CN104481942B - A kind of hydraulic means of the double executor of single pump - Google Patents
A kind of hydraulic means of the double executor of single pump Download PDFInfo
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- CN104481942B CN104481942B CN201410733607.0A CN201410733607A CN104481942B CN 104481942 B CN104481942 B CN 104481942B CN 201410733607 A CN201410733607 A CN 201410733607A CN 104481942 B CN104481942 B CN 104481942B
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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 hydraulic means of the double executor of a kind of single pump of the present invention, relates to the hydraulic means of dosing pump load-sensitive.It includes driving motor, dosing pump, first drives oil cylinder, second drives oil cylinder, first electromotor, second electromotor, first engine controller, second engine controller, inverter, first hydraulic motor, second hydraulic motor, first proportional direction valve, second proportional direction valve, first shuttle valve, second shuttle valve, 3rd shuttle valve, pressure-compensated valve, first differential pressure pickup, second differential pressure pickup, cyclelog etc., this device uses hydraulic motor and electromotor as the regulation unit of pressure reduction before and after proportional direction valve control throttle orifice, tradition consumption is converted into electrical power storage in electricity storage element in the throttling loss of uniform-pressure-drop valve valve port, solve when different executor's operating pressure difference are bigger a large amount of energy expenditures weak point on the uniform-pressure-drop valve valve port of the less executor of operating pressure.
Description
Technical field
The present invention relates to the hydraulic means of a kind of dosing pump load-sensitive.
Background technology
Existing dosing pump load sensitive system is mainly by the load of multiple executors in shuttle valve acquisition system
Maximum pressure, and act on dosing pump outlet pressure compensator so that the outlet pressure of dosing pump only than
Load maximum pressure is more than certain less pressure reduction, it is achieved the load needed for dosing pump output pressure and system
The Dynamic Matching of maximum pressure.A kind of knot of the hydraulic means of the double executor of typical load-sensitive type list pump
Structure, as shown in Figure 1.The rotating shaft driving motor 1 is coaxially connected with the main shaft of dosing pump 2.Entering of dosing pump 2
Mouth 201 connected tanks 20,202 point of three tunnel of the outlet of dosing pump 2: the first via connects the oil-feed of pressure compensator 10
Mouth 1001；Second tunnel meets the oil-in 11P of the first uniform-pressure-drop valve 11；3rd tunnel connects second and determines subtractive pressure
The oil-in 12 of valve 12.Oil-out 1002 connected tank 20 of pressure compensator 10.
The oil-in 4P of the first proportional reversing valve 4 and the outlet 1101 of the first uniform-pressure-drop valve 11 are connected, the
The oil-out 4T connected tank 20 of one proportional reversing valve 4.First actuator port 4A of the first proportional reversing valve 4 divides
It is not connected with the first oil-in 5A1, the rodless cavity 301 of the first driving oil cylinder 3 of the first shuttle valve 5, the first ratio
Second actuator port 4B of example reversal valve 4 respectively with the second oil-in 5A2 of the first shuttle valve 5, first drive
The rod chamber 302 of oil cylinder 3 is connected.First drives oil cylinder 3 and the first proportional reversing valve 4 to form this hydraulic system
In the first executor, the first shuttle valve 5 is the detector unit of this first executor load pressure.
The oil-in 7P of the second proportional reversing valve 7 and the outlet 1201 of the second uniform-pressure-drop valve 12 are connected, the
The oil-out 7T connected tank 20 of two proportional reversing valves 7.First actuator port 7A of the second proportional reversing valve 7 divides
It is not connected with the first oil-in 8A1, the rodless cavity 601 of the second driving oil cylinder 6 of the second shuttle valve 8, the second ratio
Second working oil 7B of example reversal valve 7 respectively with the second oil-in 8A2 of the second shuttle valve 8, second drive oil
The rod chamber 602 of cylinder 6 is connected.Second drives oil cylinder 6 and the second proportional reversing valve 7 to form in this hydraulic system
The second executor, the second shuttle valve 8 is the detector unit of this second executor load pressure.
First oil-in 9A1 of the 3rd shuttle valve 9 is fixed poor with the oil-out 503 and first of the first shuttle valve 5 respectively
The control port 11L of the spring cavity of air relief valve 11 be connected, the second oil-in 9A2 of the 3rd shuttle valve 9 respectively with
The oil-out 803 of the second shuttle valve 8 is connected with the control port 12L of the spring cavity of the second uniform-pressure-drop valve 12,
The oil-out 903 of the 3rd shuttle valve 9 is connected with the control port 1003 of the spring cavity of pressure compensator 10.3rd
Shuttle valve 9 is the detector unit that two executors load maximum pressure.
The hydraulic means of the double executor of this list pump is operationally: drive motor 1 to drive dosing pump 2 by fuel tank 20
In hydraulic oil extract out, by two uniform-pressure-drop valves respectively to two executor's fuel feeding and provide the two
The operating pressure that executor needs；First drives oil cylinder 3 and the first proportional reversing valve 4 to form this hydraulic means
In the first executor；Two controls valve port 4K1,4K2 of first proportional reversing valve 4 are operated,
Dosing pump 2 can be made to supply the liquid of the first proportional reversing valve 4 oil-in 4P by the first uniform-pressure-drop valve 11
Force feed enters the rodless cavity 301 of the first driving oil cylinder 3 by its first actuator port 4A, and meanwhile, first drives
Original section hydraulic oil the second working oil by the first proportional reversing valve 3 in dynamic oil cylinder 3 rod chamber 302
Mouth 3B and oil-out 3T returns fuel tank 20；Or make dosing pump 2 supply first by the first uniform-pressure-drop valve 4
The hydraulic oil of proportional reversing valve 4 oil-in 4P enters the first driving oil cylinder 3 by its first actuator port 4B
Rod chamber 302, meanwhile, first drives in oil cylinder 3 rodless cavity 301 original section hydraulic oil by the
First actuator port 4A of one proportional reversing valve 4 and oil-out 4T returns fuel tank 20；Thus change first and drive
Rodless cavity 301 and the volume ratio of rod chamber 302 in dynamic oil cylinder 3, make the piston 303 in the first driving oil cylinder 3
Do axial movement.
Second drives oil cylinder 6 and the second proportional reversing valve 7 to form the second executor in this hydraulic means；Right
Two of second proportional reversing valve 7 control valve port 7K1,7K2 operate, and dosing pump 2 can be made by the
Two uniform-pressure-drop valves 12 supply the hydraulic oil of the second proportional reversing valve 7 oil-in 7P by its first working oil
Mouth 7A enters the rodless cavity 601 of the second driving oil cylinder 6, meanwhile, former in the second driving oil cylinder 6 rod chamber 602
Some section hydraulic oil returns oil by the second actuator port 7B and oil-out 7T of the second proportional reversing valve 7
Case 20；Or make dosing pump 2 supply the second proportional reversing valve 7 oil-in 7P by the second uniform-pressure-drop valve 12
Hydraulic oil entered the rod chamber 602 of the second driving oil cylinder 6, meanwhile, the by its second actuator port 7B
Two drive original section hydraulic oil the first work by the second proportional reversing valve 7 in oil cylinder 6 rodless cavity 601
Make hydraulic fluid port 7A and oil-out 7T and return fuel tank 20；Thus rodless cavity 601 and having in changing the second driving oil cylinder 6
The volume ratio in bar chamber 602, makes the piston 603 in the second driving oil cylinder 6 do axial movement.
During driving oil cylinder 3 and the second driving oil cylinder 6 work first, the first shuttle valve 5 is dynamically examined
Measure the load pressure that the first driving oil cylinder 3 undertakes, and by its oil-out 503, this load pressure is transmitted
To control port 11L and first oil-in of the 3rd shuttle valve 9 of the spring cavity of the first uniform-pressure-drop valve 11
9A1；First uniform-pressure-drop valve 11 is controlled by this load pressure so that it is outlet 1101 is with suitable stream
Measure and supply hydraulic oil to the oil-in 4P of the first proportional reversing valve 4.Second shuttle valve 8 dynamically detects second
Drive the load pressure that oil cylinder 6 undertakes, and by its oil-out 803, this load pressure is passed to second calmly
The control port 12L of the spring cavity of difference pressure-reducing valve 12 and the second oil-in 9A2 of the 3rd shuttle valve 9；Second is fixed
Difference pressure-reducing valve 12 is driven oil cylinder 6 load pressure to be controlled by second so that it is outlet 1201 is with suitable stream
Measure and supply hydraulic oil to the oil-in 7P of the second proportional reversing valve 7.3rd shuttle valve 9 obtains the first driving oil cylinder
The load pressure of 3 and second drive oil cylinder 6 load pressure, and take wherein the greater as the current institute of system
Need to load maximum pressure pmax, this load maximum pressure pmax is acted on by the oil-out 903 of the 3rd shuttle valve 9
The control port 1003 of the spring cavity of pressure compensator 10, due to the oil-in 1001 of pressure-compensated valve 10
Pressure ratio this load maximum pressure pmax big one by its spring pressure reduction set in advance △ p1, so quantitatively
The outlet pressure of pump 2 oil-out 202 is only bigger certain less pressure than system present load maximum pressure pmax
Difference △ p1, it is achieved that the Dynamic Matching of the load maximum pressure needed for dosing pump 2 output pressure and system.
But, in this plant running, owing to the operating pressure needed for different executors is different, dosing pump
The outlet pressure of 2 is determined by maximum load pressure, the work needed for that executor that operating pressure is less
There is pressure reduction with the outlet pressure of dosing pump 2 in pressure, it is necessary to by that executor that operating pressure is less
The valve port above-mentioned pressure reduction of balance of uniform-pressure-drop valve.Therefore its essence is to realize pressure by throttling loss
The balance of power difference, the capacity usage ratio causing dosing pump load sensitive system is the highest, especially not
With the operating pressure difference of executor bigger time.
Summary of the invention
It is desirable to provide the hydraulic means of the double executor of a kind of single pump, it can with recovery operation pressure relatively
Energy corresponding to pressure reduction between that little executor and the outlet pressure of dosing pump 2, improves energy profit
By rate.
The technical scheme is that the hydraulic means of the double executor of a kind of single pump, wherein, drive motor
Coaxially connected with dosing pump；The import connected tank of dosing pump, quantitative delivery side of pump meets entering of pressure compensator
Hydraulic fluid port；The oil-out connected tank of pressure compensator；The oil-out connected tank of the first proportional reversing valve, first
First actuator port of proportional reversing valve connects the first oil-in of the first shuttle valve respectively, first drives oil cylinder
Rodless cavity, the second actuator port of the first proportional reversing valve connect respectively the second oil-in of the first shuttle valve,
One rod chamber driving oil cylinder；The oil-out connected tank of the second proportional reversing valve, the second proportional reversing valve
First actuator port connect respectively the first oil-in of the second shuttle valve, second drive oil cylinder rodless cavity, second
Second actuator port of proportional reversing valve connects the second oil-in of the second shuttle valve respectively, second drives oil cylinder
Rod chamber；First oil-in of the 3rd shuttle valve connects the oil-out of the first shuttle valve, the second oil-feed of the 3rd shuttle valve
Mouth connects the oil-out of the second shuttle valve, and the oil-out of the 3rd shuttle valve connects the control oil of the spring cavity of pressure compensator
Mouthful；It also have the first hydraulic motor, the first electromotor, the first engine controller, the second hydraulic motor,
Second electromotor, the second engine controller, cyclelog, electricity storage element, inverter,
One differential pressure pickup and the second differential pressure pickup；Quantitatively delivery side of pump connects the oil-feed of the first hydraulic motor respectively
Mouth and the oil-in of the second hydraulic motor；The oil-in of the first proportional reversing valve connects the first hydraulic motor respectively
Outlet and the first oil-in of the first differential pressure pickup；The oil-in of the second proportional reversing valve connects respectively
The outlet of two hydraulic motors and the first oil-in of the second differential pressure pickup；Electricity storage element is respectively with inverse
Become the DC supply input mouth of device, the DC source port of the first engine controller, the second electromotor
The DC source port of controller is connected；The ac power output mouth of inverter becomes electrical with driving motor
Connect；The alternating current power supply port of the first engine controller and the first electromotor become to be electrically connected with, second
The alternating current power supply port of electric machine controller and the second electromotor become to be electrically connected with；First letter of cyclelog
Number input port connects the signal output port of the first differential pressure pickup, the secondary signal input of cyclelog
Port connects the signal output port of the second differential pressure pickup, and the first control output end mouth of cyclelog connects
The control input port of the first engine controller, the second control output end mouth of cyclelog connects the
The control input port of two engine controllers.
The hydraulic means of the double executor of list pump of the present invention, uses the electromotor joint of new-energy automobile field innovation
Technology can combine with hydraulic motor, instead of traditional uniform-pressure-drop valve with electromotor with hydraulic motor combination
Regulation, i.e. uses volume adjustment to instead of traditional flow restriction control.When two executors operating pressure not
Meanwhile, the pressure reduction between executor less with load for hydraulic pump outlet pressure by corresponding hydraulic pressure horse
Reach and electromotor, and engine controller is converted into electrical power storage at electricity storage element so that be corresponding
Before and after proportional reversing valve, pressure reduction is only a pressure reduction less needed for regulating flow, is ensureing ratio
Energy loss is reduced while control.
Accompanying drawing explanation
Fig. 1 is the structural representation of the hydraulic means of the double executor of a kind of existing single pump.
Fig. 2 is the structural representation of one embodiment of hydraulic means of the double executor of list pump of the present invention.
Fig. 3 is pressure reduction control principle schematic diagram before and after the first proportional reversing valve in Fig. 2 embodiment.
In figure: 1, drive motor；2, dosing pump；3, first drives oil cylinder；4, the first proportional reversing valve；
5, the first shuttle valve；6, second drives oil cylinder；7, the second proportional reversing valve；8, the second shuttle valve；
9, the 3rd shuttle valve；10, pressure-compensated valve；11, the first uniform-pressure-drop valve；12, second determines subtractive pressure
Valve；13, the first hydraulic motor；14, the first electromotor；15, the first engine controller；
16, the second hydraulic motor；17, the second electromotor；18, the second engine controller；
20, fuel tank；30, cyclelog, 40, electricity storage element；41, inverter；
50, the first differential pressure pickup；60, the second differential pressure pickup.
Detailed description of the invention
One, embodiment one
The structure of the hydraulic means of the double executor of list pump of the present invention, refer to Fig. 2.This device includes driving
Motor 1, dosing pump 2, first drive oil cylinder the 3, first proportional reversing valve the 4, first shuttle valve 5, second drive
Dynamic oil cylinder the 6, second proportional reversing valve the 7, second shuttle valve the 8, the 3rd shuttle valve 9, pressure-compensated valve 10, first
Hydraulic motor the 13, first electromotor the 14, first engine controller the 15, second hydraulic motor 16, second
Electromotor the 17, second engine controller 18, fuel tank 20, cyclelog 30, electricity storage element 40,
Inverter the 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 can be at digital signal processor (Digital Signal Processing)
Controlling the lower IGBT power model run, when motor is as generator operation, engine controller will be sent out
The AC energy that motor sends is converted into direct current energy and delivers to the electricity storage of storage capacitor or accumulator etc
Memory cell 40 stores.Cyclelog 30 can use known Programmable Logic Controller (PLC)
Or digital signal processor (DSP) or industrial controlled machine.
The rotating shaft of motor 1 is driven coaxially to be mechanically coupled with the rotating shaft of dosing pump 2；Turning of first hydraulic motor 13
The rotating shaft of axle and the first electromotor 14 is coaxially mechanically coupled；The rotating shaft of the second hydraulic motor 16 and the second generating
The rotating shaft of machine 17 is coaxially mechanically coupled.
Import 201 connected tank 20 of dosing pump 2.202 point of three tunnel of the outlet of dosing pump 2: the first via connects pressure
The oil-in 1001 of compensator 10；Second tunnel connects the oil-in 1301 of the first hydraulic motor 13；3rd tunnel connects
The oil-in 1601 of the second hydraulic motor 16.Oil-out 1002 connected tank 20 of pressure compensator 10.
The oil-in 4P of the first proportional reversing valve 4 respectively with the outlet 1302 and first of the first hydraulic motor 13
First oil-in 50A1 of differential pressure pickup 50 is connected, the oil-out 4T connected tank of the first proportional reversing valve 4
20.First actuator port 4A of the first proportional reversing valve 4 and the first oil-in 5A1 of the first shuttle valve 5,
One drives the rodless cavity 301 of oil cylinder 3 to be connected, the second actuator port 4B of the first proportional reversing valve 4 respectively with
Second oil-in 5A2 of the first shuttle valve 5, the rod chamber 302 of the first driving oil cylinder 3 are connected.First pressure reduction passes
Second oil-in 50A2 of sensor 50 and the oil-out 503 of the first shuttle valve 5 are connected.
The oil-in 7P of the second proportional reversing valve 7 respectively with the outlet 1602 and second of the second hydraulic motor 16
First oil-in 60A1 of differential pressure pickup 60 is connected, the oil-out 7T connected tank of the second proportional reversing valve 7
20.First actuator port 7A of the second proportional reversing valve 7 and the first oil-in 8A1 of the second shuttle valve 8,
Two drive the rodless cavity 601 of oil cylinder 6 to be connected, the second working oil 7B of the second proportional reversing valve 7 and the second shuttle
Second oil-in 8A2 of valve 8, the rod chamber 602 of the second driving oil cylinder 6 are connected.Second differential pressure pickup 60
The second oil-in 60A2 and the oil-out 803 of the second shuttle valve 8 be connected.
First oil-in 9A1 of the 3rd shuttle valve 9 and the oil-out 503 of the first shuttle valve 5 are connected, the 3rd shuttle valve 9
The second oil-in 9A2 and the oil-out 803 of the second shuttle valve 8 be connected, the oil-out 903 of the 3rd shuttle valve 9 with
The control port 1003 of the spring cavity of pressure compensator 10 is connected.
Electricity storage element 40 respectively with DC supply input mouth 4101, first electromotor of inverter 41
DC source port 1801 phase of DC source port 1501, second engine controller 18 of controller 15
Even.The ac power output mouth 4102 of inverter 41 becomes to be electrically connected with driving motor 1.First generating
The alternating current power supply port 1502 of machine controller 15 becomes to be electrically connected with the first electromotor 14, the second electromotor control
The alternating current power supply port 1802 of device 18 processed becomes to be electrically connected with the second electromotor 17.
First signal input port 3001 of cyclelog 30 connects the signal of the first differential pressure pickup 50
Output port 5003；The secondary signal input port 3002 of cyclelog 30 connects the second differential pressure pickup
The signal output port 6003 of 60.First control output end mouth 3003 of cyclelog 30 connects first
The control input port 1503 of electric machine controller 15, the second control output end mouth 3004 of cyclelog 30
Connect the control input port 1803 of the second engine controller 18.
The specific works principle of the hydraulic means of the double executor of list pump of the present invention is as follows:
Electricity storage element 40 is powered to driving motor 1 by inverter 41.Motor 1 is driven to drive dosing pump
Hydraulic oil in fuel tank 20 is extracted out, to whole hydraulic system fuel feeding and provide this hydraulic system to need by 2
Operating pressure.
First drives oil cylinder 3 and the first proportional reversing valve 4 to form the first executor in this hydraulic system；Right
Two of first proportional reversing valve 4 control valve port 4K1,4K2 operate, and dosing pump 2 can be made by the
One hydraulic motor 13 supplies the hydraulic oil of the first proportional reversing valve 4 oil-in 4P by its first actuator port
4A enters the rodless cavity 301 of the second driving oil cylinder 3, meanwhile, original in the first driving oil cylinder 3 rod chamber 302
Section hydraulic oil return fuel tank by the second actuator port 4B and oil-out 4T of the first proportional reversing valve 4
20；Or make dosing pump 2 supply the liquid of the first proportional reversing valve 4 oil-in 4P by the first hydraulic motor 13
Force feed enters the rod chamber 302 of the first driving oil cylinder 3 by its first actuator port 4B, and meanwhile, first drives
Original section hydraulic oil the first working oil by the first proportional reversing valve 4 in dynamic oil cylinder 3 rodless cavity 301
Mouth 4A and oil-out 4T returns fuel tank 20；Thus change rodless cavity 301 and rod chamber in the first driving oil cylinder 3
The volume of 302, makes the piston 303 in the first driving oil cylinder 3 do axial movement.
Second drives oil cylinder 6 and the second proportional reversing valve 7 to form the second executor in this hydraulic system；Right
Two of second proportional reversing valve 7 control valve port 7K1,7K2 operate, and dosing pump 2 can be made by the
Two hydraulic motors 16 supply the hydraulic oil of the second proportional reversing valve 7 oil-in 7P by its first actuator port
7A enters the rodless cavity 601 of the second driving oil cylinder 6, meanwhile, original in the second driving oil cylinder 6 rod chamber 602
Section hydraulic oil return fuel tank by the second actuator port 7B and oil-out 7T of the second proportional reversing valve 7
20；Or make dosing pump 2 supply the liquid of the second proportional reversing valve 7 oil-in 7P by the second hydraulic motor 16
Force feed enters the rod chamber 602 of the second driving oil cylinder 6 by its second actuator port 7B, and meanwhile, second drives
Original section hydraulic oil the first working oil by the second proportional reversing valve 7 in dynamic oil cylinder 6 rodless cavity 601
Mouth 7A and oil-out 7T returns fuel tank 20；Thus change rodless cavity 601 and rod chamber in the second driving oil cylinder 6
The volume of 602, makes the piston 603 in the second driving oil cylinder 6 do axial movement.
Presser sensor regulatory function referring initially to the hydraulic means of the double executor of list pump of the present invention.
During driving oil cylinder 3 and the second driving oil cylinder 6 work first, the first shuttle valve 5 is dynamically examined
Measure the load pressure that the first driving oil cylinder 3 undertakes, and by its oil-out 503, this load pressure is transmitted
To the first oil-in 9A1 of the 3rd shuttle valve 9；Second shuttle valve 8 dynamically detects that the second driving oil cylinder 6 undertakes
Load pressure, and by its oil-out 803, this load pressure is passed to the second oil-feed of the 3rd shuttle valve 9
Mouth 9A2；3rd shuttle valve 9 obtains two above load pressure, and take wherein the greater as the current institute of system
Need to load maximum pressure pmax, load maximum pressure pmax is acted on pressure by the oil-out 903 of the 3rd shuttle valve 9
The control port 1003 of the spring cavity of force compensating device 10, due to the pressure of the oil-in 1001 of pressure-compensated valve 10
Force rate this load maximum pressure pmax big one by its spring pressure reduction set in advance △ p1, so dosing pump
The outlet pressure of 2 oil-outs 202 is only bigger certain less pressure reduction than system present load maximum pressure pmax
△ p1, it is achieved that the Dynamic Matching of the load maximum pressure needed for dosing pump 2 output pressure and system.
See again the double executor of list pump of the present invention hydraulic means proportional reversing valve before and after pressure reduction control function
(as a example by the first proportional reversing valve 4).
The control rule of the first proportional reversing valve 4 is as it is shown on figure 3, specific as follows:
According to controlling requirement by being manually set the first proportional reversing valve 4 oil-in 4P and the first actuator port 4A
And the target differential pressure △ p2 that second between actuator port 4B (namely specifies the of the first differential pressure pickup 50
The pressure reduction △ p2 of one oil-in 50A1 and the second oil-in 50A2), such as 1MPa.
In this plant running, target differential pressure △ p2 automatically enters the proportional integral control within cyclelog 30
Device processed (is abbreviated as PI).Cyclelog 30 is by believing the pressure differential of the first differential pressure pickup 50 output
Number it is acquired and data process, it is thus achieved that the valve port 4P-4A (or valve port 4P-4B) of the first proportional reversing valve 4
Actual pressure differential data, as the feed back input of the internal PI of cyclelog 30；
Cyclelog 30 is produced by its internal PI and clipping unit and controls the first engine controller
The echo signal of 15, is adjusted the rotating speed of the first electromotor 14, thus adjusts by the first engine controller 15
Save the rotating speed of the first hydraulic motor 13, and then change the pressure of the oil-in 4P of the first proportional reversing valve 4,
Thus by pressure reduction (i.e. oil-in 4P and the first working oil before and after the control valve port of the first proportional reversing valve 4
Numerical value the greater in mouthful pressure reduction of 4A and the pressure reduction of oil-in 4P and the second actuator port 4B) numerical value adjustment
For identical with the numerical value of target differential pressure △ p2.
In like manner, the second electromotor 17 and the second hydraulic motor 16 are to pressure reduction before and after the second proportional reversing valve 7
Control process, also with similarly as described above.Repeat no more.
Finally have a talk about the energy-saving principle of the hydraulic means of the double executor of list pump of the present invention.
1) assume that the spring of differential pressure compensator 10 sets corresponding pressure reduction △ p1 as 2MPa；The a certain moment
Load pressure (driving pressure) p1 of the first driving oil cylinder 3 is 5MPa, and second drives the negative of oil cylinder 6
Carrying pressure (driving pressure) p2 is 15MPa；
2) the 3rd shuttle valve 9 obtains system present load maximum by the first shuttle valve 5 and the second shuttle valve 8
Pressure p max is 15MPa；
3) output of the 3rd shuttle valve 9 makes the outlet pressure pz of dosing pump 2 by pressure compensator 5
Only ratio load maximum pressure pmax big △ p1, is 17MPa；
4) cyclelog 30 is right by the first engine controller 15 and the first differential pressure pickup 50
First electromotor 14 and the first hydraulic motor 13 are controlled so that before and after the first proportional reversing valve 4
Pressure reduction △ pb1 is 1MPa, and therefore the two ends pressure reduction of the first hydraulic motor 13 is △ pm1=pz p1-△
Pb1=11MPa；This pressure reduction makes the first hydraulic motor 13 and the first electromotor 14 carry out with corresponding rotating speed
Rotating, at this moment the first electromotor 14 enters alternator operation state, correspondingly the first electromotor control
Device 15 processed is switched to the transmitter duty of AC-DC, the exchange sent by the first electromotor 14
Electric energy changes 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 is at the first uniform-pressure-drop valve 11
Valve port on, be converted into conduct heat away and go out.And in the hydraulic means of the double executor of list pump of the present invention,
The pressure reduction of this 11MPa passes through the first hydraulic motor the 13, first electromotor 14 and the first engine controller
15 change into electrical power storage in electricity storage element 6, can drive again through driving motor 1 discharge
Dynamic dosing pump 2.
According to identical principle, when the load pressure of the first oil hydraulic cylinder 3 is higher than the load of the second oil hydraulic cylinder 6
During pressure, the pressure reduction on the second hydraulic motor 16 will make the second hydraulic motor 16 and the second electromotor 17
Rotating with corresponding rotating speed, at this moment the second electromotor 17 enters alternator operation state, phase
Answer ground the second engine controller 18 to be switched to the transmitter duty of AC-DC, generate electricity second
The AC energy that machine 17 sends changes into direct current energy and is stored in electricity storage element 40.
The above, only present pre-ferred embodiments, do not limit, with this, the scope that the present invention implements, depend on
Equivalence change and the modification that technical scheme and description are made, all should belong to the present invention and contain
The scope of lid.
Claims (1)
1. the hydraulic means of the double executor of single pump, wherein, drives motor coaxially connected with dosing pump；
The import connected tank of dosing pump, quantitative delivery side of pump connects the oil-in of pressure compensator；Pressure compensator
Oil-out connected tank；The oil-out connected tank of the first proportional reversing valve, the first work of the first proportional reversing valve
Making hydraulic fluid port and connect the first oil-in of the first shuttle valve, the rodless cavity of the first driving oil cylinder respectively, the first ratio is changed
To the second actuator port of valve connect respectively the second oil-in of the first shuttle valve, first drive oil cylinder have bar
Chamber；The oil-out connected tank of the second proportional reversing valve, the first actuator port of the second proportional reversing valve is respectively
Connect the first oil-in of the second shuttle valve, the rodless cavity of the second driving oil cylinder, the second of the second proportional reversing valve
Actuator port connects the second oil-in of the second shuttle valve, the rod chamber of the second driving oil cylinder respectively；3rd shuttle valve
The first oil-in connect the oil-out of the first shuttle valve, the second oil-in of the 3rd shuttle valve meets going out of the second shuttle valve
Hydraulic fluid port, the oil-out of the 3rd shuttle valve connects the control port of the spring cavity of pressure compensator；It is characterized in that:
It also have the first hydraulic motor, the first electromotor, the first engine controller, the second hydraulic motor,
Two electromotors, the second engine controller, cyclelog, electricity storage element, inverter, first
Differential pressure pickup and the second differential pressure pickup；Quantitatively delivery side of pump connects the oil-in of the first hydraulic motor respectively
Oil-in with the second hydraulic motor；The oil-in of the first proportional reversing valve connects the first hydraulic motor respectively
Outlet and the first oil-in of the first differential pressure pickup；The oil-in of the second proportional reversing valve connects second respectively
The outlet of hydraulic motor and the first oil-in of the second differential pressure pickup；Electricity storage element respectively with inversion
The DC supply input mouth of device, the DC source port of the first engine controller, the second electromotor control
The DC source port of device processed is connected；The ac power output mouth of inverter becomes electrically connect with driving motor
Connect；The alternating current power supply port of the first engine controller and the first electromotor become to be electrically connected with, the second generating
The alternating current power supply port of machine controller and the second electromotor become to be electrically connected with；First signal of cyclelog
Input port connects the signal output port of the first differential pressure pickup, the secondary signal input of cyclelog
Mouth connects the signal output port of the second differential pressure pickup, and the first control output end mouth of cyclelog connects the
The control input port of one engine controller, the second control output end mouth of cyclelog connects second
The control input port of engine controller.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410733607.0A CN104481942B (en) | 2014-12-04 | 2014-12-04 | A kind of hydraulic means of the double executor of single pump |
Applications Claiming Priority (1)
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| CN108506259B (en) * | 2018-04-09 | 2022-02-11 | 徐州燕大传动与控制技术有限公司 | Load sensing type multi-way valve with independently controlled inlet and outlet for valve post compensation |
| 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 |
| CN111577682B (en) * | 2020-05-19 | 2022-03-04 | 华侨大学 | Two-way speed regulating valve based on variable pressure difference active control |
| CN111706564A (en) * | 2020-06-03 | 2020-09-25 | 华侨大学 | Two-way speed regulating valve based on volume variable pressure difference active control |
| CN111706563B (en) * | 2020-06-03 | 2022-05-03 | 华侨大学 | Three-way speed regulating valve based on hydraulic motor-generator pressure compensator |
| CN113027874B (en) * | 2021-03-11 | 2022-05-27 | 中联重科股份有限公司 | Concrete pumping equipment energy recovery system and method and concrete pumping equipment |
| CN113062888B (en) * | 2021-04-23 | 2023-03-10 | 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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| CN101980881B (en) * | 2008-03-27 | 2013-12-18 | 力至优三菱叉车株式会社 | Hybrid industrial vehicle |
| US20110056194A1 (en) * | 2009-09-10 | 2011-03-10 | Bucyrus International, Inc. | Hydraulic system for heavy equipment |
| US8909434B2 (en) * | 2011-06-29 | 2014-12-09 | Caterpillar, Inc. | System and method for controlling power in machine having electric and/or hydraulic devices |
| EP2754758B1 (en) * | 2011-09-09 | 2018-03-07 | Sumitomo Heavy Industries, Ltd. | Excavator and control method for excavator |
| CN103148031B (en) * | 2013-03-27 | 2015-07-08 | 南京工业大学 | Hydraulic movable arm loop energy-saving control system |
| CN204371806U (en) * | 2014-12-04 | 2015-06-03 | 华侨大学 | The hydraulic pressure installation of the two final controlling element of a kind of single pump |
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