected level relief valve PR1 one time between commutation series flow control valve DV1 and the interface A1, is connected level relief valve PR2 one time between commutate series flow control valve DV1 and the interface B1.

Described jib lubbing mechanism proportional control valve comprises the jib lubbing mechanism commutation series flow control valve DV2 that is connected in parallel with described diverter valve PC1, the commutation series flow control valve DV2 decompression recuperation valve SC2 that is connected in series, commutation series flow control valve DV2 is provided with the A2 and the B2 of two interfaces of jib lubbing mechanism, be connected level relief valve PR3 one time between the A2 of commutation series flow control valve DV2 and interface, be connected level relief valve PR4 one time between the B2 of commutate series flow control valve DV2 and interface.

Described pair of volume mechanism proportional control valve comprises with described diverter valve PC2 is connected in parallel pays the commutation series flow control valve DV3 of a volume mechanism, the commutation series flow control valve DV3 decompression recuperation valve SC3 that is connected in series; Commutation series flow control valve DV3 is provided with the A3 and the B3 of two interfaces paying volume mechanism, is connected level relief valve PR5 one time between the A3 of commutation series flow control valve DV3 and interface.

Described master file mechanism proportional control valve comprises the commutation series flow control valve DV4 of master file mechanism that is connected in parallel with described diverter valve PC2, the commutation series flow control valve DV4 decompression recuperation valve SC4 that is connected in series, commutation series flow control valve DV4 is provided with the A4 and the B4 of two interfaces of jib lubbing mechanism, is connected level relief valve PR6 one time between the A4 of commutation series flow control valve DV4 and interface.

The pressure information inlet opening of all elements that network mutually among the load-sensitive information circuits LS is provided with to reaching all elements actions damping measure perfect cooperation, that improve dynamic performance.

Be provided with four logical valve SV1~SV4 in the load-sensitive information circuits altogether, first to the 3rd logical valve SV1~SV3 connects mutually, therefrom select the highest load pressure of four commutation series flow control valve DV1~DV4 feedback, and pass to two diverter valve PC1, PC2, the 4th logical valve SV4 selects highest load pressure flexible and luffing commutation series flow control valve feedback, passes to single double pump automatic transfer valve PS.

Flexible, luffing, pay volume and four proportional control valves of master file all can be provided with the hydraulic jack that manual control handle or hydraulic control are handled separately.

When adopting the hydraulic control maneuverability pattern, flexible, luffing, pay volume and four proportional control valves of master file, two end hydraulic jacks all are provided with air vent W1~W8.

This valve group provides the pressure source that declutches interface for master file and secondary volume oil motor break.Pump 1 is provided with off-load mouth V1, V2 with pump 2 outlet main relief valve R1, R2 separately.

Two pumps respectively are provided with pressure tap G1, G2, and the tank drainback interface is provided with oil return pressure tap G3.

Compared with prior art, the invention has the advantages that:

The main overall hydraulic parameter of this valve group is: rated working pressure 23~25Mpa, single pump displacement 160L/min, (the former is used for flexible and jib lubbing mechanism to double pump interflow 320L/min, the latter is used for master file and pays a volume mechanism) and in diesel engine speed high proper functioning during to 2200r.p.m and low speed 600r.p.m, outside hydraulic control maneuverability pattern, outer governor pressure 0.6~2.2Mpa, the manual control mode; Thrust 25~the 36kg of changeover valve core.

The more Japanese UCHIDA of the hydraulic pressure function ins and outs company like product that this valve group is comprised is more perfect, and in structural design and stack combinations mode, internal load information network loop constitutes the technical characterstic with oneself.

Flexible and luffing is single oil pump feed input, and master file automaticallyes switch when paying volume work or this inside of input, double pump interflow has automatic control function and relies on the instruction of valve internal loading information circuits LS circuit transmission to finish fully, need not the artificial instruction of giving in addition, reliable automatically pump 2 discharge capacities that stop flow backwards to pump 1 during the list oil pump feed, also need not to establish in addition outside the valve group control valve

Overcome traditional homemade main control valve can only singly grasp (promptly can only carry out manipulation work) to single execution can not stepless speed regulation, the shortcoming that can not handle simultaneously several actuators.Because all commutation series flow control valve DV1~DV4 inlets are provided with decompression recuperation valve SC1~SC4 in this valve group, they are networked mutually with logical valve SV1~SV3 and LS loop, thereby guarantee the ratio stepless speed regulation under variant load pressure when this valve group can not only realize singly grasping and grasping together, the A, B mouth output flow of series flow control valve DV1~DV4 of promptly respectively commutating is only proportional with the instruction (stirring angle as outer governor pressure size, operating handle) of input, and not influenced by each A, B mouth load variations.

For reaching the maximum energy-saving effect of valve control system, this valve group is provided with shunting PC1 and PC2 at pump 1 and pump 2 outlets, by LS loop and logical valve SV1~SV3, automatically select with maximum load pressure signal among the behaviour, making pump 1 and pump 2 export charge oil pressure automatically is complementary therewith, unnecessary discharge capacity branches to the T loop with this pressure, realized the dual coupling of pressure and flow, as be equipped with the load-sensitive variable pump systems, can realize not having the most energy-conservation power match system of shunting, this valve group needed only and changed inlet connection and transition connection this moment, changed the arrangement of inner LS loop and selector valve and got final product.

Be provided with complexity in this valve group, complete information on load network loop and several logical valves carries out the logic arrangement, eight different load information of four actuators are detected, transmit, select comparison automatically, duplicate, are divided into four the tunnel and lead to the valve member and the loop of different functions, and the terminal point that arrives at information on load is provided with the damping vibration attenuation device, the dynamic response and the static stability of each valve member action of automatic synchronization, and eliminate spurious oscillation.

Jib lubbing mechanism commutation series flow control valve DV2 in this valve group has unique function design, cooperated Xu Chong factory to adopt state-of-the-art in the world " load control valve of band overcompensation ", realization need not oil pump feed, only depend on jib deadweight, and safe, the free arm movement speed that falls that can coordinate mutually from motion tracking luffing moment variations.

Logical valve SV1~the SV4 of this valve group setting is for being threaded into the formula structure, can be screwed into the LS loop of valve group inside from the outer surface of valve group, when in debugging or work, breaking down, the whole valve group of needn't disintegrating, as long as logical valve is screwed out, check fast and judge whether the SL loop is unobstructed whether select self to move malfunctioning.The secondary relief valve PR1~PR6 that installs in this valve group is also for being threaded into the formula structure, main relief valve is that safety valve R1, R2 are that flange connects stacked system, the remote control unloading mouth of safety valve, for the break pressure source interface that declutches, pump 1 by-pass port, pump 1 pump 2 and oil return pressure tap G1~G3 are internal thread interface, connect external pipeline to make things convenient for the user.

In a word, the advance that manoeuvring performance increases substantially, having abundant technology to extend is worth, can realize the ratio stepless speed regulation of several actuators under different load separately, no matter an actuator is handled, still several actuators are handled simultaneously, all can keep original ratio stepless speed governing characteristic, to extending means, jib lubbing mechanism, pay volume mechanism, the valve interface output flow of master file mechanism is only proportional (as fluid control pressure with the input instruction, manual control handle angle), can progressively replace each old-fashioned homemade main operating valve set, price only is the 1/3-1/4 of import.

Description of drawings

Fig. 1 is the responsive double pump confluent type of the on-load multi-channel proportional control valve hydraulic schematic diagram of the outside hydraulic control control command of the present invention;

Fig. 2 is the responsive double pump confluent type of the on-load multi-channel proportional control valve hydraulic principle of stick control instruction of the present invention;

Fig. 3 is information on load network loop of the present invention and pump delivery pressure information circuits skeleton diagram;

Fig. 4 handles the responsive double pump confluent type of on-load proportional multi-path valve general assembly drawing for hydraulic control of the present invention;

Fig. 5 is the responsive double pump confluent type of manual control on-load of the present invention proportional multi-path valve general assembly drawing;

Fig. 6 is the commutate erection drawing of series flow control valve (DV valve) and pressure-compensated valve (SC valve) of the present invention;

Fig. 7 is the valve core structure figure of luffing commutation series flow control valve of the present invention;

Fig. 8 is the erection drawing of single double pump automatic transfer valve PS of the present invention and pump 2 outlet pressure compensators (PC2);

Fig. 9 is the structural drawing of diverter valve for pump 1 of the present invention with pump 2 outlet pressure compensators;

Figure 10 is the sectional drawing of logical valve of the present invention (SV valve);

Figure 11 is a partial L S return passage section of the present invention;

Figure 12 is a kind of main control valve hydraulic system principle figure of prior art;

Figure 13 is the main control valve hydraulic system principle figure of another kind of prior art.

Embodiment

Embodiment describes in further detail the present invention below in conjunction with accompanying drawing.

Fig. 1 to Figure 11 shows the responsive double pump confluent type of on-load of the present invention multi-channel proportional control valve mode of execution.

Fig. 1 is the on-load responsive type multi-channel proportional control valve hydraulic schematic diagram that outside hydraulic control is handled; Fig. 2 is the on-load responsive type multi-channel proportional control valve hydraulic schematic diagram of manual control mode, now says the name of sth. main symbol name among the figure bright as follows:

P1, P2 are the input interface of pump 1 and pump 2 discharge capacities

R1, R2 are the main relief valve that pump 1 and pump 2 export separately, are called safety valve in present embodiment;

PC1, PC2 are the pressure compensator that pump 1 and pump 2 export separately, are called diverter valve in present embodiment;

DV1 is an extending means commutation series flow control valve, claims flexible selector valve again;

DV2 is a jib lubbing mechanism commutation series flow control valve, claims the luffing selector valve again;

DV3 claims to pay the volume selector valve again for paying volume mechanism commutation series flow control valve;

DV4 claims the master file selector valve again for master file mechanism commutation series flow control valve;

SC1, SC2, SC3, SC4 are respectively the preposition reduction valve of inlet of DV1, DV2, DV3, DV4 commutation series flow control valve, are called the decompression recuperation valve in present embodiment;

PS is single double pump automatic transfer valve;

PR1, PR2, PR3, PR4 are secondary relief valve;

PR5, PR6 are secondary relief valve;

SV1, SV2, SV3, SV4 are the selector valve that is arranged on the LS load-sensitive information circuits, claim the fusiformis valve again, are called logical valve in present embodiment;

S is an one-way valve, claims safety check again;

T is logical tank drainback interface;

A1, A2, A3, A4, be to extending means, jib lubbing mechanism, pay the interface of rolling up mechanism, master file mechanism with B1, B2, B3, B4;

Y1~Y8 is outer liquid governor pressure inlet opening, claims hydraulic control instruction inlet opening in present embodiment;

H1, H2, H3, H4 for flexible, luffing, pay volume, master file Joystick separately, claim the manual control instruction again;

B be main, pay the volume break pressure source interface that declutches;

W1~W8 air vent;

V1, V2 are the mouth of off-load separately of R1 and R2;

G1, G2 are the pressure tap of pump 1 and pump 2;

G3 is the oil return pressure tap;

LS is the load-sensitive information circuits;

L is pump 1 by-pass port, is blocking up at ordinary times, need connect this mouthful by the user.

First kind of embodiment:

The responsive double pump confluent type of the on-load multi-channel proportional control valve of fluid control pressure instruction as shown in Figure 1.Its implementation process:

The hydraulic control instruction is to point to Y mouth input outer liquid governor pressure PX, by conventional its scope of GB is between 0.6~2.0MPa, the magnitude range of its expression input instruction signal, forward instruction is from hydraulic control instruction inlet opening Y1, Y3, Y5, Y7 input, and reverse instruction is from hydraulic control instruction inlet opening Y2, Y4, Y6, Y8 input.0.6MPa be the minimum instruction signal, 2.0MPa be maximum command signal, the pressure that surpasses 0.6Mpa just can make commutation series flow control valve DV1, the commutation series flow control valve DV2 in the jib lubbing mechanism proportional control valve 20 ' in the extending means proportional control valve 10 ', the spool unlatching of paying commutation series flow control valve DV3, the commutation series flow control valve DV4 in the master file mechanism proportional control valve 40 ' in the volume mechanism proportional control valve 30 ', and 2.0MPa is maximum the unlatching.The circulation area FX that it opens extending means commutation series flow control valve DV1, jib lubbing mechanism commutation series flow control valve DV2 that the back forms, pay the import and export of the commutation series flow control valve DV3 of volume mechanism, the commutation series flow control valve DV4 of master file mechanism changes and imports hydraulic control command signal size and be directly proportional.From interface A1, A2, A3, A4 and interface B1, B2, B3, B4 is to extending means, jib lubbing mechanism, pay volume mechanism, the flow QX of the interface output of master file mechanism is directly proportional with circulation area FX, therefore, so-called stepless proportionality velocity modulation is meant from extending means commutation series flow control valve DV1, jib lubbing mechanism commutation series flow control valve DV2, pay the commutation series flow control valve DV3 of volume mechanism, the interface A1 of the commutation series flow control valve DV4 of master file mechanism, A2, A3, A4 and interface B1, B2, B3, B4 output flow QX and hydraulic control input instruction signal are that forward instruction is from hydraulic control instruction inlet opening Y1, Y3, Y5, the Y7 input, reverse instruction is from hydraulic control instruction inlet opening Y2, Y4, Y6, Y8 is entered as proportional relation.

As use the interface Y1 input fluid control pressure 1.3MPa signal of commutation series flow control valve DV1 to extending means, commutation series flow control valve DV1 produces the 5mm displacement, open 1/2 maximum flow area, half discharge capacity of pump 1 flows to interface A through decompression recuperation valve SC1, commutation series flow control valve DV1, make telescopic oil cylinder protruding, the logical tank drainback of T that the oil return of oil cylinder is got back to this valve from the B interface of commutation series flow control valve DV1 is interfaced to fuel tank.

Because telescopic oil cylinder overcomes outer load, its load pressure PL detects mouth from the pressure of commutation series flow control valve DV1 automatically and feeds back to decompression recuperation valve SC1 valve spring chamber, compare with commutation series flow control valve DV1 inlet pressure and to carry out preposition decompression compensation, remain commutation series flow control valve DV1 inlet and A (B) mouthful of constant pressure difference, SC1 forms the series flow control valve group with the decompression recuperation valve, load pressure PL the second tunnel leads to logical valve SV4, the interior steel ball of promotion logical valve SV4 valve is cut out and the series flow control valve DV2 load pressure that commutates detects a mouthful path, the PL propagation of pressure is to automatic transfer valve PS spring chamber, PS closes with automatic transfer valve, cut off pump 1 discharge capacity and flow to pump 2, stop and pump 2 discharge capacities interflow.

Load pressure PL Third Road leads to the interior steel ball of logical valve SV1 promotion logical valve SV1 valve and closes to logical valve SV2 passage, PL pressure is through the spring chamber of LS circuit transmission to diverter valve PC1, and the diverter valve PC1 the other end is the delivery pressure signal that pump 1 is introduced, carry out pressure compensation, keeping pump 1 delivery pressure and load pressure PL is constant pressure difference, be that the pump delivery pressure is all the time than the high constant pressure difference of load pressure, the unnecessary discharge capacity of pump is diverted to this valve oil return inlet T from diverter valve PC1, Here it is so-called load-sensitive information circuits, the flow process of load pressure in (LS loop).

Import fluid control pressure PX signal as independent to the hydraulic control instruction inlet opening Y5 that pays volume commutation series flow control valve DV3, commutation series flow control valve DV3 opens circulation area, export corresponding flow from interface A3, load pressure one tunnel during work of its pair volume is transmitted pressure-compensated valve SC3, another road is closed logical valve SV2 one end by the LS loop and is led to commutation series flow control valve DV2, close logical valve SV1 one end and lead to commutation series flow control valve DV1, close logical valve SV3 one end and lead to commutation series flow control valve DV4, through these logical valves SV2, SV1, after SV3 valve logic is arranged, the volume load pressure be will pay and diverter valve PC2 spring chamber and PC1 spring chamber will be passed to, the load pressure of paying volume can not be passed to automatic transfer valve PS spring chamber, at this moment automatic transfer valve PS opens automatically, the discharge capacity of pump 1 is collaborated through the discharge capacity of automatic transfer valve PS and one-way valve S and pump P2, the a part of discharge capacity in back, double pump interflow flows out from interface A3 in proportion according to the open area of commutation series flow control valve DV3, use for paying volume mechanism, and unnecessary discharge capacity branches to the T mouth from diverter valve PC1 and PC2.

When handling simultaneously with a pair volume as need are flexible; only need to get final product to the fluid control pressure instruction that hydraulic control instructs inlet opening Y1 and Y5 (or Y2 and Y6) to import simultaneously separately; commutation series flow control valve DV1 and DV3 all open simultaneously; can export required separately flow simultaneously for interface A3 (or B3) mouthful of interface A1 (or B1) mouth of commutation series flow control valve DV1 and commutation series flow control valve DV3; if it is lower to pay the load pressure of volume; stopped by steel ball in the logical valve SV1 valve; at this moment pump 1 and pump 2 are added the level pressure difference output that diverter valve PC1 and PC2 spring separately set with flexible load pressure respectively; to commutation series flow control valve DV1 and DV3 fuel feeding; flow out the flow that fluid control pressure instruction is separately set from interface A1 (or B1) and A3 (or B3); the unnecessary discharge capacity of two pumps is from diverter valve PC1 and PC2 branch to oil return inlet T separately; if flexible load pressure is lower than the load pressure of paying volume; and pump all adds level pressure difference output discharge capacity separately to pay the volume load pressure; at this moment; the commutation series flow control valve DV1 preposition reduction valve SC1 compensation of reducing pressure automatically in the extending means; be that preposition reduction valve SC1 valve turns down automatically; make inlet and the interface A (or B mouth) of commutation series flow control valve DV1 keep level pressure poor, the original proportional control characteristic of setting of series flow control valve DV1 valve of guaranteeing to commutate is stepless proportionality velocity modulation characteristic.

All above-mentioned manoeuvring performances all rely on the load-sensitive of this valve to finish, and the action that is complementary of each element is transmitted, compared, duplicates, orders to load pressure in the LS loop.

The hydraulic control master control valve of existing traditional type has outside hydraulic control instruction among Figure 12, but belong to direction switching valve, can't realize proportionality velocity modulation, the flow of exporting from interface A, B is subjected to the very big influence of load variations, handles work when can not carry out moving more than two and two.

Second embodiment: the responsive double pump confluent type of the on-load multi-channel proportional control valve of stick control instruction

As shown in Figure 2.Its implementation process: with first embodiment relatively, just instruct the input mode difference, the former is the fluid control pressure instruction, the latter be the stick control angular dimension as the input instruction, hydraulic principle is basic identical.

Fig. 3 expresses this valve internal load sensitive information loop with skeleton diagram and thick line, dotted line, the pressure fuel pump information circuits, and the loop and instruction output of oil pump output discharge capacity is the sketch of management networking mutually, so that understand the hydraulic principle of this valve picture group 1 and Fig. 2.

Fig. 4 is that on-load responsive type proportional multi-path valve general assembly drawing is handled in first embodiment's hydraulic control;

Fig. 5 is second embodiment's manual control on-load responsive type proportional multi-path valve general assembly drawing; They by pump 1 inlet connection, flexible, luffing connection, middle transition connection, main, pay the volume connection, the oil return connection is superimposed, with three M16 high strength long bolts pump 1 inlet is joined, flexible luffing connection is connected middle transition connection left side, will lead, pay volume connection and oil return connection with three M16 high strength long bolts and spring washer equally and be connected middle transition and join the right side.The available 4 M12 screw of whole valve group are at the other base of truck crane operator cabin.

Though two kinds of maneuverability patterns are different, but their installation dimension is identical, pump 1 inlet connection, middle transition connection, oil return join the two structure, inner body is identical, the two flexible luffing connection, and the valve body of main pair of volume connection is also identical with inner most of part, as long as change commutation series flow control valve DV spool, spring and spring housing get final product, and can reach the mutual versatility of 70% above part, help factory and produce in batches and derivation assembling mutually.

Consider the convenience that externally connected pipe is connected with this valve from the layout of external tapping, with pump P1 interface, pump P2 interface, oil return inlet T, extending means interface A1, B1, jib lubbing mechanism interface A2, B2, pair volume the interface A3 of mechanism, B3, the interface A4 of master file mechanism, B4, all parallel making progress, do not collide when spacing of these mouthfuls and screw thread specification guarantee to install the external tapping fittings body, make spanner that rotating leeway be arranged.Logical valve SV1~SV4 valve is all with being threaded into the formula structure, diverter valve PC1, PC1 and decompression recuperation valve SC1~SC4 all have and externally regulate the setting pressure of spring separately, safety valve R1 and R2, secondary relief valve PR1~PR6 also can externally regulate its cracking pressure, be contained in the attenuator on the middle transition connection, also can change internal ramp easily under the situation of not disintegrating, all these structure arrangements all make things convenient for the user to maintain.

Fig. 6 is master, pair volume multi pack figure of this valve group of second embodiment (manual control mode), and structure and Fig. 4 flexible, the luffing connection are basic identical.This connection is divided into upper, middle and lower-ranking, and secondary relief valve is installed on the upper strata, and commutation series flow control valve DV is installed in the middle level, claims selector valve again, and lower floor is for installing decompression recuperation valve SC valve.Its runner is arranged, be the input cavity of pump P2 below, middle ingress interface P ' chamber for commutation series flow control valve DV, and the top is A and B chamber, these two mouthfuls are connected with external pipeline with actuator.Secondary relief valve is installed in A, the outside, B chamber, and two sides in A, B chamber are T chamber (being oil back chamber).By spring housing 1, screw, packing ring 2,3, spring 4, sleeve 5, spring seat 6, commutation series flow control valve DV spool 7, valve body 13, decompression recuperation valve SC valve core 14, spring 15, spring seat 16, adjusting screw 18 compositions such as grade, 3 ∮ 17 join the superimposed screw that is connected with other.

Commutation series flow control valve DV spool is in the neutral position under spring 4 effects, path between down interface P ' and interface A, interface P ' and the interface B, decompression recuperation valve SC spool is in the rightmost side under spring 5 effects, guarantee to form path between pump 2 interface P2 and the interface P ', adjusting screw 18 adjustable interface P ' are to interface A chamber, and interface P ' is poor to the level pressure in interface B chamber.When need during to interface B output certain flow, stir certain distance left with the Joystick series flow control valve DV spool 7 that will commutate, intermediary interface P ' chamber and interface B chamber are linked up, and form certain circulation area (hydraulic control mode, promptly to the certain external control pressure instruction of spring chamber Y mouth input), at this moment pump 2 interface P2 chamber discharge capacity parts are imported actuator through throttling groove (variable circulation area) through decompression recuperation valve SC spool and orifice ring shape passage again to interface P ' chamber to interface B chamber, make actuator's motion, and oil return to interface A chamber through left end oil return inlet T chamber oil sump tank, stirring angle (the series flow control valve DV valve position that promptly commutates is moved, and just interface P ' is to the circulation area of interface B) from interface B output flow and Joystick is directly proportional.The load pressure that interface B forms detects mouth through radially loading to right-hand member with axial small channel of commutation series flow control valve DV spool right-hand member, lead to the LS loop and the logical valve of this valve group with the valve body annular groove, be delivered to diverter valve PC1 at last and the PC2 spring chamber carries out pressure compensation, make pump 1 and pump 2 with this load pressure add diverter valve PC1 and PC2 separately the pressure of the level pressure difference set of spring export the P2 chamber of this connection to, unnecessary discharge capacity branches to oil return idol T from diverter valve PC1 and PC2, the instruction of input (is the Joystick angle, or fluid control pressure) big more, big more from interface B output flow, and the shunt volume of pump is more little, and remaining pump delivery is interface B (or A) output flow and shunt volume sum.When the Joystick angle is zero, (or fluid control pressure is less than 0.6MPa) commutation series flow control valve DV spool is returned to meta under self spring action, down interface P ' is to the path of B (or P ' is to A), interface A, B do not have flow output, and whole discharge capacities of pump from diverter valve PC1 and PC2 valve with the low pressure bypass to the oil return inlet T oil sump tank.

The spring chamber of decompression recuperation valve SC spool is introduced interface A, the B load pressure, and the oil pump delivery pressure of radially with axial small channel introducing pump P2 chamber of right-hand member in the middle of decompression recuperation valve SC spool, decompression recuperation valve SC spool is in maximum open degree when individual operation, and when handling other commutation series flow control valves DV valve simultaneously, and when the load pressure of this connection is lower than the load pressure of other same behaviour's connection, this valve decompression recuperation valve SC valve pump P2 guides in the chamber decompression recuperation valve SC spool right-hand member pressure into and forms thrust left and greater than the thrust to the right (adding spring force) of left end spring chamber decompression recuperation valve SC spool is moved to the left, turn down the opening degree in pump P2 chamber to P ' chamber, form flow resistance, and decompression makes interface P ' chamber and B chamber still keep original level pressure poor, Here it is the compensation principle that reduces pressure.So just realized and two actuators to have handled work simultaneously, can keep original proportionality velocity modulation characteristic again.

When need during to interface A output flow, stirring Joystick moves right commutation series flow control valve DV spool to get final product, at this moment, commutation series flow control valve DV spool is closed the right-hand member load pressure and is detected mouth, detect mouth and open the left end load pressure, the load pressure in interface A chamber is communicated with the LS loop, and its load-sensitive and pressure compensation are same as described above, omit narration.

Shown in Figure 7 is the spool function of luffing selector valve of the present invention, when handling arm, cut off interface P ' fuel feeding and give interface B (being interface P ' sealing), the spool function of luffing selector valve of the present invention is different from the function of traditional approach, and it cuts the flute profile formula and in the arm position function that falls is And traditional function is And the deadweight of arm rest frame, interface A, B two chambeies have the loop of one's own, the unnecessary oil that oil cylinder rodless cavity B discharges flows out from oil return inlet T, the safety that reaches from motion tracking luffing moment variations and coordinate mutually, the arm movement speed freely falls, promptly increase gradually with luffing moment, the arm angular velocity that freely falls reduces automatically gradually, and traditional luffing spool function and interface B are when installing common equilibrium valve and using, along with luffing moment increases, the arm angular velocity that falls also increases, and easily causes the unsafe factor of stall, this on-load pressure overcompensation load control valve also needs from German import because there is not ready-made product.

Another characteristics of commutation series flow control valve DV2 spool of the present invention are that Fig. 7 A-A analyses and observe the shaped design with the timing throttle mouth shown in the partial enlarged drawing, be the circulation area FX of variable interface P ' to A (or B), flexible and the jib lubbing mechanism commutation series flow control valve DV spool of single oil pump feed is 4, and the master of double pump interflow fuel feeding, to pay a volume mechanism commutation series flow control valve DV spool be 8, every the trench cross section angle is 90 °, be 35 ° 24 ' tilt, four groove maximum flow areas are 1cm 2, 8 groove maximum flow areas are 2.0cm 2When commutate series flow control valve DV valve interface P ' and A (or B) setting level pressure difference are 1.0Mpa, the former is exportable rated flow 160L/min, the exportable rated flow 320L/min of the latter needs to change the groove angle number of degrees and quantity gets final product for different user, can make 60 ° into as angle, it is uniform that quantity can be processed into symmetries such as 2,3,5,6,8, can derive from tens of kinds of specified output flows like this, factory prepares according to customer requirements, and is very convenient.Another characteristic of this groove shape is that the circulation area variation helps dead slow speed and control at a slow speed (being the output of micrometeor and small flow), and the low speed control of large-scale to lifting by crane, expensive, frangible, military-civil goods and equipment is very favourable.

Fig. 8 is the erection drawing of single double pump automatic transfer valve PS and pump 2 outlet diverter valve PC2, this figure is also referred to as middle transition connection cut-away section, the layout of this connection, end face is installed attenuator 19, pump 2 outlet safety valve R2 20, logical valve SV2 and SV4 21, the top left end is installed diverter valve PC2 24, automatic transfer valve PS is installed in the bottom, and the bottom, left side has pump 1 by-pass port L, and the many fine rule small channels among the figure are partial L S loop.Automatic transfer valve PS spool 25 right-hand members are installed the Regulation spring 22 of setting the level pressure difference, available adjustment screw 23 is regulated, automatic transfer valve PS center spool has radial and axial small channel the delivery pressure of pump 1 is introduced automatic transfer valve PS spool left end chamber, and automatic transfer valve PS spool right-hand member spring chamber is introduced the load pressure of the flexible or luffing of selecting through logical valve SV4 valve.(by the LS loop) (consulting Fig. 1).

When flexible or jib lubbing mechanism commutation series flow control valve DV1 valve or the work of DV2 valve, its load pressure is selected to transmit by LS loop and logical valve SV4 and is entered automatic transfer valve PS spring chamber, add spring thrust, automatic transfer valve PS spool is moved to the left, down interface P1 leads in the chamber to the runner of one-way valve S, the discharge capacity that stops pump 1 is to pump 2 interflow, though (pressure of pump 1 passes through the middle small flow channels of automatic transfer valve PS spool to automatic transfer valve PS left end, but formation thrust to the right is less than the thrust of the former left, so automatic transfer valve PS spool is moved to the left) and pump 1 fuel feeding only offers commutation series flow control valve DV1 or DV2 uses, when commutating series flow control valve DV1 valve (DV2 valve) and DV3 valve (DV4 valve) when handling work simultaneously, also keep single oil pump feed.

When commutate series flow control valve DV1 valve and DV2 valve are not worked, work and handle commutation series flow control valve DV3 valve (or DV4 valve), the load pressure of paying volume and master file is stopped that by small ball in logical valve SV2 and the SV1 valve (consulting Fig. 1) can not be delivered to automatic transfer valve PS spool right-hand member spring chamber in the LS loop, pump 1 pressure of automatic transfer valve PS spool left end introducing at this moment overcomes the right-hand member spring force easily, automatic transfer valve PS spool is moved right, open interface P1 chamber to the passage that flows to one-way valve S, the discharge capacity of pump 1 goes downstream and use for commutation series flow control valve DV3 and DV4 at pump 2 interflow (consulting Fig. 1).The principle of Here it is double pump automatic merging.

The working principle of diverter valve PC2 is identical with Fig. 9 pump 1 outlet diverter valve PC1 working principle among the figure, will be in description.

Fig. 9 is the layout of pump 1 outlet diverter valve PC1 in pump 1 inlet connection, the upper-end surface is pump 1 inlet opening, bottom P1 mouth leads to other connection (to flexible luffing connection, the middle transition connection) upper right quarter is installed the main relief valve R1 26 of pump 1 outlet, diverter valve PC1 spool 27 is installed at the middle part, spool right-hand member mounting spring 28 available adjustment screws 29 are regulated, there are ∮ 3 apertures 30 to communicate in the spring chamber with the LS loop, have in the middle of the diverter valve PC1 spool ∮ 3 radially with axial small channel, pump 1 pressure is introduced the left end of diverter valve PC1 spool, T is an oil back chamber, and the pressure tap of M10 * 1 is set.

Diverter valve PC1 valve (PC2 valve) mainly contains two functions, the one, set up the required pressure of load, the 2nd, (i.e. control and each interface A of change, B output flow) discharge capacity that pump is unnecessary is diverted to the T chamber in speed regulation process, the action of diverter valve PC1 must be by the load pressure from the LS loop, spring 28 setting power, pump discharge pressure and damping plug 31 internal damping holes coordinate to finish mutually.

When commutation series flow control valve DV1 and the work of DV2 valve, command signal is sent in promptly manual or hydraulic control, commutation series flow control valve DV spool is moved, when opening interface P ' and flowing to A (B) circulation area FX, pump 1 discharge capacity is by interface P1 chamber, flow to decompression recuperation valve SC1 and SC2 when the series flow control valve DV ingress interface P ' that commutates leads to interface A or B, promote load (oil cylinder) motion, its load pressure LS loop and logical valve SV1 select to enter diverter valve PC1 spool right-hand member spring chamber, add that spring force is moved to the left diverter valve PC1 spool, be tending towards down interface P1 chamber and oil return inlet T chamber passage, the pressure of pump 1 output is that load pressure adds the level pressure difference sum that upper spring 28 is set, if handle commutation series flow control valve DV valve is maximum unlatching the (FX is for maximum), then pump 1 whole discharge capacities are used for commutation series flow control valve DV from the output of interface P1 chamber, interface A (B) rear pump 1 delivery, outer load obtains top speed, and when needing deceleration control, handle commutation series flow control valve DV, reduce in the FX process, commutation series flow control valve DV valve inlet P ' can improve to A (B) mouthful of flow velocity, the moment increase of commutation series flow control valve DV inlet P ' pressure, it is pump 1 delivery pressure moment increase, at this moment, the pressure that the moment in interface P1 chamber improves passes through diverter valve PC1 valve core inside small channel to the left end chamber, diverter valve PC1 spool left end thrust to the right adds upper spring 28 power greater than the right-hand member load pressure, diverter valve PC1 spool is moved right, open interface P1 chamber to oil return inlet T chamber runner, pump 1 unnecessary discharge capacity is diverted to the T chamber.How much being inversely proportional to commutation series flow control valve DV circulation FX automatically of shunt volume, as shunt too much, then the P1 cavity pressure can reduce moment, diverter valve PC1 spool is moved to the left automatically, turn down the actual internal area of the passage in interface P1 chamber and oil return inlet T chamber, reduce shunt volume, the dynamically quick all the time move left and right of diverter valve PC1 spool, reach and obtain constantly flat permanently between the shunt volume of output flow and diverter valve PC1 valve of interface A, B control, guarantee the output flow that the required manipulation of interface A, B is controlled.Its damping size of damping plug of installing on the damping plug that diverter valve PC1 spool left end is installed and the right-hand member spring chamber ∮ 3 aperture LS loops is different, and purpose is the stability of regulating diverter valve PC spool dynamic action.

Figure 10 is the cut-away view that logical valve (SV valve) claims fusiformis valve, logical valve again, be provided with four logical valves of SV1~SV4 in the LS information on load loop altogether, logical valve SV1 is installed in flexible luffing connection side, logical valve SV3 is installed in the master, pays volume connection side, and logical valve SV2, SV4 are installed in middle transition connection end face (consulting Fig. 3 Fig. 4), logical valve SV1 selects the higher person in self-commutation series flow control valve DV1 and the two pressure of SV2 automatically, the higher person in series flow control valve DV1 and the two pressure of DV2 and logical valve SV4 selects to commutate automatically, (consulting Fig. 1 and Fig. 2).Logical valve SV1~SV4 internal structure is identical.

As shown in figure 10, by being threaded into formula valve body 8, parts such as steel ball 9, small valve core 10 assemble, with spanner rotary valve 8, whole valve screw-in is respectively joined side of valve body and end face, three apertures of a, b, c that make among the figure to be annotated communicate with the LS loop of this valve group, and (consulting Fig. 1 and Fig. 2) series flow control valve DV1~DV4 load pressure that will commutate detects mouthful eight load pressure information of feedback output and transmits, relatively.Through mutually logic arrangement, select wherein the maximum load propagation of pressure to carry out the pressure compensation of pump delivery pressure to diverter valve PC1 and PC2 valve spring chamber.The higher person is delivered to automatic transfer valve PS valve and carries out the automatic switchover of single double pump discharge capacity in commutation series flow control valve DV1 and the two load pressure of DV2, and the load pressure that commutation series flow control valve DV1~DV4 detects separately is directly delivered to the recuperation valve SC1~SC4 spring chamber that reduces pressure separately and carries out separately preposition decompression compensation, and its flow chart can be consulted Fig. 3.

The principle that logical valve SV selects automatically: two load pressures are introduced in two end a of valve and b hole respectively as shown in figure 10, and middle c hole is a delivery outlet, and the middle shaft orientation flowing channel of valve is equipped with steel ball 9.When the load pressure in left end b hole is higher than the load pressure in right-hand member a hole, steel ball is pushed to the passage in sealing a hole, the right side to c hole, the load pressure in b hole is selected to be exported from the c hole, otherwise, when the load pressure in a hole is higher than the load pressure in b hole, then steel ball is pushed the passage in sealing b hole, the left side to c hole to, a hole load pressure is selected to be exported from the c hole, so be called selector valve, and steel ball 9 is made the motion of shuttle on the similar weaving machine of left and right sides to-and-fro motion in valve body, so claim the fusiformis valve again, the principle of its logical relation is that two bursts of load pressures are compared, select high person's output, so claim logical valve again.

The design of this logical valve SV is considered when break down in the LS loop, this valve can be screwed out easily and carry out fault judgement, checking that whether steel ball 9 sealings are malfunctioning, or be stuck, check whether seal failure of each O-ring seals (sequence number 11,12,32), check that steel ball 9 is extruded valve body etc.Figure 11 is the signal of partial L S return passage.

Characteristics of the present invention be stretch, luffing, pay volume, master file mechanism can both realize ratio stepless speed regulation, is not subjected to outer load Impact; Can choose above-mentioned four big executing agencies wantonly and carry out handling simultaneously more than two and two, not being subjected to mutually, load differs it Impact, and keep handling simultaneously to stepless proportionality velocity modulation separately; The luffing reversing valve core adopts new function, also can join standard Function commonly used still keeps single Dual-pump flow-converging automatic switchover function simultaneously.

Claims (10)

1. the responsive double pump confluent type of on-load multi-channel proportional control valve comprises it is characterized in that input interface P1, P2, tank drainback interface T and the hydraulic system of pump 1 and pump 2:
Hydraulic system is provided with extending means proportional control valve (10 '), jib lubbing mechanism proportional control valve (20 '), pays volume mechanism's proportional control valve (30 '), master file mechanism proportional control valve (40 ');
The inlet opening of commutation series flow control valve DV1 in the extending means proportional control valve (10 '), commutation series flow control valve DV2, diverter valve PC1 in the jib lubbing mechanism proportional control valve (20 '), safety valve R1 is connected in parallel on the P1 interface of pump 1; Commutation series flow control valve DV1 in the extending means proportional control valve (10 '), the delivery outlet of the commutation series flow control valve DV2 in the jib lubbing mechanism proportional control valve (20 ') are connected respectively on extending means and the jib lubbing mechanism; The delivery outlet of diverter valve PC1, safety valve R1 is connected on the tank drainback interface T;
The inlet opening of paying commutation series flow control valve DV3 in volume mechanism's proportional control valve (30 '), commutation series flow control valve DV4, diverter valve PC2 in the master file mechanism proportional control valve (40 '), safety valve R2 is connected in parallel on the P2 interface of pump 2; The delivery outlet of paying commutation series flow control valve DV3, the commutation series flow control valve DV4 in the master file mechanism proportional control valve (40 ') in volume mechanism's proportional control valve (30 ') is connected respectively to be paid in volume mechanism and the master file mechanism; The delivery outlet of diverter valve PC2, safety valve R2 is connected on the tank drainback interface T;
Be provided with single double pump automatic transfer valve PS and one-way valve S between pump 1 and pump 2 series loops;
Extending means proportional control valve (10 '), jib lubbing mechanism proportional control valve (20 '), commutation series flow control valve DV1~4 one ends of paying in volume mechanism's proportional control valve (30 '), the master file mechanism proportional control valve (40 ') are connected with hydraulic control instruction inlet opening Y1, Y3, Y5, Y7, and the other end is connected with hydraulic control instruction inlet opening Y2, Y4, Y6, Y8;
Be provided with load-sensitive information circuits LS between commutation series flow control valve DV1~4, load-sensitive information circuits LS has selected three logical valve SV1~3 combined, select the maximum load pressure of commutation series flow control valve DV1~4 feedbacks, be passed to that diverter valve PC1 and diverter valve PC2 carry out pressure and flow compensates automatically; Load-sensitive information circuits LS has also adopted logical valve SV4, only select the maximum load pressure of commutation series flow control valve DV1~2 feedbacks, be passed to single double pump automatic transfer valve PS, single double pump automatic transfer valve PS is switched to single pump input interface P1 fuel feeding to DV1 commutation series flow control valve and the work of DV2 commutation series flow control valve.
2. the responsive double pump confluent type of on-load according to claim 1 multi-channel proportional control valve, it is characterized in that: extending means proportional control valve (10 ') comprises the extending means commutation series flow control valve DV1 that is connected in parallel with described diverter valve PC1, the commutation series flow control valve DV1 decompression recuperation valve SC1 that is connected in series; Commutation series flow control valve DV1 is provided with the A1 and the B1 of two interfaces of extending means, is connected level relief valve PR1 one time between commutation series flow control valve DV1 and the interface A1, is connected level relief valve PR2 one time between commutate series flow control valve DV1 and the interface B1.
3. the responsive double pump confluent type of on-load according to claim 1 multi-channel proportional control valve, it is characterized in that: jib lubbing mechanism proportional control valve (20 ') comprises the jib lubbing mechanism commutation series flow control valve DV2 that is connected in parallel with described diverter valve PC1, the commutation series flow control valve DV2 decompression recuperation valve SC2 that is connected in series, the commutation series flow control valve is provided with the A2 and the B2 of two interfaces of jib lubbing mechanism, be connected level relief valve PR3 one time between the A2 of commutation series flow control valve DV2 and interface, be connected level relief valve PR4 one time between the B2 of commutate series flow control valve DV2 and interface.
4. the responsive double pump confluent type of on-load according to claim 1 multi-channel proportional control valve, it is characterized in that: pay volume mechanism's proportional control valve (30 ') and comprise with described diverter valve PC2 is connected in parallel and pay the commutation series flow control valve DV3 of a volume mechanism, the commutation series flow control valve DV3 decompression recuperation valve SC3 that is connected in series; Commutation series flow control valve DV3 is provided with the A3 and the B3 of two interfaces paying volume mechanism, is connected level relief valve PR5 one time between the A3 of commutation series flow control valve DV3 and interface.
5. the responsive double pump confluent type of on-load according to claim 1 multi-channel proportional control valve, it is characterized in that: master file mechanism proportional control valve (40 ') comprises the commutation series flow control valve DV4 of master file mechanism that is connected in parallel with described diverter valve PC2, the commutation series flow control valve DV4 decompression recuperation valve SC4 that is connected in series, commutation series flow control valve DV4 is provided with the A4 and the B4 of two interfaces of jib lubbing mechanism, is connected level relief valve PR6 one time between the A4 of commutation series flow control valve DV4 and interface.
6. the responsive double pump confluent type of on-load according to claim 1 multi-channel proportional control valve is characterized in that: the pressure information inlet opening of all elements that network mutually among the load-sensitive information circuits LS is provided with to reaching all elements actions damping measure perfect cooperation, that improve dynamic performance.
7. the responsive double pump confluent type of on-load according to claim 1 multi-channel proportional control valve, it is characterized in that: be provided with four logical valve SV1~SV4 among the load-sensitive information circuits LS altogether, first to the 3rd logical valve connected mutually, therefrom select the highest load pressure of four commutation series flow control valve DV1~DV4 feedback, and pass to two diverter valve PC1~PC2, the 4th logical valve SV4 selects highest load pressure flexible and luffing commutation series flow control valve feedback, passes to single double pump automatic transfer valve PS.
8. according to claim 2 or the responsive double pump confluent type of 3 or 4 or 5 described on-loads multi-channel proportional control valve, it is characterized in that: extending means proportional control valve (10 '), jib lubbing mechanism proportional control valve (20 '), pair volume mechanism's proportional control valve (30 ') and master file mechanism proportional control valve (40 ') all are provided with the hydraulic jack that manual control handle or hydraulic control are handled separately.
9. the responsive double pump confluent type of on-load according to claim 1 multi-channel proportional control valve, it is characterized in that: pump 1 and pump 2 outlet main relief valve R1, R2 separately are provided with the off-load mouth, and master file provides the pressure source that declutches interface with secondary volume oil motor break.
10. the responsive double pump confluent type of on-load according to claim 8 multi-channel proportional control valve is characterized in that: the extending means proportional control valve (10 '), jib lubbing mechanism proportional control valve (20 '), pair volume mechanism's proportional control valve (30 ') and master file mechanism proportional control valve (40 ') the two end hydraulic jacks that adopt hydraulic control to handle are provided with air vent W1~W8.
CNB2004100932229A 2004-12-17 2004-12-17 Double pump confluence type multi-way ratio control valve with load sensitivity information circuit CN100362247C (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CNB2004100932229A CN100362247C (en) 2004-12-17 2004-12-17 Double pump confluence type multi-way ratio control valve with load sensitivity information circuit

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CNB2004100932229A CN100362247C (en) 2004-12-17 2004-12-17 Double pump confluence type multi-way ratio control valve with load sensitivity information circuit

Publications (2)

Publication Number Publication Date
CN1789733A CN1789733A (en) 2006-06-21
CN100362247C true CN100362247C (en) 2008-01-16

Family

ID=36787798

Family Applications (1)

Application Number Title Priority Date Filing Date
CNB2004100932229A CN100362247C (en) 2004-12-17 2004-12-17 Double pump confluence type multi-way ratio control valve with load sensitivity information circuit

Country Status (1)

Country Link
CN (1) CN100362247C (en)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102312873A (en) * 2011-08-19 2012-01-11 长沙中联重工科技发展股份有限公司 Concrete pump truck and hydraulic control system thereof
CN103267147A (en) * 2013-05-28 2013-08-28 卢宇 Small-flow high-pressure load sensitive proportional multi-way valve

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101603551B (en) * 2009-06-25 2012-08-08 卢宇 Multi-channel proportional flow distribution valve bank applicable to various variable pump systems
CN102358571B (en) * 2011-10-19 2013-07-31 四川长江液压件有限责任公司 Double-pump load hydraulic sensing system
CN102588373B (en) * 2012-03-08 2015-02-18 长沙中联消防机械有限公司 Engineering machinery and leg hydraulic control device thereof
CN103058071B (en) * 2012-12-27 2015-07-22 徐州重型机械有限公司 Crane, and hydraulic system, control system, and speed control method for superlift rope collection
CN105201933B (en) * 2015-01-15 2017-09-19 徐州重型机械有限公司 A kind of proportionality velocity modulation hydraulic system based on speed feedback
CN104863914B (en) * 2015-04-13 2017-09-26 徐州徐工液压件有限公司 A kind of electro-hydraulic joint control converging valve
CN104879336B (en) * 2015-04-14 2017-01-25 徐州徐工液压件有限公司 Valve back compensation type load-sensitive multitandem valve with bidirectional confluence function
CN107269609B (en) * 2017-07-26 2018-10-26 无锡市钻通工程机械有限公司 Combining hydraulic system in load-sensitive valve
CN108050118A (en) * 2017-12-06 2018-05-18 徐州重型机械有限公司 A kind of main valve and its hydraulic control system

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4617854A (en) * 1983-06-14 1986-10-21 Linde Aktiengesellschaft Multiple consumer hydraulic mechanisms
US5319933A (en) * 1992-02-14 1994-06-14 Applied Power Inc. Proportional speed control of fluid power devices
JPH0932042A (en) * 1995-07-19 1997-02-04 Shin Caterpillar Mitsubishi Ltd Oil pressure control method and its circuit
JP3003958B2 (en) * 1991-03-15 2000-01-31 株式会社小松製作所 Load sensing hydraulic circuit
CN1333435A (en) * 2000-07-14 2002-01-30 株式会社小松制作所 Actuator controller fro hydraulic driving machinery
CN1157515C (en) * 2000-07-28 2004-07-14 株式会社小松制作所 Oil pressure type digging vehicle

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4617854A (en) * 1983-06-14 1986-10-21 Linde Aktiengesellschaft Multiple consumer hydraulic mechanisms
JP3003958B2 (en) * 1991-03-15 2000-01-31 株式会社小松製作所 Load sensing hydraulic circuit
US5319933A (en) * 1992-02-14 1994-06-14 Applied Power Inc. Proportional speed control of fluid power devices
JPH0932042A (en) * 1995-07-19 1997-02-04 Shin Caterpillar Mitsubishi Ltd Oil pressure control method and its circuit
CN1333435A (en) * 2000-07-14 2002-01-30 株式会社小松制作所 Actuator controller fro hydraulic driving machinery
CN1157515C (en) * 2000-07-28 2004-07-14 株式会社小松制作所 Oil pressure type digging vehicle

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102312873A (en) * 2011-08-19 2012-01-11 长沙中联重工科技发展股份有限公司 Concrete pump truck and hydraulic control system thereof
CN103267147A (en) * 2013-05-28 2013-08-28 卢宇 Small-flow high-pressure load sensitive proportional multi-way valve

Also Published As

Publication number Publication date
CN1789733A (en) 2006-06-21

Similar Documents

Publication Publication Date Title
US7594396B2 (en) Hydraulic controller for working machine
DE3817218C2 (en)
US9080310B2 (en) Closed-loop hydraulic system having regeneration configuration
US4779417A (en) Hydraulic pressure system
EP0331076B1 (en) Hydraulic circuit for cylinder
CN100359104C (en) Hydraulic driving system of construction machinery
KR0145143B1 (en) Hydraulic control valve apparatus and hydraulic drive system
CN100378342C (en) Hydraulic valve device and its assembling method
KR20100127750A (en) Hydraulic circuit for construction machine
US20120233996A1 (en) System for allocating fluid from multiple pumps to a plurality of hydraulic functions on a priority basis
US5211014A (en) Hydraulic drive system
CN102913495B (en) Modularized combined electric-hydraulic multitandem valve system adopting compact type two way cartridge valve
CN101723274B (en) Main winch retracting and stretching control system of rotary drilling rig and rotary drilling rig
US8863509B2 (en) Meterless hydraulic system having load-holding bypass
CN102296665B (en) Excavator hydraulic system carrying load sensing main valve and positive flow pump
CN103470565B (en) The rotary system of rotary buffering valve and hoist
CN102758813A (en) Energy-recovery hydraulic system and engineering machinery
US7614225B2 (en) Straight traveling hydraulic circuit
CN103016438B (en) A kind of electrohydraulic proportional control valve group
US9528531B2 (en) Hydraulic drive apparatus for work machine
CN104870831B (en) Hydraulic control device and construction machine with same
JP2012523531A (en) Hydraulic circuit with multiple pumps
CN101723271B (en) Hydraulic control system for crane hoisting
CN102518170A (en) Hydraulic system of loading machine working device
CN105008626A (en) Merging circuit of hydraulic apparatus

Legal Events

Date Code Title Description
PB01 Publication
C06 Publication
SE01 Entry into force of request for substantive examination
C10 Entry into substantive examination
GR01 Patent grant
C14 Grant of patent or utility model
EE01 Entry into force of recordation of patent licensing contract

Assignee: Ningbo Jiangbei Yuzhou Hydraulic Equipment Factory

Assignor: Lu Yongsong

Contract record no.: 2011330000592

Denomination of invention: Double pump confluence type multi-way ratio control valve with load sensitivity information circuit

Granted publication date: 20080116

License type: Exclusive License

Open date: 20060621

Record date: 20110525

Assignee: Ningbo Jiangbei Yuzhou Hydraulic Equipment Factory

Assignor: Lu Yongsong

Contract record no.: 2011330000592

Denomination of invention: Double pump confluence type multi-way ratio control valve with load sensitivity information circuit

Granted publication date: 20080116

License type: Exclusive License

Open date: 20060621

Record date: 20110525

ASS Succession or assignment of patent right

Owner name: NINGBO JIANGBEI YUZHOU HYDRAULIC EQUIPMENT FACTORY

Free format text: FORMER OWNER: LU YONGSONG

Effective date: 20110708

TR01 Transfer of patent right

Effective date of registration: 20110708

Address after: Jiangbei District in Zhejiang province 315021 Hing Ningbo Yonglu No. 98

Patentee after: Ningbo Jiangbei Yuzhou Hydraulic Equipment Factory

Address before: 315211 Ningbo Jiangbei Zhejiang Kongura Rika Ningbo Jiangbei hydraulic equipment factory

Patentee before: Lu Yongsong

Effective date of registration: 20110708

Address after: Jiangbei District in Zhejiang province 315021 Hing Ningbo Yonglu No. 98

Patentee after: Ningbo Jiangbei Yuzhou Hydraulic Equipment Factory

Address before: 315211 Ningbo Jiangbei Zhejiang Kongura Rika Ningbo Jiangbei hydraulic equipment factory

Patentee before: Lu Yongsong

C41 Transfer of patent application or patent right or utility model
COR Change of bibliographic data

Free format text: CORRECT: ADDRESS; FROM: 315211 NINGBO YUZHOU HYDRAULIC EQUIPMENT FACTORY, KONGPULI, JIANGBEI, NINGBO CITY, ZHEJIANG PROVINCE TO: 315021 NO. 98, XINGYONG ROAD, JIANGBEI DISTRICT, NINGBO CITY, ZHEJIANG PROVINCE

CP01 Change in the name or title of a patent holder

Address after: Jiangbei District in Zhejiang province 315021 Hing Ningbo Yonglu No. 98

Patentee after: Ningbo Yuzhou Hydraulic Equipment Co.,Ltd.

Address before: Jiangbei District in Zhejiang province 315021 Hing Ningbo Yonglu No. 98

Patentee before: NINGBO JIANGBEI YUZHOU HYDRAULIC EQUIPMENT FACTORY