CN109519428A - A kind of more hydraulic pump multiplex control systems, work connection and engineering machinery - Google Patents

A kind of more hydraulic pump multiplex control systems, work connection and engineering machinery Download PDF

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Publication number
CN109519428A
CN109519428A CN201910019072.3A CN201910019072A CN109519428A CN 109519428 A CN109519428 A CN 109519428A CN 201910019072 A CN201910019072 A CN 201910019072A CN 109519428 A CN109519428 A CN 109519428A
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CN
China
Prior art keywords
valve
control
load
pump
signal
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Granted
Application number
CN201910019072.3A
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Chinese (zh)
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CN109519428B (en
Inventor
景军清
王普长
刘灿杰
马浩
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Jiangsu Advanced Construction Machinery Innovation Center Ltd
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Jiangsu Advanced Construction Machinery Innovation Center Ltd
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Priority to CN201910019072.3A priority Critical patent/CN109519428B/en
Publication of CN109519428A publication Critical patent/CN109519428A/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/17—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors using two or more pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/06—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with two or more servomotors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20538—Type of pump constant capacity
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20546—Type of pump variable capacity
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/20576—Systems with pumps with multiple pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/71—Multiple output members, e.g. multiple hydraulic motors or cylinders

Abstract

The invention discloses a kind of more hydraulic pump multiplex control systems, comprising: at least two hydraulic pumps, including at least one variable pump；At least two executing agencies, respectively connection corresponding at least two hydraulic pump；And signal conversion module, for selectively according to the load-sensitive signal of the corresponding executing agency of at least two hydraulic pump, being converted to the load-sensitive signal for the Ioad-sensing control chamber for being input to the variable pump.The embodiment of the present invention enables to the movement between multiple executing agencies in double pump oil supply system more to coordinate by setting signal conversion module.

Description

A kind of more hydraulic pump multiplex control systems, work connection and engineering machinery
Technical field
The present invention relates to engineering machinery field more particularly to a kind of more hydraulic pump multiplex control systems, work connection and engineering It is mechanical.
Background technique
Hydraulic pump is for the device of engineering machinery fuel feeding, and wherein constant displacement pump and variable pump are the forms of two kinds of hydraulic pumps.When When engineering machinery is using quantitative pump control system, hydraulic structure is relatively simple, system responds sensitive and executing agency's setting in motion Operating point determined completely by the unlatching of system service aisle.And when using variable pump control system, then it can correspondingly make to become The pivot angle of pump and the state (stroke of spool or the aperture of valve port) of control valve are measured with certain relationship change, so that variable pump Output flow is determined by the operating rate demand of actuator.
However individually use constant displacement pump for hydraulic system fuel feeding, can accordingly generate hydraulic system to the bad adaptability of load, The problems such as performance is unstable and power loss is big.And individually then can accordingly be generated using variable pump: variable pump systems are being held more When row device moves at the same time, actuator motions speed is obvious by load effect, and the highest element of load pressure, which exists, at this time stops fortune Dynamic possibility；And the characteristic being mutually matched as possessed by variable pump and multi-way valve, so that hydraulic system can only apply phase The Hydraulic Elements for answering parameter lead to problems such as element application range be restricted.
In addition, there is the scenes of more executing agencies synchronous working in engineering machinery field.It is with telescopic arm crane Example, generally there are elevator, luffing and the operation such as flexible, and often elevator and luffing, elevator and flexible or elevator and elevator Between need to carry out composite move.Based on this, existing engineering machinery face composite move scene, mostly use constant displacement pump with The double pump of variable pump combination is for oil form, to achieve the effect that oil inlet loss less and flexible conversion fuel system.
But in relevant double pump oil supply system, the control signal of variable pump systems is fixed, can not be according to host operating condition Variation and change itself fuel delivery；And double pump oil supply system mostly uses valve precompensation principle, multiple executing agencies simultaneously When movement, preferentially meet the lower executing agency of workload, so that the exercise not harmony between multiple executing agencies；And it is double Oil pump feed is separately connected oil circuit, so that fluid pressure line is more complex, is unfavorable for carrying out hydraulic system maintenance and emergency processing.
Summary of the invention
At least one purpose of the invention is to propose a kind of more hydraulic pump multiplex control systems, work connection and engineering machinery, The movement between multiple executing agencies in double pump oil supply system is enabled to more to coordinate.Many technical sides provided by the invention Many technical effects elaboration as detailed below that optimal technical scheme in case can be generated.
To achieve the above object, the present invention provides following technical schemes:
A kind of more hydraulic pump multiplex control systems provided by the invention, comprising: at least two hydraulic pumps, including at least One variable pump；At least two executing agencies, respectively connection corresponding at least two hydraulic pump；And signal modulus of conversion Block, for selectively according to the load-sensitive signal of the corresponding executing agency of at least two hydraulic pump, to input Load-sensitive signal to the Ioad-sensing control chamber of the variable pump is converted.
The optimization of technical solution, described after any technical solution or any optimization that provide above or hereinafter as the present invention Control system includes: signal screening module, is set to the load-sensitive signal of the signal conversion module Yu the executing agency Between, it is exported for load-sensitive signal described in the Rules Filtering with setting, and by the selection result to the signal conversion module.
The optimization of technical solution, described after any technical solution or any optimization that provide above or hereinafter as the present invention Control system includes: the first hydraulic pump, corresponding first executing agency and the first load-sensitive signal；And second hydraulic pump, it is right Answer the second executing agency and the second load-sensitive signal；The feedback signal screening module includes: the first control valve, Neng Gouxuan It selects to the signal conversion module and exports the first load-sensitive signal, the second load-sensitive signal or described first Pressure the greater in load-sensitive signal and the second load-sensitive signal, or make the first load-sensitive signal with it is described Second load-sensitive signal is back to fuel tank.
The optimization of technical solution, described after any technical solution or any optimization that provide above or hereinafter as the present invention First control valve is four four-way control valves；The feedback signal screening module includes: the first reversal valve, can be by described first One control mouth of control valve selectively connection to pilot pressure oil sources or fuel tank；And second reversal valve, it can will be described Another control mouth of first control valve selectively connection to pilot pressure oil sources or fuel tank.
The optimization of technical solution, described after any technical solution or any optimization that provide above or hereinafter as the present invention At least one in first reversal valve and second reversal valve can make first control valve be at least two different works Make position.
The optimization of technical solution, described after any technical solution or any optimization that provide above or hereinafter as the present invention Signal conversion module includes: proportioning valve, one of oil inlet connection of the proportioning valve at least two hydraulic pump, Neng Gougen According to the proportionate relationship between the load-sensitive signal received and the spring force of setting, the pressure signal of oil inlet is converted to defeated Enter the load-sensitive signal to the Ioad-sensing control chamber of the variable pump.
The optimization of technical solution, described after any technical solution or any optimization that provide above or hereinafter as the present invention Proportional pressure-reducing valve is electric proportional valve, can be according to the spring force of the load-sensitive signal, setting received and electric proportional valve The pressure signal of oil inlet is converted to the Ioad-sensing control chamber for being input to the variable pump by the proportionate relationship between active force Load-sensitive signal.
The optimization of technical solution, described after any technical solution or any optimization that provide above or hereinafter as the present invention Electric proportional valve can further receive the pressure of oil inlet, and according to spring force, the electricity of the load-sensitive signal, setting that receive The pressure signal of oil inlet is converted to and is input to institute by the proportionate relationship between the active force of proportioning valve and the pressure of oil inlet State the load-sensitive signal of the Ioad-sensing control chamber of variable pump.
The optimization of technical solution, described after any technical solution or any optimization that provide above or hereinafter as the present invention Control system includes: interflow control module, can selectively control at least two hydraulic pump in an independent way to right The executing agency's fuel feeding answered, or to one of at least two executing agency fuel feeding in a manner of interflow.
The optimization of technical solution, described after any technical solution or any optimization that provide above or hereinafter as the present invention Collaborating control module includes: interflow control valve group, and connection at least two hydraulic pump can control at least two liquid Oil circuit connection or disconnection between press pump.
The optimization of technical solution, described after any technical solution or any optimization that provide above or hereinafter as the present invention Control valve group includes: the second control valve, is inserted valve, for controlling the connection on-off of the oil circuit between at least two hydraulic pump It opens；And third control valve, the control mouth and at least two hydraulic pumps connection of second control valve can be controlled, or return It flow to fuel tank.
The optimization of technical solution, described after any technical solution or any optimization that provide above or hereinafter as the present invention Collaborating control module includes: shuttle valve, is set to the oil circuit of the second control valve connection at least two hydraulic pump, is used for Make one of second control valve and discharge highest at least two hydraulic pump of oil pressure connection.
The optimization of technical solution, described after any technical solution or any optimization that provide above or hereinafter as the present invention Control system includes: constant flow module, and the delivery outlet of connection to the signal conversion module is input to the variable pump for making The load-sensitive signal of Ioad-sensing control chamber is back to fuel tank with the flow part that sets.
The optimization of technical solution, described after any technical solution or any optimization that provide above or hereinafter as the present invention Constant flow module includes: the first overflow valve, is set between the signal conversion module and fuel tank；And first throttle valve, with institute Overflow valve parallel connection is stated, and is set between the signal conversion module and fuel tank.
The optimization of technical solution, described after any technical solution or any optimization that provide above or hereinafter as the present invention Control system includes: constant displacement pump, corresponding constant displacement pump executing agency and constant displacement pump load-sensitive signal；And variable pump, to strain Liang Beng executing agency and variable pump load-sensitive signal.
The optimization of technical solution, described after any technical solution or any optimization that provide above or hereinafter as the present invention Control system includes: pressure compensator, is set to the oil circuit of the constant displacement pump and fuel tank, and a control mouth connection is to described The oil inlet of pressure compensator, another control mouth connection to the constant displacement pump load-sensitive signal or the variable pump load are quick Feel signal.
The optimization of technical solution, described after any technical solution or any optimization that provide above or hereinafter as the present invention Control system includes: fixed pressure reducing valve, can be under the action of the spring force of setting and the pilot pressure oil sources pressure, by institute It states pilot pressure oil sources and distinguishes connection to the variable pump or the fuel tank；Second throttle is set to the fixed pressure reducing valve With the oil circuit of the variable pump；And the 4th overflow valve, it is set to the oil circuit of the pilot pressure oil sources and the fuel tank, it can The pilot pressure oil sources is set to be back to fuel tank according to the pressure of setting.
The optimization of technical solution, described after any technical solution or any optimization that provide above or hereinafter as the present invention Control system includes: interflow control module, can selectively control at least two hydraulic pump in an independent way to right The executing agency's fuel feeding answered, or to one of at least two executing agency fuel feeding in a manner of interflow.
The present invention also provides a kind of work connection, including more hydraulic pump multiplex control systems as previously described.
Invention further provides a kind of engineering machinery, including the compound control of more hydraulic pumps as described in any one above System processed.
Based on the above-mentioned technical proposal, the embodiment of the present invention is by signal conversion module, selectively according to described at least two The load-sensitive signal of the corresponding executing agency of a hydraulic pump, to the Ioad-sensing control chamber for being input to the variable pump Load-sensitive signal is converted, so that the movement between multiple executing agencies in double pump oil supply system is more coordinated.
Detailed description of the invention
The drawings described herein are used to provide a further understanding of the present invention, constitutes part of this application, this hair Bright illustrative embodiments and their description are used to explain the present invention, and are not constituted improper limitations of the present invention.In the accompanying drawings:
Fig. 1 is more hydraulic pump multiplex control system hydraulic flow path structural schematic diagrams provided by the embodiment of the present invention；
In figure: P1 constant displacement pump, P2 variable pump, first executing agency's hydraulic fluid port of A1, B1, second executing agency's hydraulic fluid port of A2, B2, A3, B3 third executing agency hydraulic fluid port, first executing agency's hydraulic fluid port pressure tap of MA1, MB1, second executing agency's hydraulic fluid port of MA2, MB2 are surveyed Press mouth, MA3, MB3 third executing agency hydraulic fluid port pressure tap, X pilot pressure oil sources, LS1 constant displacement pump load-sensitive signal, LS2 change Measure pump load sensitive signal, 110 signal screening modules, 120 interflow control modules, 9 signal conversion modules, 1 overflow valve, 2 definite values Pressure reducing valve, 3 overflow valves, 4-1~4-3 switching valve, 5-1~5-8 solenoid directional control valve valve, 6-1~6-3 check valve, 7-1~7-2 pressure Force compensating device, 8-1~8-2 safety valve, 10 constant flow modules, 11 pressure compensators, the main overflow valve of 12 constant displacement pumps, 13 determine subtractive pressure Valve, 14 uniform-pressure-drop valves, 15 first control valves, 16 shuttle valves, 17 solenoid directional control valves, 18 inserted valves.
Specific embodiment
It is referred to attached drawing below and word content understands between the contents of the present invention and the present invention and the prior art Distinctive points.Hereafter attached drawing and by way of enumerating some alternative embodiments of the invention, to technical solution of the present invention (including optimal technical scheme) is described in further detail.
It should be understood that any technical characteristic, any technical solution in the present embodiment are the technologies of plurality of optional One or more of feature or optional technical solution, in order to describe it is succinct need it is impossible to exhaust of the invention in this document All alternative technical characteristics and alternative technical solution, the embodiment for being also not easy to each technical characteristic are emphasized It is one of for optional numerous embodiments, so those skilled in the art will appreciate that can will be provided by the invention any Technological means is replaced or any two or more technical means or technical features provided by the invention is carried out mutually group It closes and obtains new technical solution.
Any technical characteristic and any technical solution in the present embodiment do not limit the scope of the invention, this hair Bright protection scope should include that those skilled in the art do not make the creative labor the thinkable any alternate embodiments of institute And any two or more technical means or technical features provided by the invention are carried out mutually group by those skilled in the art New technical solution obtained from conjunction.
The embodiment of the invention provides a kind of more hydraulic pump multiplex control systems, comprising: at least two hydraulic pumps, wherein wrapping Include at least one variable pump；At least two executing agencies, respectively connection corresponding at least two hydraulic pump；And signal turns Block is changed the mold, it is right for selectively according to the load-sensitive signal of the corresponding executing agency of at least two hydraulic pump The load-sensitive signal for being input to the Ioad-sensing control chamber of the variable pump is converted.
In hydraulic system, load sensitive system refers to the pressure of impression system, flow demand, and provides needed for system Flow and pressure hydraulic circuit.For constant displacement pump hydraulic circuit, constant flow load sensitive system structure is simple, system Corresponding sensitive, the operating point of executive device setting in motion is determined by the unlatching of system service aisle completely.For variable pump hydraulic pressure For circuit, variable pump can be controlled on demand, i.e., the state of the pivot angle of variable pump and control valve (open by spool stroke or valve port Degree) can be by certain relationship change, therefore the output flow of variable pump will be determined by the corresponding operating rate demand of executive device It is fixed.
More hydraulic pump multiplex control systems provided by the present invention have at least one variable pump, therefore, by executing agency Load-sensitive signal converted, and be input to the Ioad-sensing control chamber of variable pump, variable pump can be made correspondingly to export Different flows with meet hydraulic system under different operating conditions to flow the needs of.
Further, since including at least two executing agencies in the present invention, therefore quick for the load for being input to variable pump The load-sensitive signal of sense chamber can choose the load-sensitive signal of the executing agency corresponding to the variable pump, can also choose not The load-sensitive signal of executing agency corresponding to the variable pump, for example, can choose the corresponding executing agency of other variable pumps or The load-sensitive signal of the corresponding executing agency of constant displacement pump, specifically can be according to variable pump in different displacements, different pressure levels Under needs and flexibly choose, to expand load-sensitive signal under the premise of not changing the design of more hydraulic pump oil circuits and answer With range, so that the movement between multiple executing agencies is more coordinated.
The optimization of technical solution, described after any technical solution or any optimization that provide above or hereinafter as the present invention Control system includes: signal screening module, is set to the load-sensitive signal of the signal conversion module Yu the executing agency Between, it is exported for load-sensitive signal described in the Rules Filtering with setting, and by the selection result to the signal conversion module.
As previously mentioned, in order to which the load-sensitive signal to the Ioad-sensing control chamber for being input to the variable pump carries out effectively Control, the present invention are gone out the load-sensitive signal screening of at least two executing agency by signal screening module, and to letter The output of number conversion module.Wherein, the rule of the setting may include: at least two executing agency it is specific some Mode screens load-sensitive signal；The load-sensitive letter of at least two executing agency is screened with certain population size relationship Number, such as choose pressure the maximum or pressure reckling；With the load of at least two executing agencies described in certain conditional filtering Sensitive signal, such as under specific stress level, filter out the load-sensitive signal of specific executing agency；Or to it is described extremely The load-sensitive signal of Shao Liangge executing agency.
The screening rule of above-mentioned signal screening module is impossible to exhaust, therefore it will be appreciated by those skilled in the art that the present invention Key point be screen thinking, i.e., so as to signal conversion module export a specific executing agency load-sensitive letter Number, and at this time since the rule of screening is controllable, it is possible to further such that being converted to by signal conversion module Load-sensitive signal be controllable.
The technical effect generated therefrom includes:
Keep the control mode for the load-sensitive signal for feeding back to variable pump more flexible, tradition is overcome to export single pressure work The mode of matter signal enables variable pump (to be executed according to loading condition by controlling the screening rule of load-sensitive signal The flow and pressure demand of mechanism), change the operating condition of itself；
The influence for overcoming the load-sensitive signal for feeding back to variable pump to fluctuate vulnerable to system pressure, by the way that constant displacement pump is corresponding Executing agency be included in the screening range of load-sensitive signal so that the anti-interference ability of variable pump is reinforced；
Under the operative scenario of the corresponding more executing agencies of more pumps, variable pump discharge is overcome preferentially to meet workload lower The problem of executing agency, the source of the load-sensitive signal by changing input value variable pump, so that the flow and pressure of variable pump Power can change in the larger context, to meet the needs of workload higher executing agency.
When at least two hydraulic pump is two, as any technical solution for providing above or hereinafter of the present invention or The optimization of technical solution after any optimization, the control system include: the first hydraulic pump, corresponding first executing agency and first Load-sensitive signal；And second hydraulic pump, corresponding second executing agency and the second load-sensitive signal；The feedback signal Screening module includes: the first control valve 15, can select to export to the signal conversion module the first load-sensitive signal, The second load-sensitive signal or the first load-sensitive signal and pressure in the second load-sensitive signal are larger Person, or the first load-sensitive signal and the second load-sensitive signal is made to be back to fuel tank.
When at least two hydraulic pump and its corresponding executing agency are two, first control valve 15 can Filter out the first load-sensitive signal or the second load-sensitive signal respectively, and can be by setting logical valve, such as shuttle valve is into one Step filters out the first load-sensitive signal and the greater or smaller in the second load-sensitive signal.Meanwhile in order to protect Demonstrate,prove hydraulic system normal aerial drainage function, first control valve 15 further comprise make the first load-sensitive signal with it is described Second load-sensitive signal is back to the working condition of fuel tank.
Based on this, the case where for hydraulic pump and its corresponding executing agency's quantity more than two, can also take similar Thinking be arranged the first control valve 15, making it accordingly has multiple and different working conditions, and makes above-mentioned different work shape State is able to be unlikely to omit multiple executing agencies with certain rule output by the load-sensitive signal of whole executing agencies The load information (load-sensitive signal) of middle part, and retain the working condition of aerial drainage, to guarantee the starting of hydraulic flow path and stop The only safety under state.
Further, it in order to effectively be controlled first control valve 15, is mentioned above or hereinafter as the present invention The optimization of technical solution after any technical solution or any optimization that supply, first control valve 15 are four four-way control valves； The feedback signal screening module includes: the first reversal valve 5-5, a control mouth of first control valve 15 can be had choosing Ground connection is selected to pilot pressure oil sources or fuel tank；And the second reversal valve 5-6, can by first control valve 15 another Control mouth selectively connection to pilot pressure oil sources or fuel tank.
Four of four four-way control valves include 1. quick to signal conversion module output first load Feel signal, 2. to signal conversion module output the second load-sensitive signal, 3. to signal conversion module output The first load-sensitive signal makes first load quick with pressure the greater in the second load-sensitive signal and 4. Sense signal and the second load-sensitive signal are back to fuel tank, these four different working conditions.And four four-way controls Four general rules of valve processed refer to that connection is distinguished to the first load-sensitive signal and institute in two input ports of first control valve 15 The second load-sensitive signal is stated, two delivery outlets distinguish connection to fuel tank and the signal conversion module.
Further, it by the way that the first reversal valve 5-5 and the second reversal valve 5-6 is arranged, may be implemented to first control The working condition of valve 15 is controlled.In the present embodiment, first control valve 15 is by hydraulic drive spool, therefore will be described Selectively connection to pilot pressure oil sources or fuel tank can be realized to first control valve control mouth of first control valve 15 The control of 15 control mouth oil liquid pressures, i.e., by control mouth connection fuel tank to realize pressure release, by control mouth connection pilot pressure oil sources To realize pressurization.
Certainly, to those skilled in the art, the control to first control valve 15 and corresponding cooperation member The selection of device can also take other modes.Such as when first control valve 15 is solenoid valve, control electricity can be passed through The size of magnetic force changes the working condition of first control valve 15.Certainly, the working condition of first control valve 15 can also By rocking bar or handle drives.Concrete condition needs to determine according to the operative scenario of control system provided by the present invention.
Since there are four types of different working conditions for first control valve 15 tool, mentioned above or hereinafter as the present invention The optimization of technical solution, the first reversal valve 5-5 and second reversal valve after any technical solution or any optimization that supply At least one in 5-6 can make first control valve 15 be at least two different operating positions.
For the present embodiment, the first reversal valve 5-5 and the second reversal valve 5-6 can select one using electricity The form of magnetic control, and the aperture by setting reversal valve corresponding to different electric currents makes first control valve 15 to realize The operating position different at least two.
Specifically, first control valve 15 is aerial drainage position under middle position state, make the load-sensitive signal system of input One is back to fuel tank；When the first reversal valve 5-5 obtains electric 550mA, the upper control mouth and fuel tank of first control valve 15 Connection, and its spool has the first aperture, and first control valve 15 moves up one at this time, is in upper two, filters out The greater in the first load-sensitive signal and the second load-sensitive signal, and output this to the signal conversion Module；Further, when the first reversal valve 5-5 obtains electric 800mA, the upper control mouth and fuel tank of first control valve 15 Connection, and its spool has second of aperture, and first control valve 15 continues to move up one at this time, is in upper one, sieve It selects the first load-sensitive signal and exports to signal conversion module；And when the second reversal valve 5-6 obtains electric 550mA, institute The lower control mouth and fuel tank connection of the first control valve 15 are stated, therefrom position moves down one to first control valve 15 at this time, is in down It one, filters out the second load-sensitive signal and exports to signal conversion module.
The numerical value that above-mentioned first reversal valve 5-5 and the second reversal valve 5-6 obtains electric 550mA and 800mA is relative to its model For.Therefore, when the first reversal valve 5-5 and the second reversal valve 5-6 uses the solenoid valve of other models, accordingly Electric current can also change, only need an one of reversal valve to can satisfy first control valve 15 and work at two Switch between state.
The optimization of technical solution, described after any technical solution or any optimization that provide above or hereinafter as the present invention Signal conversion module includes: proportioning valve 9, one of oil inlet connection of the proportioning valve 9 at least two hydraulic pump, can According to the proportionate relationship between the load-sensitive signal received and the spring force of setting, the pressure signal of oil inlet is converted to It is input to the load-sensitive signal of the Ioad-sensing control chamber of the variable pump.
Oil inlet (i.e. input port) connection of the proportioning valve 9 is one of at least two hydraulic pump, by the ratio The transformation of example valve 9, the flow flowed out by the hydraulic pump can be converted into load-sensitive signal, to re-enter To the Ioad-sensing control chamber of variable pump, so that the output to variable pump controls.
Wherein, when the oil inlet of the proportioning valve 9 is connected to variable pump, the load-sensitive that is exported by the proportioning valve 9 Signal is by by the output quantity of variable pump and the load-sensitive signal filtered out co-determination, and variable pump forms defeated to itself at this time Feedback control out, and at the same time variable pump also can carry out flow adjustment according to the state change of different executing agencies.When When oil inlet connection to the constant displacement pump of the proportioning valve 9, the load-sensitive signal exported by the proportioning valve 9 will be filtered out only Load-sensitive signal deciding, the anti-interference ability for being input to the load-sensitive signal of variable pump at this time is stronger, so that variable pump The adaptability of load is reinforced, performance is more stable.
Further, since load-sensitive signal F received by the proportioning valve 91With the spring force F of settingtIt is respectively acting on The left and right control side of the proportioning valve 9, therefore F1With FtBetween proportionate relationship can with the variation of the load-sensitive signal and Variation, the aperture of proportioning valve 9 can also change correspondingly.Based on this, the signal conversion module can be according to the load received Sensitive signal and change itself output to variable pump Ioad-sensing control chamber load-sensitive signal.
Further, the output of the proportioning valve 9 can be adjusted in order to realize at any time, is mentioned above or hereinafter as the present invention The optimization of technical solution after any technical solution or any optimization that supply, the proportional pressure-reducing valve 9 are electric proportional valve, being capable of basis The proportionate relationship between load-sensitive signal, the spring force of setting and the active force of electric proportional valve received, by oil inlet Pressure signal be converted to the load-sensitive signal for being input to the Ioad-sensing control chamber of the variable pump.
The load-sensitive signal F received by the proportioning valve 91With the spring force F of settingtIt is respectively acting on the ratio On the basis of the left and right control side of example valve 9, the directed force F of electric proportional valvedLoad-sensitive signal F can be acted on1It is ipsilateral, The spring force F of setting can be acted ontIt is ipsilateral.Accordingly by adjusting the directed force F of electric proportional valvedI.e. it is comparable directly and The load-sensitive signal that easily comparative example valve 9 is converted continuously is adjusted.
Further, negative in order to also be used as factor to be included in the output parameter for the hydraulic pump being connected with the proportioning valve 9 The conversion of sensitive signal is carried according among, technical side after any technical solution or any optimization that the present invention provides above or hereinafter The optimization of case, the electric proportional valve 9 can further receive the pressure of oil inlet, and according to the load-sensitive signal received, Proportionate relationship between the pressure of the spring force of setting, the active force of electric proportional valve and oil inlet believes the pressure of oil inlet Number be converted to the load-sensitive signal for being input to the Ioad-sensing control chamber of the variable pump.
At this point, the 9 inlet pressure F of proportioning valvepIt can be with load-sensitive signal F1, setting spring force FtAnd electricity The directed force F of proportioning valvedThe left and right control side of the proportioning valve 9 is respectively acting in a manner of side two-by-two.And due to drawing 9 inlet pressure F of proportioning valve is enteredp, so that the proportioning valve 9 can work under the influence of four kinds of active forces in equilibrium state Under, that is, it includes
Fd+Fl=Ft+Fp；
The principle for being simply in equilibrium state to the proportioning valve 9 below is illustrated:
When only with load-sensitive signal F1With the spring force F of settingtWhen, with 9 valve port opening of proportioning valve or spool stroke Variation, spring force FtAlso can change therewith, therefore in the case where rationally setting spring force range, as load-sensitive signal F1 With the spring force F of settingtWhen equal, the state of proportioning valve 9 just no longer changes, and is in equilibrium state at this time.
On its basis, it is further added by the directed force F of electric proportional valved, when can only change the proportioning valve 9 and reaching equilibrium state Valve port opening or spool stroke.Therefore pass through the directed force F of control electric proportional valve at this timedIt can directly adjust by proportioning valve 9 The load-sensitive signal of output.
And work as the inlet pressure F of the proportioning valve 9pAlso the valve port opening of comparative example valve 9 or spool stroke have an impact When, and when oil inlet connection to the variable flow valve of the proportioning valve 9, formation is directed to the variable pump by the proportioning valve 9 Feedback control system.Specifically, the output of the variable flow valve will be right as one of the governing factor of the proportioning valve 9 It exports to the load-sensitive signal of the variable flow valve load-sensitive chamber and has an impact, and then change the output quantity of the variable pump.
It is illustrated so that distortion (such as flow increases suddenly) occurs in the output flow of variable pump as an example below: due to variable Pump is unstable to the performance of executing agency, and when the output of variable pump increases suddenly, a control side of proportioning valve 9 will be therewith By bigger active force, keep the equilibrium state of the proportioning valve 9 mobile to more high spring force and bigger inlet pressure side, It is rebalanced in new state.Under the new state of more high spring force, the proportioning valve 9 is input to the variable pump load-sensitive The load-sensitive signal of chamber will be reduced, to make the flow of the variable pump reduce again, until the flow of the variable pump is extensive The multiple state to before distorting.
Therefore, it is based on inlet pressure Fp, load-sensitive signal F1, setting spring force FtAnd the effect of electric proportional valve Power FdBuilding block of the proportioning valve 9 as signal conversion module, enable to the output of the variable pump can be with whole liquid Demand of the pressure system to flow is adjustable, output performance is stable and to the adaptable of actuator load.
The optimization of technical solution, described after any technical solution or any optimization that provide above or hereinafter as the present invention Control system includes: interflow control module, can selectively control at least two hydraulic pump in an independent way to right The executing agency's fuel feeding answered, or to one of at least two executing agency fuel feeding in a manner of interflow.
At this point, the mode at interflow will include: variable when at least two hydraulic pump includes at least one variable pump Pump to constant displacement pump executing agency fuel feeding, variable pump to variable pump executing agency fuel feeding, constant displacement pump to constant displacement pump executing agency fuel feeding, And constant displacement pump is to variable pump executing agency fuel feeding.
Based on this, when constant displacement pump is to constant displacement pump executing agency fuel feeding or variable pump to variable pump executing agency fuel feeding, though Quantitative, the mutually matched advantage of variable pump can not be so generated, but is to continue with and can retain constant displacement pump stability of flow or variable pump pair The strong feature of workload-adaptability.
And when constant displacement pump executing agency is by flow from variable pump, Constant Pump System is able to solve to executing agency The problem that workload-adaptability is poor, performance is unstable and power consumption is big；And when variable pump executing agency is by from constant displacement pump Flow when, be able to solve variable pump systems when more executing agencies act, due to variable pumpage it is insufficient caused by system Saturated phenomenon makes variable pump systems better adapt to actuator load variation, reduces power loss and energy dissipation, promoted whole Machine performance.
Due at least two hydraulic pump respectively with corresponding executing agency's connection, in order to enable the interflow module Normally to one of any at least two executing agency fuel feeding, any technology provided above or hereinafter as the present invention The optimization of technical solution after scheme or any optimization, the interflow control module include: interflow control valve group, connection to it is described extremely Few two hydraulic pumps, can control the oil circuit connection or disconnection between at least two hydraulic pump.
In order to control effectively to the interflow control valve group, as any technology of the invention provided above or hereinafter The optimization of technical solution after scheme or any optimization, the control valve group include: the second control valve 18, are inserted valve, for controlling Make the oil circuit connection or disconnection between at least two hydraulic pump；And third control valve 17, second control can be controlled The control mouth of valve 18 processed and at least two hydraulic pumps connection, or it is back to fuel tank.
Second control valve 18 can also use the control valve of other forms, such as reversal valve, as long as institute can be controlled It states connection between at least two hydraulic pumps or disconnects.Under the action of third control valve 17, second control valve 18 in the off state, is acted on by the pressure oil of cartridge valve controlled donsole and is in close state, and works as the third control valve 17 When being powered or being opened by other mechanism, the pressure oil of 18 control mouth of the second control valve is back to fuel tank, the pressure of control chamber Zero, at this time under the differential pressure action of at least two hydraulic pumps output hydraulic pressure oil, second control valve 18, which is in, to be opened State makes the multiple hydraulic pump realize interflow.
The fuel feeding side between at least two hydraulic pump and at least two executing agency under the state of interflow To will be determined by the pressure dependence between at least two hydraulic pump between load-sensitive signal.Specifically, ought wherein one When the load-sensitive signal pressure of a hydraulic pump is higher than the load-sensitive signal of another hydraulic pump, held corresponding to the hydraulic pump Row mechanism will executing agency's fuel feeding demand corresponding to another hydraulic pump meets itself under the premise of, receive from another Fuel feeding corresponding to one hydraulic pump.
Further, in order to make the second control valve 18 control mouth oil by enough pressure always in the off state The active force of liquid, as the optimization of technical solution after the present invention any technical solution or any optimization that provide above or hereinafter, The interflow control module includes: shuttle valve 16, is set to 18 connection of the second control valve at least two hydraulic pump Oil circuit, for making one of second control valve 18 and discharge highest at least two hydraulic pump of oil pressure connection.
Typically, the difference in flow between the output flow of hydraulic pump and load-sensitive signal is away from larger, in order to make by institute The load-sensitive signal for stating signal conversion module output can adapt to load-sensitive chamber in hydraulic pump, as the present invention above or The optimization of technical solution after any technical solution or any optimization that provide hereinafter, the control system includes: constant flow module, connection The delivery outlet for passing to the signal conversion module, for making the load-sensitive for the Ioad-sensing control chamber for being input to the variable pump Signal is back to fuel tank with the flow part that sets.
Based on above-mentioned constant flow module, the signal conversion module is input to the negative of the Ioad-sensing control chamber of the variable pump The vent flow for carrying sensitive signal will be kept fixed, therefore the reduction that the load-sensitive signal at any moment is equivalent, only can be more It is adapted to the flow of load-sensitive signal required for hydraulic pump, is generated without the precision to the load-sensitive signal exported It influences.
The optimization of technical solution, described after any technical solution or any optimization that provide above or hereinafter as the present invention Constant flow module includes: the first overflow valve 10, is set between the signal conversion module and fuel tank；And first throttle valve, with The overflow valve 10 is in parallel, and is set between the signal conversion module and fuel tank.
Since the first throttle valve is in normally open, flow will will receive the hydraulic of the first throttle valve both ends It influences, therefore first overflow valve 10 by being arranged in parallel, so that the first throttle valve pressure at both sides is in conjunction always It manages in range, and then the constant flow module is enable to be back to fuel tank by the first throttle valve with constant flow always.
For general pump hydraulic system, as any technical solution of the invention provided above or hereinafter or appoint The optimization of technical solution after one optimization, the control system includes: constant displacement pump P1, corresponding constant displacement pump executing agency and constant displacement pump Load-sensitive signal；And variable pump P2, corresponding variable pump executing agency and variable pump load-sensitive signal.
The optimization of technical solution, described after any technical solution or any optimization that provide above or hereinafter as the present invention Control system includes: pressure compensator 11, is set to the oil circuit of the constant displacement pump P1 and fuel tank, and a control mouth connection is extremely The oil inlet of the pressure compensator 11, another control mouth connection to the constant displacement pump load-sensitive signal or the variable pump Load-sensitive signal.
By being arranged the pressure compensator 11, the constant displacement pump can in no constant displacement pump load-sensitive signal or When the variable pump load-sensitive signal, the pressure compensator 11 is opened by the constant displacement pump and carries out off-load；And occurring When stating constant displacement pump load-sensitive signal or the variable pump load-sensitive signal, the constant displacement pump no longer passes through the pressure compensation Device 11 carries out off-load, but starts fuel feeding to executing agency corresponding to constant displacement pump, or by the interflow module to variable pump Corresponding execution system fuel feeding.
Further, the pressure compensator 11 can be set to slide valve.At this point, the structure type by slide valve can make The pressure compensator 11 has any intermediate position, so that the constant displacement pump be made to put down in leak condition and working condition Sliding cutting changes, and does not generate biggish impact to the executing agency of its oil supply.
It is similar with the function of the pressure compensator 11, to enable the safe aerial drainage of the variable pump, before the present invention The optimization of technical solution after text or any technical solution or any optimization that provide hereinafter, the control system includes: that definite value subtracts Pressure valve 2 can distinguish the pilot pressure oil sources under the action of spring force of setting and the pilot pressure oil sources pressure Connection is to the variable pump P2 or the fuel tank；Second throttle is set to the fixed pressure reducing valve 2 and variable pump P2's Oil circuit；And the 4th overflow valve 3, it is set to the oil circuit of the pilot pressure oil sources and the fuel tank, it can be according to the pressure of setting Power makes the pilot pressure oil sources be back to fuel tank.
The optimization of technical solution, described after any technical solution or any optimization that provide above or hereinafter as the present invention Control system includes: interflow control module, can selectively control at least two hydraulic pump in an independent way to right The executing agency's fuel feeding answered, or to one of at least two executing agency fuel feeding in a manner of interflow.Based on this, the present invention is also Provide a kind of work connection, including more hydraulic pump multiplex control systems as previously described.
Work connection includes signal conversion module, signal screening module and reasonable control module, be can be used as Between module and be set in overall work connection, to realize to multiple hydraulic pumps, multiple executing agencies and multiple loads The coupling of sensitive signal controls.The work connection can be integrated in the same valve body assembly, to improve its globality.
Invention further provides a kind of engineering machinery, including the compound control of more hydraulic pumps as described in any one above System processed.Certainly, more hydraulic pumps provided by the present invention, which meet control system, can also be not limited to engineering machinery field, and wide It is general to be applied to other relevant industrial circles.
Based on the above-mentioned technical proposal, the embodiment of the present invention is by signal conversion module, selectively according to described at least two The load-sensitive signal of the corresponding executing agency of a hydraulic pump, to the Ioad-sensing control chamber for being input to the variable pump Load-sensitive signal is converted, so that the movement between multiple executing agencies in double pump oil supply system is more coordinated.
With reference to the accompanying drawing the interflow control module in 1 pair of technical solution provided by the invention, signal screening module and Signal conversion module is illustrated in more detail:
(1) collaborate control module
Effect is the effect of Constant Pump System and variable pump systems interflow.
Particular technique route is Constant Pump System and variable pump systems pressure oil under 17 unpowered state of solenoid electric valve High-voltage signal oil is filtered out by shuttle valve 16 and 18 control chamber of inserted valve is applied to by solenoid electric valve 17, and inserted valve 18 is being pressed It is in close state under the action of difference.After solenoid electric valve 17 is powered, 18 control chamber pressure oil of inserted valve returns T, control chamber pressure Power is zero, and inserted valve 18 is used cooperatively under differential pressure action with the first control valve 15, realizes constant displacement pump and variable pump difference operating condition Under flow control.
(2) signal screening module
Effect realizes different LS signal on-off functions to lead to different electric currents by different solenoid directional control valves, and it is fixed to realize Amount pumping system, variable pump systems work independently and collaborate control.
Particular technique route are as follows:
A) when Constant Pump System and variable pump systems executing agency are movement: the commutation of the first reversal valve 5-5 and second Valve 5-6 not it is electric, the first control valve 15 is in lower two working position, and Constant Pump System LS signal, variable pump LS signal return T, constant current Module (throttling overflow valve 10) is in working position under the effect of P mouthfuls of pressure, spring force and constant displacement pump load-sensitive chamber power, quantitative Pump discharge returns T by pressure compensator 11, and variable pump is in minimum injection rate, solenoid directional control valve 17 not it is electric, inserted valve 18 is not beaten It opens, quantitative pump discharge and variable pump discharge are not collaborated；
B) when Constant Pump System and variable pump systems executing agency separately act: the second reversal valve 5-6 obtains electric (550mA), 15 next bit of the first control valve are working position, and 15 output variable pumping system LS signal of the first control valve to signal is converted The control chamber of module 9 realizes the control to variable pump output flow, constant displacement pump by signal conversion module 9 and constant flow module 10 System is by the independent fuel feeding of constant displacement pump.Therefore, the first control valve 15 can realize Constant Pump System and variable pump systems in next bit It is independent to work together, solenoid directional control valve 17 not it is electric, inserted valve 18 is not switched on, and quantifies pump discharge and variable pump discharge is not collaborated；
C) flow needed for Constant Pump System or variable pump systems executing agency is larger, when being more than original system metered flow, Then need to collaborate work: the first reversal valve 5-5 is obtained electric (550mA), and the first control valve 15 is in lower three working position, the first control valve 1515 output Constant Pump Systems and the LS signal of variable pump systems after comparison are realized through signal conversion module 9 and constant flow module 10 Control to variable pump output flow, solenoid directional control valve 17 obtain electric, the opening of inserted valve 18, quantitative pump discharge and the conjunction of variable pump discharge Stream.At this point, the flow of variable pump output is except satisfaction change when Constant Pump System LS signal pressure is higher than variable pump systems LS signal Measure the flow that pumping system needs, moreover it is possible to use extra flow by interflow module supply Constant Pump System, it is fixed to be promoted with this Measure the work speed of pumping system executing agency；When variable pump systems LS signal is higher than Constant Pump System LS signal, variable pump system The flow of system output can only supply variable pump systems, quantify pump discharge on the basis of meeting the needs of Constant Pump System, then will Extra flow passes through 9 oil return box of feedback signal conversion module, Huo Zhe when variable pump discharge meets variable pump systems demand The flow of variable pump output is not able to satisfy (variable pump systems saturation) when variable pump systems need, is variable pump by inserted valve 18 System supplies itself extra flow, realizes the promotion of mechanical efficiency.Therefore, the first control valve 15 may be implemented fixed at lower three The interflow for measuring pumping system and variable pump systems controls, and in the course of work, interflow module control valve will be in energized state；
D) when variable pump systems are not necessarily to flow, variable pump systems flow is supplied into Constant Pump System, increases constant displacement pump system The work speed of system executing agency: the first reversal valve 5-5 is obtained electric (800mA), and the first control valve 15 is in lower four working position, described The LS signal that first control valve 15 exports Constant Pump System is realized through signal conversion module 9 and constant flow module 10 exports variable pump The control of flow, solenoid directional control valve 17 obtain electric, the opening of inserted valve 18, quantitative pump discharge and variable pump discharge interflow.At this point, variable The flow of pump output supplies Constant Pump System by inserted valve 18 and uses, to realize the promotion of Constant Pump System efficiency, variable pump Constant Pump System flow is supplied with removing behind constant displacement pump interflow, excess traffic passes through flow control valve oil return box.
(3) signal conversion module
The pressure signal of first control valve 15 output acts on the left end of signal conversion module 9, and signal conversion module is in LS Signal Fl is screened, electric proportional pressure-reducing valve directed force F d, spring Ft and inlet pressure Fp effect are lower in equilibrium state, pass through ratio The restriction of example valve 9 exports corresponding pressure signal and acts on variable pump through constant flow module 10, realizes the control to variable pumpage System.By adjustment effect, the restriction of the active force comparative example valve 9 of electromagnet is adjusted above signal conversion module, is realized The step-less adjustment of output pressure, and then the control signal of needle difference pressure difference grade is generated to the load-sensitive chamber of variable pump, it realizes From the matching with different differential pressure requirements variable pumps, the use scope of the valve is improved.
Various states locating for the control system of 1 pair of technical solution provided by the invention carry out further with reference to the accompanying drawing Description:
(1) unloading condition: 15 spool of the first control valve is located at middle position, and Constant Pump System and variable system LS be not to variable pump Output control signal.When quantitative system is in position in flow direction control valve 4-3, constant displacement pump is by opening 11 drain charges；In variable system Variable pump makes flow direction control valve 4-1 or flow direction control valve 4-2 be in middle position, this variations per hour by pressure compensator 7-1 and 7-2 Pump under minimum swash angle, be in flow minimum oil condition, solenoid directional control valve 17 not it is electric, inserted valve 18 is not switched on, constant displacement pump Flow and variable pump discharge are not collaborated.
(2) constant displacement pump and variable pump work respectively: the second reversal valve 5-6 obtain it is electric, under the spool of the first control valve 15 is located at Position, variable pump systems export control signal to variable pump.Variable pump gives variable system fuel feeding, and variable pump passes through pressure compensator 7- When 1 and 7-2, flow direction control valve 4-1 or flow direction control valve 4-2 are in middle position, variable pump is minimum in flow under minimum swash angle Oil condition.When solenoid directional control valve valve 5-4 or 5-2 obtain electric, when flow direction control valve 4-1 or flow direction control valve 4-2 are in the next, make For variable pump to A mouthfuls of output pressures, B mouthfuls lead to T；When solenoid directional control valve valve 5-1 or 5-3 obtain electric, flow direction control valve 4-1 or traffic organising When valve 4-2 is in upper, make variable pump to B mouthfuls of output pressures, A mouthfuls of logical T, the LS signal control variable pump of load sensing multi-way valve Pivot angle.At this point, constant displacement pump specified rate system fuel feeding, flow direction control valve 4-3 is in bottom, makes constant displacement pump to A mouthfuls of output pressures, B mouthfuls of logical T；When the electromagnet of solenoid directional control valve 5-7 obtain it is electric, flow direction control valve 4-3 be in it is upper, press constant displacement pump to B mouthfuls of outputs Power, A mouthfuls of logical T.
(3) variable pump specified rate system fuel feeding: the first reversal valve 5-5 obtain it is electric, 15 spool of the first control valve be located at upper first Position, solenoid directional control valve 17 must be electric, and 18 control chamber of inserted valve leads to fuel tank, and spool is opened under constant displacement pump and variable pump collective effect, Constant displacement pump controls signal to variable pump output LS, and variable pump is to quantitative system repairing.
(4) collaborate state: solenoid directional control valve valve 5-5 obtains electric, and 15 spool of signal screening module is located at upper second, and electromagnetism changes Must be electric to valve 17,18 control chamber of inserted valve leads to fuel tank, and spool is opened under constant displacement pump and variable pump collective effect, forms variable system The interflow of system and quantitative system.At this point, constant displacement pump controls signal to variable pump output LS when quantitative system control oil pressure is high, become Amount is pumped to quantitative system repairing；Variable system control oil pressure it is high when, variable system pump control LS controls signal, and constant displacement pump is to variable System repairing.
Based on the above-mentioned technical proposal, following technical effect at least may be implemented in the application:
(1) independence and complex controll that Constant Pump System and variable pump systems can be realized according to actual condition, can overcome The problems such as Constant Pump System is poor to workload-adaptability, performance is unstable, power loss is big and variable pump systems are executing machine more The system saturated phenomenon due to caused by variable pumpage deficiency, makes system better adapt to load variation, reduces when structure acts Power loss and energy dissipation promote overall performance.
(2) according to demand of the system to flow under different operating conditions, different control signals is exported to variable pump load-sensitive Control chamber, and then different flows is exported to meet system requirements.
(3) system feedback signal is converted, the variable pump of different displacements, different pressure levels can be met It needs, in the case where not changing multi-way valve design parameter, can be matched with more variable pumps, expand multi-way valve Application range.
(4) speed regulation original part of the overflow valve cooperation throttle valve as system, passes through flow regulating valve opening degree or overflow valve overflow Pressure adjusts the pressure of entering variable pump load sensitive cavity, ideal control pressure can be established in system work process, again The automatic deloading when shutting down prevents feedback oil circuit from building the pressure and causes starting with pressure, damages Hydraulic Elements.
(5) double pump work can be better to control and act more good composite performance by the commutation of control converging valve And the performances such as fine motion of a motion action.
Any technical solution disclosed in aforementioned present invention unless otherwise stated, if it discloses numberical range, Disclosed numberical range is preferred numberical range, and any it should be appreciated by those skilled in the art preferred numberical ranges The only obvious or representative numerical value of technical effect in many enforceable numerical value.It, can not since numerical value is more Exhaustion, so the present invention just discloses technical solution of the component values to illustrate the present invention, also, the above-mentioned numerical value enumerated is not The limitation to the invention protection scope should be constituted.
If the words such as " first ", " second " are used herein come if limiting components, those skilled in the art are answered This knows: the use of " first ", " second " is intended merely to facilitate in description and is distinguished components as not having Stated otherwise Outside, above-mentioned word has no special meaning.
Meanwhile if aforementioned present invention discloses or relates to the components or structural member of connection fastened to each other, except another There is statement outer, is fixedly connected it is to be understood that connection (such as using bolt or screw connection) can be removedly fixed, it can also be with Understand are as follows: non-removable to be fixedly connected with (such as riveting, welding), certainly, connection fastened to each other or integral structure (such as manufacturing using casting technique is integrally formed) is replaced (obviously can not be using except integrally formed technique).
In addition, for indicating the art of positional relationship or shape applied in any technical solution disclosed in aforementioned present invention Its meaning includes approximate with its, similar or close state or shape to language unless otherwise stated.Either component provided by the invention Either being assembled by multiple individual component parts, or the separate part that integrally formed technique manufactures.
In the description of the present invention if used term " center ", " longitudinal direction ", " transverse direction ", "front", "rear", " left side ", " right side ", "vertical", "horizontal", "top", "bottom", "inner", "outside" etc., then the orientation or positional relationship of above-mentioned term instruction is base In orientation or positional relationship shown in the drawings, it is merely for convenience of description of the present invention and simplification of the description, rather than indication or suggestion Signified equipment, mechanism, component or element must have a particular orientation, be constructed and operated in a specific orientation, therefore cannot It is interpreted as limiting the scope of the invention.
Finally it should be noted that: the above embodiments are merely illustrative of the technical scheme of the present invention and are not intended to be limiting thereof；To the greatest extent The present invention is described in detail with reference to preferred embodiments for pipe, it should be understood by those ordinary skilled in the art that: still It can modify to a specific embodiment of the invention or some technical features can be equivalently replaced；Without departing from this hair The spirit of bright technical solution should all cover within the scope of the technical scheme claimed by the invention.

Claims (20)

1. a kind of more hydraulic pump multiplex control systems characterized by comprising
At least two hydraulic pumps, including at least one variable pump；
At least two executing agencies, respectively connection corresponding at least two hydraulic pump；And
Signal conversion module, it is quick for the load selectively according to the corresponding executing agency of at least two hydraulic pump Feel signal, the load-sensitive signal for the Ioad-sensing control chamber for being input to the variable pump is converted.
2. control system according to claim 1, which is characterized in that the control system includes:
Signal screening module is set between the signal conversion module and the load-sensitive signal of the executing agency, is used for Load-sensitive signal described in Rules Filtering with setting, and the selection result is exported to the signal conversion module.
3. control system according to claim 2, which is characterized in that the control system includes:
First hydraulic pump, corresponding first executing agency and the first load-sensitive signal；And
Second hydraulic pump, corresponding second executing agency and the second load-sensitive signal；
The feedback signal screening module includes:
First control valve (15) can select to export the first load-sensitive signal, described the to the signal conversion module Pressure the greater in two load-sensitive signals or the first load-sensitive signal and the second load-sensitive signal, or make The first load-sensitive signal and the second load-sensitive signal are back to fuel tank.
4. control system according to claim 3, which is characterized in that first control valve (15) is four four-way controls Valve；
The feedback signal screening module includes:
First reversal valve (5-5), can by a control mouth of first control valve (15) selectively connection to first pilot Power oil sources or fuel tank；And
Second reversal valve (5-6), can by another control mouth of first control valve (15) selectively connection to guide Pressure oil-source or fuel tank.
5. control system according to claim 4, which is characterized in that first reversal valve (5-5) and described second is changed At least one can make first control valve (15) be at least two different operating positions in valve (5-6).
6. control system according to claim 1, which is characterized in that the signal conversion module includes:
Proportioning valve (9), one of oil inlet connection of the proportioning valve (9) at least two hydraulic pump, can be according to reception The pressure signal of oil inlet is converted to and is input to institute by the proportionate relationship between the load-sensitive signal arrived and the spring force of setting State the load-sensitive signal of the Ioad-sensing control chamber of variable pump.
7. control system according to claim 6, which is characterized in that the proportional pressure-reducing valve (9) is electric proportional valve, can It, will be into according to the proportionate relationship between the load-sensitive signal, the spring force of setting and the active force of electric proportional valve received The pressure signal of hydraulic fluid port is converted to the load-sensitive signal for being input to the Ioad-sensing control chamber of the variable pump.
8. control system according to claim 7, which is characterized in that the electric proportional valve (9) can further receive into The pressure of hydraulic fluid port, and according to load-sensitive signal, the spring force of setting, the active force of electric proportional valve and the oil inlet received Pressure between proportionate relationship, the pressure signal of oil inlet is converted to the Ioad-sensing control chamber for being input to the variable pump Load-sensitive signal.
9. control system according to claim 1, which is characterized in that the control system includes:
Collaborate control module, can selectively control at least two hydraulic pump in an independent way to corresponding execution machine Structure fuel feeding, or to one of at least two executing agency fuel feeding in a manner of interflow.
10. control system according to claim 9, which is characterized in that the interflow control module includes:
Collaborate control valve group, connection at least two hydraulic pump can control the oil between at least two hydraulic pump Road connection or disconnection.
11. control system according to claim 10, which is characterized in that the control valve group includes:
Second control valve (18) is inserted valve, for controlling oil circuit connection or disconnection between at least two hydraulic pump；With And
Third control valve (17), the control mouth and at least two hydraulic pump that can control second control valve (18) join It is logical, or it is back to fuel tank.
12. control system according to claim 10, which is characterized in that the interflow control module includes:
Shuttle valve (16) is set to the oil circuit of the second control valve (18) connection at least two hydraulic pump, for making State one of the second control valve (18) and discharge highest at least two hydraulic pump of oil pressure connection.
13. control system according to claim 1, which is characterized in that the control system includes:
Constant flow module, the delivery outlet of connection to the signal conversion module, the load-sensitive for making to be input to the variable pump The load-sensitive signal of control chamber is back to fuel tank with the flow part that sets.
14. control system according to claim 13, which is characterized in that the constant flow module includes:
First overflow valve (10), is set between the signal conversion module and fuel tank；And
First throttle valve, it is in parallel with the overflow valve (10), and be set between the signal conversion module and fuel tank.
15. control system according to claim 1, which is characterized in that the control system includes:
Constant displacement pump (P1), corresponding constant displacement pump executing agency and constant displacement pump load-sensitive signal；And
Variable pump (P2), corresponding variable pump executing agency and variable pump load-sensitive signal.
16. control system according to claim 15, which is characterized in that the control system includes:
Pressure compensator (11), is set to the oil circuit of the constant displacement pump (P1) and fuel tank, and a control mouth connection is to described The oil inlet of pressure compensator (11), another control mouth connection to the constant displacement pump load-sensitive signal or the variable pump are negative Carry sensitive signal.
17. control system according to claim 15, which is characterized in that the control system includes:
Fixed pressure reducing valve (2), can be under the action of the spring force of setting and the pilot pressure oil sources pressure, by the guide Pressure oil-source distinguishes connection to the variable pump (P2) or the fuel tank；
Second throttle is set to the oil circuit of the fixed pressure reducing valve (2) Yu the variable pump (P2)；And
4th overflow valve (3) is set to the oil circuit of the pilot pressure oil sources and the fuel tank, can be made according to the pressure of setting The pilot pressure oil sources is back to fuel tank.
18. control system according to claim 2, which is characterized in that the control system includes:
Collaborate control module, can selectively control at least two hydraulic pump in an independent way to corresponding execution machine Structure fuel feeding, or to one of at least two executing agency fuel feeding in a manner of interflow.
19. a kind of work connection, which is characterized in that including more hydraulic pump multiplex control systems as claimed in claim 18.
20. a kind of engineering machinery, which is characterized in that compound including more hydraulic pumps as described in claim 1~18 any one Control system.
CN201910019072.3A 2019-01-09 2019-01-09 Multi-hydraulic-pump composite control system, working coupler and engineering machinery Active CN109519428B (en)

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN113007157A (en) * 2021-03-03 2021-06-22 中联重科股份有限公司 Load-sensitive multi-way valve, boom hydraulic control system and concrete pump truck
CN113464514A (en) * 2021-07-30 2021-10-01 湖南三一中型起重机械有限公司 Integrated electric control multi-way valve and crane

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103047207A (en) * 2012-12-24 2013-04-17 中联重科股份有限公司 Flow dividing and collecting valve bank, hydraulic system, load sensitive type hydraulic system and engineering machine
CN103291674A (en) * 2013-05-31 2013-09-11 武汉船用机械有限责任公司 Hydraulic lifting control system
CN103388598A (en) * 2013-08-06 2013-11-13 中联重科股份有限公司 Lazy arm telescopic mechanism and hydraulic control system, hydraulic control method and crane thereof
CN103671336A (en) * 2013-12-12 2014-03-26 中联重科股份有限公司 Load-sensitive hydraulic system and power matching control method, device and system
CN105570220A (en) * 2014-10-17 2016-05-11 徐工集团工程机械股份有限公司 Multiway valve and hydraulic flow sharing system
CN208123138U (en) * 2017-09-21 2018-11-20 博世力士乐（北京）液压有限公司 Hydraulic control system and corresponding mobile working equipment

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103047207A (en) * 2012-12-24 2013-04-17 中联重科股份有限公司 Flow dividing and collecting valve bank, hydraulic system, load sensitive type hydraulic system and engineering machine
CN103291674A (en) * 2013-05-31 2013-09-11 武汉船用机械有限责任公司 Hydraulic lifting control system
CN103388598A (en) * 2013-08-06 2013-11-13 中联重科股份有限公司 Lazy arm telescopic mechanism and hydraulic control system, hydraulic control method and crane thereof
CN103671336A (en) * 2013-12-12 2014-03-26 中联重科股份有限公司 Load-sensitive hydraulic system and power matching control method, device and system
CN105570220A (en) * 2014-10-17 2016-05-11 徐工集团工程机械股份有限公司 Multiway valve and hydraulic flow sharing system
CN208123138U (en) * 2017-09-21 2018-11-20 博世力士乐（北京）液压有限公司 Hydraulic control system and corresponding mobile working equipment

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN113007157A (en) * 2021-03-03 2021-06-22 中联重科股份有限公司 Load-sensitive multi-way valve, boom hydraulic control system and concrete pump truck
CN113464514A (en) * 2021-07-30 2021-10-01 湖南三一中型起重机械有限公司 Integrated electric control multi-way valve and crane

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