CN104481942A - Hydraulic device with single pump and double actuators - Google Patents
Hydraulic device with single pump and double actuators Download PDFInfo
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- CN104481942A CN104481942A CN201410733607.0A CN201410733607A CN104481942A CN 104481942 A CN104481942 A CN 104481942A CN 201410733607 A CN201410733607 A CN 201410733607A CN 104481942 A CN104481942 A CN 104481942A
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- 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
- F15B11/08—Servomotor systems without provision for follow-up action; Circuits therefor with only one servomotor
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Abstract
The invention discloses a hydraulic device with a single pump and double actuators and relates to quantitative pump load-sensitive hydraulic devices. The hydraulic device comprises a drive motor, a quantitative pump, a first driving oil cylinder, a second driving oil cylinder, a first power generator, a second power generator, a first power generator controller, a second power generator controller, an inverter, a first hydraulic motor, a second hydraulic motor, a first proportional direction valve, a second proportional direction valve, a first shuttle valve, a second shuttle valve, a third shuttle valve, a pressure compensation valve, a first pressure difference sensor, a second pressure difference sensor, a programming controller and the like. The hydraulic motors and the power generators are adopted to serve as adjustment units for front-rear pressure difference of throttling valve ports of the proportional direction valves, throttling loss traditionally consumed at valve ports of fixed-differential reducing valves is converted into electric energy which is stored in an electricity storage unit, and the defect that a lot of energy is consumed on the valve ports of the fixed-differential reducing valves of the actuators low in operation pressure when different actuators are large in operation pressure difference is overcome.
Description
Technical field
The present invention relates to a kind of hydraulic pressure installation of metering pump load-sensitive.
Background technique
Existing metering pump load sensitive system is mainly through the load pressure maximum of multiple final controlling element in shuttle valve acquisition system, and act on the pressure compensator of metering pump outlet, make the outlet pressure of metering pump only be greater than certain less pressure reduction than load pressure maximum, realize the Dynamic Matching of the load pressure maximum needed for metering pump delivery pressure and system.A structure for the hydraulic pressure installation of the two final controlling element of typical load-sensitive type list pump, as shown in Figure 1.The rotating shaft of drive motor 1 is coaxially connected with the main shaft of metering pump 2.Import 201 connected tank 20 of metering pump 2, outlet 202 point of three tunnel of metering pump 2: the first via connects the filler opening 1001 of pressure compensator 10; Second tunnel meets the filler opening 11P of the first Fixed differential reducing valve 11; 3rd tunnel connects the filler opening 12 of the second Fixed differential reducing valve 12.Oil outlet 1002 connected tank 20 of pressure compensator 10.
The filler opening 4P of the first proportional reversing valve 4 is connected with the outlet 1101 of the first Fixed differential reducing valve 11, the oil outlet 4T connected tank 20 of the first proportional reversing valve 4.First actuator port 4A of the first proportional reversing valve 4 drives the rodless cavity 301 of oil cylinder 3 to be connected with the first filler opening 5A1, first of the first shuttle valve 5 respectively, and the second actuator port 4B of the first proportional reversing valve 4 drives the rod chamber 302 of oil cylinder 3 to be connected with the second filler opening 5A2, first of the first shuttle valve 5 respectively.First driving oil cylinder 3 and the first proportional reversing valve 4 form the first final controlling element in this hydraulic system, and the first shuttle valve 5 is detection units of this first final controlling element induced pressure.
The filler opening 7P of the second proportional reversing valve 7 is connected with the outlet 1201 of the second Fixed differential reducing valve 12, the oil outlet 7T connected tank 20 of the second proportional reversing valve 7.First actuator port 7A of the second proportional reversing valve 7 drives the rodless cavity 601 of oil cylinder 6 to be connected with the first filler opening 8A1, second of the second shuttle valve 8 respectively, and the second working oil 7B of the second proportional reversing valve 7 drives the rod chamber 602 of oil cylinder 6 to be connected with the second filler opening 8A2, second of the second shuttle valve 8 respectively.Second driving oil cylinder 6 and the second proportional reversing valve 7 form the second final controlling element in this hydraulic system, and the second shuttle valve 8 is detection units of this second final controlling element induced pressure.
First filler opening 9A1 of the 3rd shuttle valve 9 is connected with the control port 11L of the spring chamber of the first Fixed differential reducing valve 11 with the oil outlet 503 of the first shuttle valve 5 respectively, second filler opening 9A2 of the 3rd shuttle valve 9 is connected with the control port 12L of the spring chamber of the second Fixed differential reducing valve 12 with the oil outlet 803 of the second shuttle valve 8 respectively, and the oil outlet 903 of the 3rd shuttle valve 9 is connected with the control port 1003 of the spring chamber of pressure compensator 10.3rd shuttle valve 9 is detection units of two final controlling element load pressure maximums.
The hydraulic pressure installation of the two final controlling element of this single pump is operationally: drive motor 1 drives metering pump 2 to be extracted out by the hydraulic oil in fuel tank 20, provides this working pressure that two final controlling element need by two Fixed differential reducing valves respectively to two final controlling element fuel feeding; First driving oil cylinder 3 and the first proportional reversing valve 4 form the first final controlling element in this hydraulic pressure installation; Two control valve ports 4K1,4K2 of first proportional reversing valve 4 are operated, the hydraulic oil that metering pump 2 can be made to supply the first proportional reversing valve 4 filler opening 4P by the first Fixed differential reducing valve 11 enters the rodless cavity 301 of the first driving oil cylinder 3 by its first actuator port 4A, meanwhile, first oily the second actuator port 3B by the first proportional reversing valve 3 and oil outlet 3T of original section hydraulic in oil cylinder 3 rod chamber 302 is driven to return fuel tank 20; Or the hydraulic oil making metering pump 2 supply the first proportional reversing valve 4 filler opening 4P by the first Fixed differential reducing valve 4 enters the rod chamber 302 of the first driving oil cylinder 3 by its first actuator port 4B, meanwhile, first oily the first actuator port 4A by the first proportional reversing valve 4 and oil outlet 4T of original section hydraulic in oil cylinder 3 rodless cavity 301 is driven to return fuel tank 20; Thus change the volume ratio that first drives rodless cavity 301 and rod chamber 302 in oil cylinder 3, make the piston 303 in the first driving oil cylinder 3 do axial movement.
Second driving oil cylinder 6 and the second proportional reversing valve 7 form the second final controlling element in this hydraulic pressure installation; Two control valve ports 7K1,7K2 of second proportional reversing valve 7 are operated, the hydraulic oil that metering pump 2 can be made to supply the second proportional reversing valve 7 filler opening 7P by the second Fixed differential reducing valve 12 enters the rodless cavity 601 of the second driving oil cylinder 6 by its first actuator port 7A, meanwhile, second oily the second actuator port 7B by the second proportional reversing valve 7 and oil outlet 7T of original section hydraulic in oil cylinder 6 rod chamber 602 is driven to return fuel tank 20; Or the hydraulic oil making metering pump 2 supply the second proportional reversing valve 7 filler opening 7P by the second Fixed differential reducing valve 12 enters the rod chamber 602 of the second driving oil cylinder 6 by its second actuator port 7B, meanwhile, second oily the first actuator port 7A by the second proportional reversing valve 7 and oil outlet 7T of original section hydraulic in oil cylinder 6 rodless cavity 601 is driven to return fuel tank 20; Thus change the volume ratio that second drives rodless cavity 601 and rod chamber 602 in oil cylinder 6, make the piston 603 in the second driving oil cylinder 6 do axial movement.
Drive in oil cylinder 3 and the second process driving oil cylinder 6 to work first, first shuttle valve 5 dynamically detects the induced pressure that the first driving oil cylinder 3 is born, and by its oil outlet 503, this induced pressure is passed to the control port 11L of the spring chamber of the first Fixed differential reducing valve 11 and the first filler opening 9A1 of the 3rd shuttle valve 9; First Fixed differential reducing valve 11 is subject to the control of this induced pressure, makes it export 1101 with the filler opening 4P supply hydraulic oil of suitable flow to the first proportional reversing valve 4.Second shuttle valve 8 dynamically detects the induced pressure that the second driving oil cylinder 6 is born, and by its oil outlet 803, this induced pressure is passed to the control port 12L of the spring chamber of the second Fixed differential reducing valve 12 and the second filler opening 9A2 of the 3rd shuttle valve 9; Second Fixed differential reducing valve 12 is subject to the control of the second driving oil cylinder 6 induced pressure, makes it export 1201 with the filler opening 7P supply hydraulic oil of suitable flow to the second proportional reversing valve 7.3rd shuttle valve 9 obtains the induced pressure of the first driving oil cylinder 3 and the induced pressure of the second driving oil cylinder 6, and get wherein the grater as the current required load pressure maximum pmax of system, this load pressure maximum pmax is acted on the control port 1003 of the spring chamber of pressure compensator 10 by the oil outlet 903 of the 3rd shuttle valve 9, the large pressure reduction △ p1 preset by its spring of this load pressure maximum of pressure ratio pmax due to the filler opening 1001 of pressure-compensated valve 10, so the outlet pressure of metering pump 2 oil outlet 202 only certain less pressure reduction △ p1 larger than system present load pressure maximum pmax, achieve the Dynamic Matching of the load pressure maximum needed for metering pump 2 delivery pressure and system.
But, in this plant running, working pressure needed for different final controlling element is different, the outlet pressure of metering pump 2 is determined by maximum load pressure, there is pressure reduction in the outlet pressure of the working pressure needed for that final controlling element that working pressure is less and metering pump 2, must by the pressure reduction of the valve port balance those of the Fixed differential reducing valve of less that final controlling element of working pressure.Therefore its essence is the balance being realized pressure difference by throttling loss, causes the capacity usage ratio of metering pump load sensitive system still not high, especially when the working pressure difference of different final controlling element is larger.
Summary of the invention
The present invention aims to provide the hydraulic pressure installation of the two final controlling element of a kind of single pump, and it can energy between less that final controlling element of recovery operation pressure and the outlet pressure of metering pump 2 corresponding to pressure reduction, improves capacity usage ratio.
Technological scheme of the present invention is: the hydraulic pressure installation of the two final controlling element of a kind of single pump, and wherein, drive motor is coaxially connected with metering pump; The import connected tank of metering pump, quantitative delivery side of pump connects the filler opening of pressure compensator; The oil outlet connected tank of pressure compensator; The oil outlet connected tank of the first proportional reversing valve, first actuator port of the first proportional reversing valve connects the first filler opening of the first shuttle valve, the rodless cavity of the first driving oil cylinder respectively, and the second actuator port of the first proportional reversing valve connects the rod chamber that the second filler opening of the first shuttle valve, first drives oil cylinder respectively; The oil outlet connected tank of the second proportional reversing valve, first actuator port of the second proportional reversing valve connects the first filler opening of the second shuttle valve, the rodless cavity of the second driving oil cylinder respectively, and the second actuator port of the second proportional reversing valve connects the rod chamber that the second filler opening of the second shuttle valve, second drives oil cylinder respectively; First filler opening of the 3rd shuttle valve connects the oil outlet of the first shuttle valve, and the second filler opening of the 3rd shuttle valve connects the oil outlet of the second shuttle valve, and the oil outlet of the 3rd shuttle valve connects the control port of the spring chamber of pressure compensator; It also has the first oil hydraulic motor, the first generator, the first engine controller, the second oil hydraulic motor, the second generator, the second engine controller, programming controller, electricity storage element, inverter, the first differential pressure pickup and the second differential pressure pickup; Quantitative delivery side of pump connects the filler opening of the first oil hydraulic motor and the filler opening of the second oil hydraulic motor respectively; The filler opening of the first proportional reversing valve connects the outlet of the first oil hydraulic motor and the first filler opening of the first differential pressure pickup respectively; The filler opening of the second proportional reversing valve connects the outlet of the second oil hydraulic motor and the first filler opening of the second differential pressure pickup respectively; Electricity storage element is connected with the DC supply input mouth of inverter, the DC electrical source port of the first engine controller, the DC electrical source port of the second engine controller respectively; The ac power output mouth of inverter becomes to be electrically connected with drive motor; The ac power supply port of the first engine controller becomes to be electrically connected with the first generator, and the ac power supply port of the second engine controller becomes to be electrically connected with the second generator; First signal input port of programming controller connects the signal output port of the first differential pressure pickup, the secondary signal input port of programming controller connects the signal output port of the second differential pressure pickup, first control output end mouth of programming controller connects the control inputs port of the first engine controller, and the second control output end mouth of programming controller connects the control inputs port of the second engine controller.
The hydraulic pressure installation of the two final controlling element of list pump of the present invention, the electric generator energy-conserving technology of new-energy automobile field innovation and oil hydraulic motor is adopted to combine, combine with generator and oil hydraulic motor and instead of traditional Fixed differential reducing valve and regulate, namely adopt volume adjustment to instead of traditional flow restriction control.When the working pressure of two final controlling element is different, the pressure reduction between final controlling element less to hydraulic pump outlet pressure and load by corresponding oil hydraulic motor and generator, and engine controller converts electrical power storage at electricity storage element, make the front and back pressure reduction of corresponding proportion selector valve be only one for pressure reduction less needed for adjust flux, while guarantee proportional control, reduce energy loss.
Accompanying drawing explanation
Fig. 1 is the structural representation of the hydraulic pressure installation of the two final controlling element of a kind of existing single pump.
Fig. 2 is the structural representation of a hydraulic pressure installation embodiment of the two final controlling element of list pump of the present invention.
Fig. 3 is the front and back pressure reduction control principle schematic diagram of the first proportional reversing valve in Fig. 2 embodiment.
In figure: 1, drive motor; 2, metering pump; 3, first drives oil cylinder; 4, first proportional reversing valve;
5, first shuttle valve; 6, second drives oil cylinder; 7, second proportional reversing valve; 8, second shuttle valve;
9, three shuttle valve; 10, pressure-compensated valve; 11, first Fixed differential reducing valve; 12, second Fixed differential reducing valve; 13, first oil hydraulic motor; 14, first generator; 15, first engine controller;
16, second oil hydraulic motor; 17, second generator; 18, second engine controller;
20, fuel tank; 30, programming controller, 40, electricity storage element; 41, inverter;
50, first differential pressure pickup; 60, second differential pressure pickup.
Embodiment
One, embodiment one
The structure of the hydraulic pressure installation of the two final controlling element of list pump of the present invention, please refer to Fig. 2.This device comprises drive motor 1, metering pump 2, first drives oil cylinder 3, first proportional reversing valve 4, first shuttle valve 5, second drives oil cylinder 6, second proportional reversing valve 7, second shuttle valve 8, 3rd shuttle valve 9, pressure-compensated valve 10, first oil hydraulic motor 13, first generator 14, first engine controller 15, second oil hydraulic motor 16, second generator 17, second engine controller 18, fuel tank 20, programming controller 30, electricity storage element 40, inverter 41, first differential pressure pickup 50 and the second differential pressure pickup 60.Wherein, engine controller is the AC/DC conversion equipment with energy in bidirectional flow function occurred in new-energy automobile development process, such as there is rectification function and the IGBT power model that can run under DSP digital signal processor (Digital Signal Processing) controls, when motor is as generator operation, the AC energy that generator sends by engine controller is converted into direct current energy and delivers in the electricity storage element 40 of storage capacitor or storage battery and so on and store.Programming controller 30 can adopt known programmable controller (PLC) or DSP digital signal processor (DSP) or industrial controlled machine.
The rotating shaft of drive motor 1 is connected with shaft mechanical with the rotating shaft of metering pump 2; The rotating shaft of the first oil hydraulic motor 13 is connected with shaft mechanical with the rotating shaft of the first generator 14; The rotating shaft of the second oil hydraulic motor 16 is connected with shaft mechanical with the rotating shaft of the second generator 17.
Import 201 connected tank 20 of metering pump 2.Outlet 202 point of three tunnel of metering pump 2: the first via connects the filler opening 1001 of pressure compensator 10; Second tunnel connects the filler opening 1301 of the first oil hydraulic motor 13; 3rd tunnel connects the filler opening 1601 of the second oil hydraulic motor 16.Oil outlet 1002 connected tank 20 of pressure compensator 10.
The filler opening 4P of the first proportional reversing valve 4 is connected with the first filler opening 50A1 of the first differential pressure pickup 50 with the outlet 1302 of the first oil hydraulic motor 13 respectively, the oil outlet 4T connected tank 20 of the first proportional reversing valve 4.First actuator port 4A of the first proportional reversing valve 4 drives the rodless cavity 301 of oil cylinder 3 to be connected with the first filler opening 5A1, first of the first shuttle valve 5, and the second actuator port 4B of the first proportional reversing valve 4 drives the rod chamber 302 of oil cylinder 3 to be connected with the second filler opening 5A2, first of the first shuttle valve 5 respectively.Second filler opening 50A2 of the first differential pressure pickup 50 is connected with the oil outlet 503 of the first shuttle valve 5.
The filler opening 7P of the second proportional reversing valve 7 is connected with the first filler opening 60A1 of the second differential pressure pickup 60 with the outlet 1602 of the second oil hydraulic motor 16 respectively, the oil outlet 7T connected tank 20 of the second proportional reversing valve 7.First actuator port 7A of the second proportional reversing valve 7 drives the rodless cavity 601 of oil cylinder 6 to be connected with the first filler opening 8A1, second of the second shuttle valve 8, and the second working oil 7B of the second proportional reversing valve 7 drives the rod chamber 602 of oil cylinder 6 to be connected with the second filler opening 8A2, second of the second shuttle valve 8.Second filler opening 60A2 of the second differential pressure pickup 60 is connected with the oil outlet 803 of the second shuttle valve 8.
First filler opening 9A1 of the 3rd shuttle valve 9 is connected with the oil outlet 503 of the first shuttle valve 5, second filler opening 9A2 of the 3rd shuttle valve 9 is connected with the oil outlet 803 of the second shuttle valve 8, and the oil outlet 903 of the 3rd shuttle valve 9 is connected with the control port 1003 of the spring chamber of pressure compensator 10.
Electricity storage element 40 is connected with the DC electrical source port 1801 of DC electrical source port 1501, second engine controller 18 of DC supply input mouth 4101, first engine controller 15 of inverter 41 respectively.The ac power output mouth 4102 of inverter 41 is electrically connected with drive motor 1 one-tenth.The ac power supply port one 502 of the first engine controller 15 is electrically connected with 14 one-tenth, the first generator, and the ac power supply port one 802 of the second engine controller 18 is electrically connected with 17 one-tenth, the second generator.
First signal input port 3001 of programming controller 30 connects the signal output port 5003 of the first differential pressure pickup 50; The secondary signal input port 3002 of programming controller 30 connects the signal output port 6003 of the second differential pressure pickup 60.First control output end mouth 3003 of programming controller 30 connects the control inputs port 1503 of the first engine controller 15, and the second control output end mouth 3004 of programming controller 30 connects the control inputs port 1803 of the second engine controller 18.
The specific works principle of the hydraulic pressure installation of the two final controlling element of list pump of the present invention is as follows:
Electricity storage element 40 is powered to drive motor 1 by inverter 41.Drive motor 1 drives metering pump 2 to be extracted out by the hydraulic oil in fuel tank 20, provides the working pressure that this hydraulic system needs to whole hydraulic system fuel feeding.
First driving oil cylinder 3 and the first proportional reversing valve 4 form the first final controlling element in this hydraulic system; Two control valve ports 4K1,4K2 of first proportional reversing valve 4 are operated, the hydraulic oil that metering pump 2 can be made to supply the first proportional reversing valve 4 filler opening 4P by the first oil hydraulic motor 13 enters the rodless cavity 301 of the second driving oil cylinder 3 by its first actuator port 4A, meanwhile, first oily the second actuator port 4B by the first proportional reversing valve 4 and oil outlet 4T of original section hydraulic in oil cylinder 3 rod chamber 302 is driven to return fuel tank 20; Or the hydraulic oil making metering pump 2 supply the first proportional reversing valve 4 filler opening 4P by the first oil hydraulic motor 13 enters the rod chamber 302 of the first driving oil cylinder 3 by its first actuator port 4B, meanwhile, first oily the first actuator port 4A by the first proportional reversing valve 4 and oil outlet 4T of original section hydraulic in oil cylinder 3 rodless cavity 301 is driven to return fuel tank 20; Thus change the volume that first drives rodless cavity 301 and rod chamber 302 in oil cylinder 3, make the piston 303 in the first driving oil cylinder 3 do axial movement.
Second driving oil cylinder 6 and the second proportional reversing valve 7 form the second final controlling element in this hydraulic system; Two control valve ports 7K1,7K2 of second proportional reversing valve 7 are operated, the hydraulic oil that metering pump 2 can be made to supply the second proportional reversing valve 7 filler opening 7P by the second oil hydraulic motor 16 enters the rodless cavity 601 of the second driving oil cylinder 6 by its first actuator port 7A, meanwhile, second oily the second actuator port 7B by the second proportional reversing valve 7 and oil outlet 7T of original section hydraulic in oil cylinder 6 rod chamber 602 is driven to return fuel tank 20; Or the hydraulic oil making metering pump 2 supply the second proportional reversing valve 7 filler opening 7P by the second oil hydraulic motor 16 enters the rod chamber 602 of the second driving oil cylinder 6 by its second actuator port 7B, meanwhile, second oily the first actuator port 7A by the second proportional reversing valve 7 and oil outlet 7T of original section hydraulic in oil cylinder 6 rodless cavity 601 is driven to return fuel tank 20; Thus change the volume that second drives rodless cavity 601 and rod chamber 602 in oil cylinder 6, make the piston 603 in the second driving oil cylinder 6 do axial movement.
First see the presser sensor regulatory function of the hydraulic pressure installation of the two final controlling element of list pump of the present invention.
Drive in oil cylinder 3 and the second process driving oil cylinder 6 to work first, the first shuttle valve 5 dynamically detects the induced pressure that the first driving oil cylinder 3 is born, and this induced pressure is passed to the first filler opening 9A1 of the 3rd shuttle valve 9 by its oil outlet 503, second shuttle valve 8 dynamically detects the induced pressure that the second driving oil cylinder 6 is born, and this induced pressure is passed to the second filler opening 9A2 of the 3rd shuttle valve 9 by its oil outlet 803, 3rd shuttle valve 9 obtains above two induced pressures, and get wherein the grater as the current required load pressure maximum pmax of system, load pressure maximum pmax is acted on the control port 1003 of the spring chamber of pressure compensator 10 by the oil outlet 903 of the 3rd shuttle valve 9, the large pressure reduction △ p1 preset by its spring of this load pressure maximum of pressure ratio pmax due to the filler opening 1001 of pressure-compensated valve 10, so the outlet pressure of metering pump 2 oil outlet 202 only certain less pressure reduction △ p1 larger than system present load pressure maximum pmax, achieve the Dynamic Matching of the load pressure maximum needed for metering pump 2 delivery pressure and system.
Pressure reduction controlling functions (for the first proportional reversing valve 4) before and after the proportional reversing valve seeing the hydraulic pressure installation of the two final controlling element of list pump of the present invention again.
The control law of the first proportional reversing valve 4 is as shown in Figure 3, specific as follows:
According to control overflow by the target differential pressure △ p2 artificially set between the first proportional reversing valve 4 filler opening 4P and the first actuator port 4A and the second actuator port 4B (namely specifying the first filler opening 50A1 of the first differential pressure pickup 50 and pressure reduction △ p2 of the second filler opening 50A2), such as 1MPa.
In this plant running, the proportional plus integral controller (referred to as PI) of target differential pressure △ p2 automatic input routine controller 30 inside.Programming controller 30 is gathered and data processing by the differential pressure signal exported the first differential pressure pickup 50, obtain the actual pressure differential data of the valve port 4P-4A (or valve port 4P-4B) of the first proportional reversing valve 4, as the feed back input of the inner PI of programming controller 30;
The PI of programming controller 30 by its inside and the target signal of clipping unit generation control first engine controller 15, the rotating speed of the first generator 14 is adjusted by the first engine controller 15, regulate the rotating speed of the first oil hydraulic motor 13 thus, and then change the pressure of filler opening 4P of the first proportional reversing valve 4, thus the numerical value of the front and back pressure reduction (i.e. filler opening 4P and numerical value the grater in the pressure reduction of the first actuator port 4A and the pressure reduction of filler opening 4P and the second actuator port 4B) of the control valve port of the first proportional reversing valve 4 is adjusted to identical with the numerical value of target differential pressure △ p2.
In like manner, the second generator 17 and the second oil hydraulic motor 16 are to the control procedure of pressure reduction before and after the second proportional reversing valve 7, also similar with the above.Repeat no more.
Finally have a talk about the energy-saving principle of the hydraulic pressure installation of the two final controlling element of list pump of the present invention.
1) suppose that the pressure reduction △ p1 of the spring setting correspondence of differential pressure compensator 10 is 2MPa; The a certain moment first drives induced pressure (driving pressure) p1 of oil cylinder 3 to be 5MPa, and second drives induced pressure (driving pressure) p2 of oil cylinder 6 to be 15MPa;
2) the 3rd shuttle valve 9 obtains system present load pressure maximum pmax by the first shuttle valve 5 and the second shuttle valve 8 is 15MPa;
3) output of the 3rd shuttle valve 9 makes the outlet pressure pz of metering pump 2 only △ p1 larger than load pressure maximum pmax by pressure compensator 5, is 17MPa;
4) programming controller 30 is controlled the first generator 14 and the first oil hydraulic motor 13 by the first engine controller 15 and the first differential pressure pickup 50, the front and back pressure reduction △ pb1 making the first proportional reversing valve 4 is 1MPa, and therefore the two ends pressure reduction of the first oil hydraulic motor 13 is △ pm1=pz – p1-△ pb1=11MPa; This pressure reduction makes the first oil hydraulic motor 13 and the first generator 14 rotate with corresponding rotating speed, at this moment the first generator 14 enters alternator operation state, correspondingly the first engine controller 15 is switched to the transmitter working state of AC-DC, the AC energy that the first generator 14 sends is changed into direct current energy and is stored in electricity storage element 40.
In traditional load-sensitive hydraulic system, the pressure reduction consumption of this 11MPa, on the valve port of the first Fixed differential reducing valve 11, converts conduct heat away to and goes out.And in the hydraulic pressure installation of the two final controlling element of list pump of the present invention, the pressure reduction of this 11MPa changes into electrical power storage in electricity storage element 6 by the first oil hydraulic motor 13, first generator 14 and the first engine controller 15, again can be discharged by drive motor 1 and drive metering pump 2.
According to identical principle, when induced pressure higher than the second oil hydraulic cylinder 6 of the induced pressure of the first oil hydraulic cylinder 3, pressure reduction on second oil hydraulic motor 16 will make the second oil hydraulic motor 16 and the second generator 17 rotate with corresponding rotating speed, at this moment the second generator 17 enters alternator operation state, correspondingly the second engine controller 18 is switched to the transmitter working state of AC-DC, the AC energy that the second generator 17 sends is changed into direct current energy and is stored in electricity storage element 40.
The above, be only present pre-ferred embodiments, do not limit scope of the invention process with this, and equivalence change and the modification done according to technological scheme of the present invention and description, all should belong to the scope that the present invention is contained.
Claims (1)
1. a hydraulic pressure installation for the two final controlling element of single pump, wherein, drive motor is coaxially connected with metering pump; The import connected tank of metering pump, quantitative delivery side of pump connects the filler opening of pressure compensator; The oil outlet connected tank of pressure compensator; The oil outlet connected tank of the first proportional reversing valve, first actuator port of the first proportional reversing valve connects the first filler opening of the first shuttle valve, the rodless cavity of the first driving oil cylinder respectively, and the second actuator port of the first proportional reversing valve connects the rod chamber that the second filler opening of the first shuttle valve, first drives oil cylinder respectively; The oil outlet connected tank of the second proportional reversing valve, first actuator port of the second proportional reversing valve connects the first filler opening of the second shuttle valve, the rodless cavity of the second driving oil cylinder respectively, and the second actuator port of the second proportional reversing valve connects the rod chamber that the second filler opening of the second shuttle valve, second drives oil cylinder respectively; First filler opening of the 3rd shuttle valve connects the oil outlet of the first shuttle valve, and the second filler opening of the 3rd shuttle valve connects the oil outlet of the second shuttle valve, and the oil outlet of the 3rd shuttle valve connects the control port of the spring chamber of pressure compensator; It is characterized in that: it also has the first oil hydraulic motor, the first generator, the first engine controller, the second oil hydraulic motor, the second generator, the second engine controller, programming controller, electricity storage element, inverter, the first differential pressure pickup and the second differential pressure pickup; Quantitative delivery side of pump connects the filler opening of the first oil hydraulic motor and the filler opening of the second oil hydraulic motor respectively; The filler opening of the first proportional reversing valve connects the outlet of the first oil hydraulic motor and the first filler opening of the first differential pressure pickup respectively; The filler opening of the second proportional reversing valve connects the outlet of the second oil hydraulic motor and the first filler opening of the second differential pressure pickup respectively; Electricity storage element is connected with the DC supply input mouth of inverter, the DC electrical source port of the first engine controller, the DC electrical source port of the second engine controller respectively; The ac power output mouth of inverter becomes to be electrically connected with drive motor; The ac power supply port of the first engine controller becomes to be electrically connected with the first generator, and the ac power supply port of the second engine controller becomes to be electrically connected with the second generator; First signal input port of programming controller connects the signal output port of the first differential pressure pickup, the secondary signal input port of programming controller connects the signal output port of the second differential pressure pickup, first control output end mouth of programming controller connects the control inputs port of the first engine controller, and the second control output end mouth of programming controller connects the control inputs port of the second engine controller.
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| CN201410733607.0A CN104481942B (en) | 2014-12-04 | 2014-12-04 | A kind of hydraulic means of the double executor of single pump |
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| CN201410733607.0A CN104481942B (en) | 2014-12-04 | 2014-12-04 | A kind of hydraulic means of the double executor of single pump |
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| CN104481942B CN104481942B (en) | 2016-08-24 |
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| CN109578354A (en) * | 2018-12-20 | 2019-04-05 | 徐工集团工程机械股份有限公司 | A kind of hydraulic control system and integrated valve group of hanging oil cylinder synchronization lifting |
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| CN111706563A (en) * | 2020-06-03 | 2020-09-25 | 华侨大学 | Three-way speed regulating valve based on hydraulic motor-generator pressure compensator |
| CN113027874A (en) * | 2021-03-11 | 2021-06-25 | 中联重科股份有限公司 | Concrete pumping equipment energy recovery system and method and concrete pumping equipment |
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| CN111706563B (en) * | 2020-06-03 | 2022-05-03 | 华侨大学 | Three-way speed regulating valve based on hydraulic motor-generator pressure compensator |
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| CN113062888A (en) * | 2021-04-23 | 2021-07-02 | 中国铁建重工集团股份有限公司 | Rotary hydraulic control system of assembling machine |
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