CN212744559U - Crane extension valve group and hydraulic system - Google Patents

Crane extension valve group and hydraulic system Download PDF

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Publication number
CN212744559U
CN212744559U CN202022084442.2U CN202022084442U CN212744559U CN 212744559 U CN212744559 U CN 212744559U CN 202022084442 U CN202022084442 U CN 202022084442U CN 212744559 U CN212744559 U CN 212744559U
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valve
oil
port
normally closed
pressure
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陈海军
丁方园
王惠
何月华
蒋记
刘林楠
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Construction Machinery Branch of XCMG
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Construction Machinery Branch of XCMG
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Abstract

The utility model discloses a crane expansion valve group and a hydraulic system, which comprises a two-position two-way normally closed solenoid valve, an adjustable throttle valve, a pressure compensator, an overflow valve, a damper and a valve block; the oil inlet of two lead to normally closed solenoid valve communicates with each other with the pressure hydraulic fluid port of valve block, the oil-out of two lead to normally closed solenoid valve is linked together with the oil inlet of adjustable choke valve, the oil-out of adjustable choke valve is linked together with the oil inlet of pressure compensator, the first mouth of damped of overflow valve and the work hydraulic fluid port of valve block communicate with each other, the oil-out of overflow valve communicates with each other with the oil return opening of valve block, the second mouth of pressure compensation valve, the load feedback hydraulic fluid port of damped second mouth and valve block communicate with each other. The beneficial effects of the utility model are that utilize the utility model discloses an extension valves can realize auxiliary system and the parallelly connected return circuit structure of main pump system, reduces an auxiliary pump, optimizes auxiliary system, solves the short condition in space office.

Description

Crane extension valve group and hydraulic system
Technical Field
The utility model relates to an engineering machine tool technical field specifically is a hoist extension valves and hydraulic system.
Background
In the field of mobile cranes, particularly crawler cranes, a main machine not only performs lifting, amplitude changing, walking, rotating and the like, but also performs auxiliary actions such as mast jacking, cab pitching, cab rotating, counterweight lifting, auxiliary self-assembly and disassembly, get-off supporting legs, crawler beam stretching, various pin shaft oil cylinders stretching and the like, generally adopts the oil cylinder as an execution element for the auxiliary actions, and the auxiliary actions tend to increase along with the increase of the tonnage of products. The main action and the auxiliary action of the crane can sometimes be combined, for example, the luffing winch and the mast jacking cylinder are often required to be combined, so that the auxiliary system and the main system are required to be independent from each other and not influenced by each other.
The main system usually adopts a load sensitive control system with a load sensitive main pump matched with a multi-way valve based on post-valve compensation, and flow distribution can be realized without being influenced by load. The schematic diagram of the load-sensitive pump is shown in fig. 1, with pump outlet pressure P and actuator load pressure PLSThe flow Q output by the main pump is led into an actuating element (a motor and an oil cylinder) through a main valve throttling opening. Differential pressure Δ P-P across a valve restrictionLS(ii) a P simultaneously acts on the left end of the valve core of the variable valve (LS valve),PLSwith a predetermined spring pressure PKThe (constant value) coacts at the right end of the spool. When the LS valve core is stressed in balance, PK=P-PLSThe main pump maintains a stable discharge capacity; if the opening of the throttle opening is changed, the dynamic delta P is larger or smaller than PKAt the moment, in order to restore the LS valve core to a force balance state, the LS valve automatically adjusts the discharge capacity of the main pump, then changes the output flow Q, and enables P to be changed againKΔ P is a constant value. I.e. the larger the main valve opening, the larger the pump displacement. Commonly used post-valve compensation multi-way valves are the Lishi LUDV (Load Pressure Lastdrive independent Unabhalengge Flow Durchfans Distribution Verteiilung Load independent Flow Distribution) multi-way valve and the Linde LSC (Linde Synchron Control Linde synchronous Control system) multi-way valve. LUDV means load-independent pressure-flow distribution, i.e. a load-flow independent distribution system, in which a pressure compensation valve is placed after the main valve, and the system pressure is post-valve compensated, when a plurality of actuators are simultaneously operated, as shown in fig. 2, P1>P2, the minimum actuator pressure is compensated for by the maximum actuator pressure (P1), and the actuator differential pressures are kept constant at any time, i.e., Δ P1 is equal to Δ P2, so proportional distribution of the flow rates of the plurality of actuators can be achieved, depending only on the valve opening sizes a1 and a 2. LSC means linde synchronous control, and is the first load-sensitive system that uses post-valve compensation to achieve flow proportional distribution, with principles similar to lissajouv.
For a hydraulic auxiliary system, a common method of the crawler crane at present is to serially connect a gear pump or a medium-pressure plunger pump (a constant pressure pump is used as a quantitative pump) behind a rotary pump to independently supply oil to the auxiliary system. For the transmission scheme of supplying oil to the auxiliary system by adopting the auxiliary pump, on one hand, the universality of the auxiliary pump is not strong because the flow required by the auxiliary system of the cranes with different tonnages is different; the design and development of the crane are a system project, in order to meet the requirement of transportation width, the current crawler crane product is developing towards a 3m vehicle direction, so that the inner space of the rotary table is reduced, and along with the implementation of IV emission standard of non-road state, the engine displacement is increased, the appearance is increased, and the post-processing device is increased, so that the available space of a pump set in the rotary table can be further compressed, and the addition of an auxiliary pump means the need of a larger arrangement space; in addition, the gear pump is limited by structural characteristics, the gear pump is not high in reliability when used for a medium-high pressure system, and a medium-pressure plunger pump for constant-pressure variable control is usually used as an alternative scheme, but economic cost is increased.
SUMMERY OF THE UTILITY MODEL
The utility model provides a not enough to prior art, the utility model provides a hoist extension valves and hydraulic system utilizes the utility model discloses an extension valves can realize auxiliary system and the parallelly connected return circuit structure of main pump system, reduces an auxiliary pump, optimizes auxiliary system, solves the short condition in space office.
In order to achieve the above object, the utility model provides a following technical scheme:
the utility model provides a hoist extension valves which characterized in that: the device comprises a two-position two-way normally closed electromagnetic valve, an adjustable throttle valve, a pressure compensator, an overflow valve, a damper and a valve block; the expansion valve group comprises a pressure oil port, a working oil port, a load feedback oil port and an oil return port which are formed on the valve block; the oil inlet of two lead to normally closed solenoid valve communicates with each other with the pressure hydraulic fluid port of valve block, the oil-out of two lead to normally closed solenoid valve is linked together with the oil inlet of adjustable choke valve, the oil-out of adjustable choke valve is linked together with the oil inlet of pressure compensator, the first mouth of damped of overflow valve and the work hydraulic fluid port of valve block communicate with each other, the oil-out of overflow valve communicates with each other with the oil return opening of valve block, the second mouth of pressure compensation valve, the load feedback hydraulic fluid port of damped second mouth and valve block communicate with each other.
The two-position two-way normally closed electromagnetic valve plays a switching role in the expansion valve bank, when auxiliary action is needed, the two-position two-way normally closed electromagnetic valve is electrified and reversed, liquid flow is introduced into the expansion valve bank, the adjustable throttle valve connected with the expansion valve bank and the pressure compensator behind the adjustable throttle valve form a constant pressure difference system, the overflow valve plays a role of a safety valve and is used for setting the highest pressure of the auxiliary system, and the damping is positioned on the load feedback channel so as to weaken the impact of a load feedback signal on the system.
Further, a two-way normally closed electric proportional valve is adopted to replace the two-position two-way normally closed electromagnetic valve and the adjustable throttle valve, the connection relationship of the expansion valve group is that an oil inlet of the two-way normally closed electric proportional valve is communicated with a pressure oil port of the valve block, an oil outlet of the two-way normally closed electric proportional valve is communicated with an oil inlet of the pressure compensator, a first port of the pressure compensator, an oil inlet of the overflow valve, a first damped port and a working oil port of the valve block are communicated with each other, an oil outlet of the overflow valve is communicated with an oil return port of the valve block, and a second port of the pressure compensation valve, a second damped port and a load feedback oil port of the valve block are communicated with each other.
Further, a two-position two-way normally closed electromagnetic directional valve with a limit screw is adopted to replace the two-position two-way normally closed electromagnetic valve and the adjustable throttle valve, the connection relationship of the expansion valve group is that an oil inlet of the two-position two-way normally closed electromagnetic directional valve with the limit screw is communicated with a pressure oil port of the valve block, an oil outlet of the two-position two-way normally closed electromagnetic directional valve with the limit screw is communicated with an oil inlet of the pressure compensator, a first port of the pressure compensator, an oil inlet of the overflow valve, a first damped port and a working oil port of the valve block are communicated with each other, an oil outlet of the overflow valve is communicated with an oil return port of the valve block, and a second port of the pressure compensation valve, a second damped port and a load feedback oil port of the valve block.
Further, the specification of the damping is 0.6mm damping.
The utility model provides a hoist hydraulic system, includes main pump, main system executive component, main valve, supplementary executive component, supplementary control valves, auxiliary pump, rotary motor, rotary pump and hydraulic tank, its characterized in that: the auxiliary pump is replaced by the expansion valve bank, the expansion valve bank is connected with the main valve in parallel, a pressure oil port of the expansion valve bank is connected with a port P of the main pump, a working oil port of the expansion valve bank is connected with a pressure oil port of the auxiliary control valve bank, and a load feedback oil port of the expansion valve bank is merged into an LS oil port of the main valve through an MLS port connected into the main valve.
Further, when only the auxiliary system works, the pressure compensation valve in the expansion valve bank can be omitted, at the moment, the connection relationship of the expansion valve bank is that the oil inlet of the two-position two-way normally closed solenoid valve is communicated with the pressure oil port of the valve block, the oil outlet of the two-position two-way normally closed solenoid valve is communicated with the oil inlet of the adjustable throttle valve, the oil outlet of the adjustable throttle valve, the oil inlet of the overflow valve, the first damped port and the working oil port of the valve block are communicated with each other, the oil outlet of the overflow valve is communicated with the oil return port of the valve block, and the second damped port and the load feedback oil port of the valve block are communicated with each other.
Compared with the prior art, the utility model provides a hoist extension valves and hydraulic system possesses following beneficial effect:
(1) the utility model provides an extension valves, to the valve back compensation load name control system that crawler crane is commonly used, can regard the main pump of big discharge (system flow more than 300L/min) as the oil source, the output supplies auxiliary system for the low discharge (flow 30-70L/min usually), does not influence main system and auxiliary system combined action simultaneously, utilizes the utility model discloses an extension valves, can realize auxiliary system and the parallelly connected loop structure of main pump system, reduces an auxiliary pump, optimizes auxiliary system, solves the situation that the space is compelled;
(2) by adjusting the expansion valve group, the stepless adjustment of the flow of the auxiliary system can be realized within a certain flow range (the flow adjustment range is related to the through-flow capacity of the throttle valve), the adaptability is stronger, and the expansion valve group can be popularized and used on various tonnage crawler cranes;
(3) the utility model discloses an extension valves, when existing product has new function demand, nimble system architecture extension is realized to usable this valves.
Drawings
FIG. 1 is a schematic diagram of a prior art load-sensitive pump;
FIG. 2 is a schematic diagram of a prior art LUDV system;
FIG. 3 is a schematic diagram of a hydraulic system of a crawler crane in the prior art;
FIG. 4 is a schematic partial view of a LUDV main valve of a crane according to the prior art;
fig. 5 is a schematic diagram of the middle expansion valve group of the present invention;
fig. 6 is a schematic diagram of a crane hydraulic system according to the present invention (the expansion valve set shown in fig. 5 is used);
FIG. 7 is a schematic diagram of a two-way normally closed electro proportional valve;
FIG. 8 is a two-position two-way normally closed electromagnetic directional valve with a limit screw;
fig. 9 shows another scheme of the damping position setting in the middle expansion valve set of the present invention.
The reference numerals in the figures have the meaning: 1-main pump; 2-main system actuator; 3-a main valve; 3.1-LS shuttle valve; 3.2-main overflow valve; 3.3-relief valves; 3.4-pressure compensation valve; 3.5-other main valve; 3.6-LS overflow valve; 3.7-LS flow controller; 4-an auxiliary actuator; 5-auxiliary control valve group; 6-an auxiliary pump; 7-a rotary motor; 8-a rotary pump; 9-a hydraulic oil tank; 10-expanding the valve group; 10.1-two-position two-way normally closed electromagnetic valve; 10.2-adjustable throttle valve; 10.3-pressure compensator; 10.4-relief valve; 10.5-damping; 10.6-valve block.
Detailed Description
The technical solutions in the embodiments of the present invention will be described clearly and completely with reference to the accompanying drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only some embodiments of the present invention, not all embodiments. Based on the embodiments in the present invention, all other embodiments obtained by a person skilled in the art without creative work belong to the protection scope of the present invention.
As shown in fig. 3, fig. 3 is a simplified diagram of a hydraulic system of a crawler crane, a main pump 1, a rotary pump 8 and an auxiliary pump 6 are connected in series to form a pump set, the main hydraulic system and the auxiliary hydraulic system are respectively provided with oil sources by the main pump 1 and the auxiliary pump 6, the two systems are relatively independent, and the main action and the auxiliary action do not affect each other when performing compound actions. The main system flow is generally above 300L/min, the auxiliary system flow is generally 30-70L/min, the main pump 1 is a large displacement load-sensitive pump, and the auxiliary pump 6 is a small displacement pump. Generally speaking, the auxiliary system pressure level is between 20-25MPa, belonging to medium pressure system, and considering the cost, a gear pump or a medium pressure plunger pump (constant pressure variable control) is usually selected as the auxiliary pump 6. The auxiliary switch of the crane is turned on, the auxiliary pump 6 supplies oil to the auxiliary control valve 5, the auxiliary control valve 5 is operated to change direction through a remote control box or a handle to realize auxiliary action, and when the auxiliary control valve 5 is not operated, the auxiliary pump 6 is unloaded, which is a transmission scheme commonly used by the auxiliary hydraulic system of the crawler crane at present.
As shown in fig. 4, fig. 4 is a schematic partial schematic diagram of a LUDV main valve of a crane in the prior art, and includes an LS shuttle valve 3.1, a main overflow valve 3.2, an unloading valve 3.3, a pressure compensation valve 3.4, a main valve other link 3.5, an LS overflow valve 3.6, and an LS flow controller 3.7.
As shown in fig. 5, the crane expansion valve group comprises a two-position two-way normally closed solenoid valve 10.1, an adjustable throttle valve 10.2, a pressure compensator 10.3, an overflow valve 10.4, a damper 10.5 and a valve block 10.6; the expansion valve group comprises a pressure oil port P, a working oil port A, a load feedback oil port LS and an oil return port T; an oil inlet r of the two-position two-way normally closed solenoid valve 10.1 is communicated with a pressure oil port P of the valve block 10.6, an oil outlet b of the two-position two-way normally closed solenoid valve 10.1 is communicated with an oil inlet c of the adjustable throttle valve 10.2, an oil outlet d of the adjustable throttle valve 10.2 is communicated with an oil inlet e of the pressure compensator 10.3, a first port f of the pressure compensator 10.3, an oil inlet h of the overflow valve 10.4, a first port k of the damper 10.5 and a working oil port A of the valve block 10.6 are communicated with each other, an oil outlet i of the overflow valve 10.4 is communicated with an oil return port T of the valve block 10.6, and a second port g of the pressure compensation valve 10.3, a second port j of the damper 10.5 and a load feedback oil port LS of the.
The two-position two-way normally closed solenoid valve 10.1 plays a switching role in the expansion valve bank, when auxiliary action is needed, the two-position two-way normally closed solenoid valve 10.1 is electrified and reversed, liquid flow is introduced into the expansion valve bank, the adjustable throttle valve 10.2 connected with the expansion valve bank and the pressure compensator 10.3 behind the adjustable throttle valve form a constant pressure difference system, the overflow valve 10.4 plays a role of a safety valve and is used for setting the highest pressure of the auxiliary system, and the damper 10.5 is positioned on a load feedback channel so as to weaken the impact of a load feedback signal on the system.
In one embodiment of this embodiment, the damping 10.5 is specified as 0.6mm damping.
To flow system surely, the utility model discloses an adjustable throttle valve 10.2 among the extension valves is calculated through the emulation and also can be replaced by a fixed damping, realizes the constant flow of auxiliary system.
For applications where there is no combined action of the auxiliary system and the main system, the pressure compensator 10.3 in the expansion valve block may even be eliminated.
Aiming at the situation that the pressure of the auxiliary system is equivalent to that of the main system or the auxiliary control valve group 5 comprises an overflow valve, the overflow valve 10.4 in the expansion valve group 10 can be eliminated, and the function of the valve can be realized by the main overflow valve of the main valve 3 or the overflow valve on the auxiliary control valve group 5.
As shown in fig. 9, if the LS port of the extension valve set 10 of the present invention is connected to the MLS port of the main valve 3, the damping 10.5 on the feedback oil path of the extension valve set 10 can be moved to between the spring cavity of the pressure compensator 10.3 and the feedback oil path.
The utility model discloses an extension valves is except can being used to hoist hydraulic pressure auxiliary system, still can be used to any hydraulic system who adopts compensation load sensing system behind the valve and have independent little flow demand. Additionally, the utility model discloses also can cooperate exclusive use with the sensitive pump of load, constitute simple and easy volume speed governing system, realize the volume speed governing in the certain flow range.
A crane hydraulic system comprises a main pump 1, a main system executing element 2, a main valve 3, an auxiliary executing element 4, an auxiliary control valve group 5, an auxiliary pump 6, a rotary motor 7, a rotary pump 8 and a hydraulic oil tank 9, wherein the auxiliary pump 6 is replaced by an expansion valve group 10, an oil inlet P of the expansion valve group is branched from a main system LS load sensitive pump and is connected with the main system LUDV main valve 3 in parallel to serve as an expansion joint, a pressure oil port P of the expansion valve group 10 is connected with a port P of the main pump, a working oil port A of the expansion valve group 10 is connected with the pressure oil port P of the auxiliary control valve group 5 to supply oil to an auxiliary system, a load feedback oil port LS of the expansion valve group 10 is connected into an LS oil path of the LUDV main valve 3 through an MLS port connected into the main valve 3, and the expansion valve.
In a specific embodiment of this embodiment, the main pump 1 is a load-sensitive pump, the main system actuator 2 is each driving motor of a crane, the main valve 3 is a LUDV multi-way valve, the auxiliary actuator 4 is each auxiliary cylinder of the crane, and the rotary pump 8 is a closed pump.
In a specific implementation manner of this embodiment, when only the auxiliary system is operating, the load-sensitive main pump of the pressure compensator 10.3 is left to provide a stable liquid flow to the auxiliary system, at this time, the connection relationship of the expansion valve group 10 is that an oil inlet r of the two-position two-way normally closed solenoid valve 10.1 is communicated with the pressure port P of the valve block 10.6, an oil outlet b of the two-position two-way normally closed solenoid valve 10.1 is communicated with an oil inlet c of the adjustable throttle 10.2, an oil outlet d of the adjustable throttle 10.2, an oil inlet h of the overflow valve 10.4, a first port k of the damper 10.5 and a working port a of the valve block 10.6 are communicated with each other, an oil outlet i of the overflow valve 10.4 is communicated with an oil return port T of the valve block 10.6, and a second port j of the damper 10.5 and a load feedback port LS.
The working process is as follows:
when the two-position two-way normally closed electromagnetic valve 10.1 is reversed, oil liquid of the load sensitive main pump 1 enters the expansion valve group 10, the opening amount of the adjustable throttle valve 10.2 is a, when the load sensitive main pump is used as a certain linkage action of the auxiliary control valve 5, liquid flow flows to the auxiliary execution element 4 from an opening A of the expansion valve group 10 through the auxiliary control valve group 5, and the load pressure is PLSThe pump port pressure is P0At this time, the sum Δ P of the differential pressure across the adjustable throttle valve 10.2 and the differential pressure across the pressure compensator 10.3 of the expansion valve group 10 is equal to P0-PLS(ii) a Pump port pressure P0Acting simultaneously on the left end of the spool of the main pump variable volume valve (LS valve), PLSWith a predetermined spring pressure PKThe (constant value) acts on the right end of the valve core together, and at the moment of reversing the auxiliary control valve group 5, the pressure difference between the two ends of the LS valve can be dynamically adjusted until the LS valve core is stressed in balance, and P isK=P0-PLSΔ P, the main pump 1 maintains a stable displacement. When the LS valve spring of the main pump 1 is at the preset pressure PKAt a certain time, and at a certain opening of the adjustable throttle 10.2 of the extension valve group 10, the main pump 1 is finally stabilized at a fixed displacement, providing a stable oil source for the auxiliary system. Different from the traditional throttling speed regulation, the load-sensitive main pump 1 can be changed in displacement by regulating the valve, and the variable displacement hydraulic variable valve is a volume speed regulation mode. The 0.6mm damping on the LS feedback oil path of the expanded valve group 10 is used for preventing the dynamic adjustment process of the LS valve from being too violent, and further leading the pressure of the system to vibrate violently.
As shown in fig. 6, when the auxiliary system and the main system perform a combined action, when the auxiliary system load is greater than the main system load, i.e. the auxiliary system load pressure P1, the main system load pressure is P2, and P1> P2. When the main valve changes direction in a certain group (opening a1) and the auxiliary control valve group 5 changes direction in a certain group (opening a2), the main valve 3 and the expansion valve group 10 are communicated with each other and respond to each other, so that the pressure signal P2 with a large load is fed back to the right end of the LS valve of the main pump, and the signal is fed back to the spring cavity of the pressure compensator 10.3 of the main valve action group pressure compensator and the expansion valve group 10, so that the pressure difference of each actuating mechanism is kept constant at any time, namely, the pressure difference DeltaP 1 is DeltaP 2, therefore, the proportional distribution of the flow of a plurality of actuating mechanisms can be realized, and the proportional distribution is only related to the valve opening sizes a1 and a 2. The pressure (P1-P2) compensated by the highest load on the low pressure connection is consumed by the pressure compensator, and the pressure compensator 10.3 plays a role of ensuring that the pressure difference before and after the throttling ports of all the working connections is equal when two or more actions are combined. And vice versa when the main system load is greater than the auxiliary load. Although the auxiliary system is shunted from the main system, the situation that the flow is towards the low load and the high load does not act when the loads are different does not occur, and the flow of the auxiliary system and the main system is ensured to be distributed as required.
Example 2
This example differs from example 1 in that: as shown in fig. 7, the two-position two-way normally closed solenoid valve 10.1 and the adjustable throttle valve 10.2 of the expansion valve group 10 can also be replaced by a two-way normally closed electric proportional valve, the schematic diagram of which is shown in fig. 7, is equivalent to integrating a two-way electromagnetic directional valve and an adjustable throttle valve, and stepless speed regulation can be realized by giving different current signals to the proportional valve.
A two-way normally closed electric proportional valve is adopted to replace a two-position two-way normally closed electromagnetic valve 10.1 and an adjustable throttle valve 10.2, the connection relationship of an expansion valve group is that an oil inlet of the two-way normally closed electric proportional valve is communicated with a pressure oil port P of a valve block 10.6, an oil outlet of the two-way normally closed electric proportional valve is communicated with an oil inlet e of a pressure compensator 10.3, a first port f of the pressure compensator 10.3, an oil inlet h of an overflow valve 10.4, a first port k of a damper 10.5 and a working oil port A of the valve block 10.6 are communicated with each other, an oil outlet i of the overflow valve 10.4 is communicated with an oil return port T of the valve block 10.6, and a second port g of the pressure compensating valve 10.3, a second port j of the damper 10.5 and a load feedback oil port LS.
Example 3
This example differs from example 1 in that: as shown in fig. 8, the functions of the two-position two-way normally closed solenoid valve 10.1 and the adjustable throttle valve 10.2 of the expansion valve group 10 can also be replaced by a two-position two-way normally closed solenoid directional valve with a limit screw, a valve core with a full-circumference opening of a conventional solenoid valve can be changed into a throttling groove, and the maximum opening degree of the valve core can be adjusted by adjusting the limit screw, so that the stepless adjustment of the flow rate is realized.
The two-position two-way normally closed electromagnetic directional valve with the limiting screw is adopted to replace the two-position two-way normally closed electromagnetic valve 10.1 and the adjustable throttle valve 10.2, the connection relationship of the expansion valve group 10 is that an oil inlet of the two-position two-way normally closed electromagnetic directional valve with the limiting screw is communicated with a pressure oil port P of the valve block 10.6, an oil outlet of the two-position two-way normally closed electromagnetic directional valve with the limiting screw is communicated with an oil inlet e of the pressure compensator 10.3, a first port f of the pressure compensator 10.3, an oil inlet h of the overflow valve 10.4, a first port k of the damper 10.5 and a working oil port A of the valve block 10.6, an oil outlet i of the overflow valve 10.4 is communicated with an oil return port T of the valve block 10.6, and a second port g of the pressure compensator valve 10.3, a second port j of the damper 10.5 and a load feedback oil port.
The utility model discloses an extension valves 10 is based on the load sensing control system realization work of valve back compensation, and the system pump mouth of following owner shunts, supplies the auxiliary action oil source. The extension valves adopts compensation technique behind the valve, through LS feedback oil circuit with extension valves 10 as independent antithetical couplet can with the main system compensate the multiple unit valve parallelly connected behind the valve, each other is for responding, realizes load flow independent distribution, can stepless speed regulation through adjustable choke valve 10.2, satisfies wider function demand, when existing product has new function demand, usable the utility model discloses extension valves 10 realizes nimble system architecture extension.
It is noted that, herein, relational terms such as first and second, and the like may be used solely to distinguish one entity or action from another entity or action without necessarily requiring or implying any actual such relationship or order between such entities or actions. Also, the terms "comprises," "comprising," or any other variation thereof, are intended to cover a non-exclusive inclusion, such that a process, method, article, or apparatus that comprises a list of elements does not include only those elements but may include other elements not expressly listed or inherent to such process, method, article, or apparatus. Without further limitation, an element defined by the phrase "comprising an … …" does not exclude the presence of other identical elements in a process, method, article, or apparatus that comprises the element.
Although embodiments of the present invention have been shown and described, it will be appreciated by those skilled in the art that changes, modifications, substitutions and alterations can be made in these embodiments without departing from the principles and spirit of the invention, the scope of which is defined in the appended claims and their equivalents.

Claims (6)

1. The utility model provides a hoist extension valves which characterized in that: the device comprises a two-position two-way normally closed electromagnetic valve, an adjustable throttle valve, a pressure compensator, an overflow valve, a damper and a valve block; the expansion valve group comprises a pressure oil port, a working oil port, a load feedback oil port and an oil return port which are formed on the valve block; the oil inlet of two lead to normally closed solenoid valve communicates with each other with the pressure hydraulic fluid port of valve block, the oil-out of two lead to normally closed solenoid valve is linked together with the oil inlet of adjustable choke valve, the oil-out of adjustable choke valve is linked together with the oil inlet of pressure compensator, the first mouth of damped of overflow valve and the work hydraulic fluid port of valve block communicate with each other, the oil-out of overflow valve communicates with each other with the oil return opening of valve block, the second mouth of pressure compensator, the load feedback hydraulic fluid port of damped second mouth and valve block communicate with each other.
2. The crane extension valve group of claim 1, wherein: the two-position two-way normally closed electromagnetic valve and the adjustable throttle valve are replaced by a two-way normally closed electric proportional valve, the connection relationship of the expansion valve group is that an oil inlet of the two-way normally closed electric proportional valve is communicated with a pressure oil port of the valve block, an oil outlet of the two-way normally closed electric proportional valve is communicated with an oil inlet of the pressure compensator, a first port of the pressure compensator, an oil inlet of the overflow valve, a first damped port and a working oil port of the valve block are communicated with each other, an oil outlet of the overflow valve is communicated with an oil return port of the valve block, and a second port of the pressure compensator, a second damped port and a load feedback oil port of the valve block are communicated with each other.
3. The crane extension valve group of claim 1, wherein: the two-position two-way normally closed electromagnetic directional valve with the limiting screw is adopted to replace the two-position two-way normally closed electromagnetic valve and the adjustable throttle valve, the connection relationship of the expansion valve group is that an oil inlet of the two-position two-way normally closed electromagnetic directional valve with the limiting screw is communicated with a pressure oil port of the valve block, an oil outlet of the two-position two-way normally closed electromagnetic directional valve with the limiting screw is communicated with an oil inlet of the pressure compensator, a first port of the pressure compensator, an oil inlet of the overflow valve, a first damped port and a working oil port of the valve block are communicated with each other, an oil outlet of the overflow valve is communicated with an oil return port of the valve block, and a second port of the pressure compensator, a second damped port and a load feedback oil port of the valve.
4. The crane extension valve group of claim 1, wherein: the specification of the damping is 0.6mm damping.
5. The utility model provides a hoist hydraulic system, includes main pump, main system executive component, main valve, supplementary executive component, supplementary control valves, rotary motor, rotary pump and hydraulic tank, its characterized in that: the expansion valve set of any one of claims 1-4, wherein the expansion valve set is connected with the main valve in parallel, a pressure oil port of the expansion valve set is connected with a P port of the main pump, a working oil port of the expansion valve set is connected with a pressure oil port of the auxiliary control valve set, and a load feedback oil port of the expansion valve set is merged into an LS oil port of the main valve through an MLS port connected into the main valve.
6. The crane hydraulic system as claimed in claim 5, wherein: when only the auxiliary system works, the pressure compensator in the expansion valve bank can be omitted, at the moment, the connection relationship of the expansion valve bank is that the oil inlet of the two-position two-way normally closed solenoid valve is communicated with the pressure oil port of the valve block, the oil outlet of the two-position two-way normally closed solenoid valve is communicated with the oil inlet of the adjustable throttle valve, the oil outlet of the adjustable throttle valve, the oil inlet of the overflow valve, the first damped port and the working oil port of the valve block are communicated with each other, the oil outlet of the overflow valve is communicated with the oil return port of the valve block, and the second damped port and the load feedback oil port of the valve block are communicated with each other.
CN202022084442.2U 2020-09-21 2020-09-21 Crane extension valve group and hydraulic system Active CN212744559U (en)

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN116447191A (en) * 2023-04-10 2023-07-18 重庆大学 Active damping compensation vibration suppression method for dual-actuator valve port independent control system

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN116447191A (en) * 2023-04-10 2023-07-18 重庆大学 Active damping compensation vibration suppression method for dual-actuator valve port independent control system
CN116447191B (en) * 2023-04-10 2024-01-16 重庆大学 Active damping compensation vibration suppression method for dual-actuator valve port independent control system

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