CN104785568B - Extruder extrusion process hydraulic system modeling and energy consumption analysis method - Google Patents
Extruder extrusion process hydraulic system modeling and energy consumption analysis method Download PDFInfo
- Publication number
- CN104785568B CN104785568B CN201510208297.5A CN201510208297A CN104785568B CN 104785568 B CN104785568 B CN 104785568B CN 201510208297 A CN201510208297 A CN 201510208297A CN 104785568 B CN104785568 B CN 104785568B
- Authority
- CN
- China
- Prior art keywords
- energy consumption
- plunger
- valve
- loss
- energy
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Active
Links
Landscapes
- Reciprocating Pumps (AREA)
- Extrusion Moulding Of Plastics Or The Like (AREA)
Abstract
The invention discloses extruder extrusion process hydraulic system modeling and energy consumption analysis method, with 10MN aluminium extruding machines as research object, for the serious problem of the energy loss of extrusion process, energy flow direction, energy transition form and the energy ezpenditure that extruding machine hydraulic system is analyzed by technological means, and provide corresponding theoretical energy consumption formula, contribute to the key element for summing up power consumption, make the energy saving optimizing of extruder more purposive.
Description
Technical field
The invention belongs to the energy consumption analysis of extruder and cost control technique field, more particularly to a kind of extruder was extruded
Journey hydraulic system modeling and energy consumption analysis method.
Background technology
In recent years, with the needs of the development and energy-saving and emission-reduction of aluminium section bar industrial technology, energy consumption and the product to extruder
The control of product cost requires more and more higher.
, used as crucial equipment on extrusion process production line, its energy loss is serious, and extruding efficiency is low for extruder, and one is squeezed
60% or so, its energy for losing is converted into heat energy to the operating efficiency in pressure cycle.Wherein, recognized extruder energy consumption is main
It is to be the squeeze stage, the phase duration length, power consumption are big, is to realize that aluminium ingot is squeezed into the mistake of aluminum products conversion
Journey.The dynamical system of extruder is hydraulic transmission mode, and energy loss is the major power loss of hydraulic system.
At present, the energy saving research for extruder includes the parameter optimization of the reducing energy consumption of extruder appts, extrusion process
And extruded product lumber recovery etc. is improved, but solve problem is wanted, it is problem to be found first, currently also lacks sufficiently accurate skill
Art method fast and accurately finds the point to be optimized of extruder.
Content of the invention
The present invention, passes through with 10MN aluminium extruding machines as research object for the serious problem of the energy loss of extrusion process
Technological means analyzes energy flow direction, energy transition form and the energy ezpenditure of extruding machine hydraulic system, and provides corresponding reason
By energy consumption formula, contribute to the key element for summing up power consumption, make the energy saving optimizing of extruder more purposive.
The present invention proposes a kind of extruder extrusion process hydraulic system modeling and energy consumption analysis method.
Specifically, it is to solve above-mentioned technical problem, technical scheme is as follows：
Extruder extrusion process hydraulic system modeling and energy consumption analysis method, comprise the steps.
The first step, carry out extrusion process energy consumption analysis, plunger variable pump energy consumption analysis, the energy consumption analysis of inserted valve valve block and
Squeeze cylinder energy consumption analysis.
Extrusion process energy consumption analysis：The observation element related to energy conversion, energy loss, including plunger variable pump, inserts
Dress valve, master cylinder, the input, output energy consumption relation according to element, set up the power balance equation of system：Pp=ηpPpi=Pc+Pv；
Wherein, Ppi、Pp、ηpInput power, power output and the efficiency of hydraulic pump, P are represented respectivelycFor the power output of master cylinder 1, PvFor
The power loss of inserted valve valve block.
Plunger variable pump energy consumption analysis：Different leakage forms are set as follows：Pump plunger pair leakage loss qpp, Slipper coupling lets out
Leakage loss loses qps, Port Plate Pair leakage loss qpv, volume compression losses qpc；Additionally, by tripartite for mechanical efficiency loss：Pump
The Coulomb friction torque loss T that relative motion causes between inner partps, the torque loss T that bearing element friction is producedpr；In pump
The torque loss T that fluid viscous damping causespv.
The energy consumption relation of plunger variable pump sets as follows：qpa=qpt-Δqp=qpt-(qpp+qps+qpv+qpc), Tpi=Tpa+
ΔTp=Tpa+Tps+Tpr+Tpv.
The power loss formula of plunger variable pump：ΔPp=Ppi-Pp=2 π nTpi-ppaqpa；Wherein, qpa、qptIt is liquid respectively
The actual flow and theoretical delivery of pressure, Tpi、TpaThe motor of respectively hydraulic pressure supplies torque and input torque；ppaIt is expressed as plunger
The outlet pressure of variable pump；
The power loss of inserted valve valve block：The power loss of inserted valve shows as local pressure loss, when fluid enters valve
Mouthful, the area of passage at valve element diminishes rapidly, forms the opening degree and inlet-pressure of pressure reduction, wherein consumed energy, pressure reduction and valve
Power is relevant, because the power loss that pressure reduction is caused can be represented with below equation：Pv=Δ pAqvA；Wherein, Δ pAFor valve port pressure reduction, qvA
For flowing through the flow of primary valve.
Squeeze cylinder energy consumption analysis：The power loss Δ P of squeeze cylindercThe mechanical friction loss having between piston rod and piston cylinder
Pcf, because cylinder internal leakage formed volumetric loss PckAnd kinetic energy losses of potential energy P that piston rod movement is causedcr, the output of squeeze cylinder
Power is Pco, obtain the power balance equation of squeeze cylinder：Pc=Pco+ΔPc=Pco+Pcf+Pck+Pcr.
Second step：Set up Simulation Model.
Extrusion process hydraulic system modeling is emulated：The hydraulic control system model of extrusion process is set.
Plunger variable pump model is set up：The pump housing is oblique tray type axial plunger piston variable pump, including valve plate, plunger cavity volume, tiltedly
Four part of disk plunger connector and swash plate controller；Wherein, it is that valve plate arranges four ports, represents oil-in, fuel-displaced respectively
Mouthful, plunger hydraulic fluid port and cylinder body corner, its oil-in, oil-out high pressure chest respectively with valve plate, low pressure chamber be connected, cylinder body rotation
One week, plunger completed an oil suction and oil extraction；Plunger cavity volume is made up of plunger, hydraulic pressure cavity volume and leakage hole, and one end connects plunger
Hydraulic fluid port, the other end connect swash plate plunger connector；The power transmission shaft inertia input connection motor of swash plate plunger connector, works as cylinder body
Rotate, connector can drive piston reciprocation to move, and realize oil suction and oil extraction function according to output corner；Swash plate controller connects
The swash plate inertia input of swash plate plunger connector is connect, can be used to adjust swashplate angle, the discharge capacity of controlling pump.
The volumetric loss of the consideration pump housing, including plunger pair leakage, Slipper coupling leakage, it is considered to the compressibility of fluid, you can
Volume compression losses is arrived, the Port Plate Pair leakage sum of each plunger represents that at pump housing outlet the mechanical loss of the pump housing is damped by band
Rotary load torque model represent that the parameter of variable pump is expressed as follows：Plunger radial position 0.04m, diameter of plunger 28mm, post
Plug number 9, diameter of plunger gap 0.01mm, plunger, cylinder body contact length 68.4mm, system pressure 400null, maximum swash plate incline
Angle 20degree, pressure-control valve diameter 6mm, Slipper coupling flow leak 5.6e-2*dpL/min, and Port Plate Pair flow leaks 1e-2*
DpL/min, Coulomb friction torque lose 7mm, and moment of rolling friction loses 3mm, cylinder body rotary inertia 0.02Kgm2, rotating speed
2100rev/min.
Squeeze cylinder model is set up：Squeeze cylinder model is set up, the mechanical friction between consideration piston rod and piston cylinder, auxiliary respectively
The internal leakage of oil cylinder, the kinetic energy potential energy of piston rod movement and load is helped, the parameter for arranging each element is as follows：Master cylinder：Living
Plug diameter 730mm, diameter of piston rod 730mm, dead-center position 150mm, dead volume 50000cm3；Auxiliary cylinder：Piston diameter
200mm, diameter of piston rod 150mm, dead-center position 30mm, dead volume 1000cm3, module gap diameter 0.1mm is revealed, is revealed
Module gap length 100mm；Pressure ram：Gross mass 5x106kg；Load therein is obtained by collection in worksite data.
Inserted valve model is set up：Inserted valve includes valve body and valve seat, it is considered to the local pressure loss of valve, each component parameters letter
Breath is as follows：Valve latus rectum 40mm, area compare 14.3:1l, valve port diameter 38.5mm, valve element quality 0.4kg, valve element -10～
10m, spring rate 1N/mm, pretightning force 1N.
3rd step：Carry out simulation results show.
Simulation results show：Setting simulation time is 69s, and the commitment defini interval time is 0.01s, and moving model simultaneously checks emulation
As a result, the extrusion speed curve of extrusion process is obtained, by post processing, the power characteristic of each dissipative cell of extrusion process is obtained
Curve, it is contemplated that simulation result and actual result have error, the energy consumption of further analysis model.
4th step：Carry out energy consumption analysis.
Energy consumption analysis：Energy consumption analysis are carried out to the dissipative cell of model, its power consumption and power loss is analyzed, including post
The output energy consumption of plug variable pump and loss energy consumption, the local pressure loss energy consumption of inlet valve, the spill losses energy consumption of relief valve, crowded
The output energy consumption of cylinder pressure and loss energy consumption, and curve map is set up to above-mentioned energy consumption and is contrasted, quantify energy distribution.
5th step：Energy consumption improvement is carried out based on energy consumption analysis.
According to the quantization profile data for obtaining, specific aim improvement is carried out, improve energy consumption efficiency.
The invention has benefit that：
The present invention is analyzed with hydraulic system energy consumption to the operation principle of extrusion process, is set up system simulation model, is tested
The correctness of model of a syndrome, and the energy consumption curve of extrusion process dissipative cell is obtained, quantify energy distribution, contributed to drawing
Cause to extrude inefficient main energy loss, and targetedly improved, the method and simulation result are to extruder section
Can study and optimize and there is outstanding theoretical foundation and theory directive significance.
Description of the drawings
Hydraulic system sketches of the Fig. 1 for aluminium extruding machine extrusion process；Wherein, reference is as follows：1- master cylinders, 2- auxiliary oil
Cylinder, 3- pressure rams, 4- replenishing valves, 5- master cylinders enter valve, 6- relief valves, and 7- master cylinders move back valve, 8- master cylinder oil inlet and oil return valves, 9- sequence valves,
10- master cylinders return fuel tap, 11- threephase asynchronous machines, 12- plunger variable pumps, 13- safety valves；
Energy flow graphs of the Fig. 2 for the hydraulic process of aluminium extruding machine；
Fig. 3 is extrusion process Hydraulic System Simulation model；
Fig. 4 is single plunger discharge model；Wherein, 20- Port Plate Pairs leakage, 21- valve plates, 22- oil-ins, 23- oil-outs,
24- plunger hydraulic fluid ports, 25- plunger cavity volumes, 26- swash plate plunger connectors, 27- swash plate controllers, 28- pair leakage holes, 29- plungers,
30- hydraulic pressure cavity volumes；
Fig. 5 is emulation and extrusion speed comparison diagram in practice；
Fig. 6 is emulation and motor input energy consumption comparison diagram in practice；
Fig. 7 is the output energy consumption figure in energy consumption analysis；
Fig. 8 is the energy loss figure in energy consumption analysis.
Specific embodiment
Accompanying drawing being for illustration only property explanation, it is impossible to be interpreted as limitation of the present invention.
To those skilled in the art, it is to be appreciated that in accompanying drawing, some known features and its explanation may be omitted
's.
Figure of description in below in conjunction with the present invention, to invention in technical scheme be clearly and completely described,
Obviously, described embodiment is only a part of embodiment of the invention, rather than whole embodiment.In based on the present invention
Embodiment, the every other embodiment obtained under the premise of creative work is not made by those of ordinary skill in the art, all
Belong to the scope of protection of the invention.
The Hydraulic System Principle sketch of extrusion process is as shown in figure 1, squeeze cylinder is by two auxiliary cylinders 2 and a master cylinder 1
Composition, is asymmetry piston formula structure, and pressure ram 3 is fixed and connected to each piston-rod end, and the major function of auxiliary cylinder 2 has been
Into the action that moves forward and backward of master cylinder 1, and master cylinder 1 is responsible for main extruding forward motion, promotes pressure ram 3 to enter recipient and enters
Row extruding work.The oil circuit that master cylinder 1 and auxiliary cylinder 2 can be controlled by two-way plug-in valve, realizes various operating modes.
Extrusion process refers to extruding advancement stage, needs unlatching master cylinder to enter valve 5, sequence valve 9 and master cylinder oil inlet and oil return valve 8, squeezes
Before pressure, by 4 first topping up of replenishing valve, when extruding work, relief valve 6 can limit the maximum extruding in extrusion process to master cylinder 1
Power, realizes overload protection.Power section drives plunger variable pump 12 by threephase asynchronous machine 11, exports high pressure hydraulic power, and
The swashplate angle of the controllable plunger variable pump 12 of electric proportional control mode, adjusts its discharge capacity, realizes the speeds control of extrusion process.
The energy flow direction of hydraulic process is as shown in Figure 2.The hydraulic system of extruder includes dynamical element, executive component, control
Regulating element processed, auxiliary element, driving medium etc., and the functional realiey of each link is along with the consumption of energy.
In extrusion process, hydraulic system has three energy conversions：1st, motor is powered first, converts electrical energy into machinery
Energy；2 and then by hitch bar, drive hydraulic pump operating to convert mechanical energy into hydraulic energy, export hydraulic oil；3rd, finally squeeze
Hydraulic energy transfer is carried out extruding work for mechanical energy by compressing cylinder.
Conversion between multi-form energy is necessarily accompanied with energy loss, mainly includes that mechanical friction loss, volume are damaged
Mistake, spill losses, local pressure loss, kinetic energy losses of potential energy etc., and the loss of this part is transformed into heat energy, make oil liquid temperature
Raise.
Extrusion process energy consumption analysis：In the Hydraulic Power Transmission System of extrusion process, primary part observation and energy conversion, energy loss
Related element, including plunger variable pump 12, inserted valve, master cylinder 1 etc., and the input according to element, output energy consumption relation, can be with
Set up the power balance equation of system：
Pp=ηpPpi=Pc+Pv；Wherein, Ppi、Pp、ηpInput power, power output and the efficiency of hydraulic pump, P are represented respectivelyc
For the power output of master cylinder 1, PvPower loss for inserted valve valve block.
12 energy consumption analysis of plunger variable pump：The gross efficiency of plunger variable pump 12 mainly includes volumetric efficiency and mechanical efficiency.
Volumetric efficiency is that main leakage form has pump plunger shaft as the high pressure chest oil liquid leakage of hydraulic pump in the course of work is in low pressure chamber
Secondary leakage loss q of plugpp, Slipper coupling leakage loss qps, Port Plate Pair leakage loss qpv, volume compression losses qpc.Mechanical efficiency is main
Show as the loss of three parts：One is the Coulomb friction torque loss T caused because of relative motion between pump inner partps, including matching somebody with somebody
The secondary sliding friction torque of stream, sliding friction torque etc. between Slipper coupling sliding friction torque, typed ball bearing pair；Two are rubbed because of bearing element
Wipe the torque loss T for producingpr；Three is the torque loss T caused because of pump inner fluid viscous dampingpv.
The energy consumption relation of plunger variable pump is as follows：qpa=qpt-Δqp=qpt-(qpp+qps+qpv+qpc), Tpi=Tpa+ΔTp
=Tpa+Tps+Tpr+Tpv(3).
The power loss Δ P of plunger variable pumppFormula：ΔPp=Ppi-Pp=2 π nTpi-pqpa；Wherein, qpa、qptIt is respectively
The actual flow and theoretical delivery of hydraulic pressure, Tpi、TpaThe motor of respectively hydraulic pressure supplies torque and input torque.
The power loss of inserted valve valve block：Inserted valve changes valve port by the relative movement between adjusting spool and valve pocket
Actual internal area controlling the fluid flow direction of working connection, power loss is mainly shown as local pressure loss, works as fluid
Valve port is entered, the area of passage at valve element diminishes rapidly, form pressure reduction, consumed energy.The opening degree and import of pressure reduction and valve
Pressure is relevant, because of power loss P that pressure reduction is causedvAvailable below equation is represented：Pv=Δ pAqvA；Wherein, Δ pAFor valve port pressure
Difference, qvAFor flowing through the flow of primary valve.
Squeeze cylinder energy consumption analysis：Squeeze cylinder can realize the reciprocal of advance, extruding and the retrogressing of mechanism in extrusion process
Motion, flow and pressure of its |input paramete for fluid, output parameter are movement velocity and power of mechanism etc.[.During extruding work,
Hydraulic oil enters extrusion oil cylinder rodless cavity and promotes piston, overcomes Metal Deformation stress to do work, its power loss Δ PcMainly there is work
Mechanical friction loss P between stopper rod and piston cylindercf, because cylinder internal leakage formed volumetric loss PckAnd piston rod movement is made
Into kinetic energy losses of potential energy Pcr, the power output of squeeze cylinder is Pco.
The power balance equation of squeeze cylinder：Pc=Pco+ΔPc=Pco+Pcf+Pck+Pcr.
Extrusion process hydraulic system modeling is emulated：AMESim software environments are entered, calling system is provided under draft mode
Hydraulic pressure storehouse, mechanical storehouse, hydraulic component design storehouse and signal library, build simulation model, for plunger variable pump mentioned above, squeeze
The energy consumption of cylinder pressure, Cartridge inserted valve integrated block and oil circuit is used and carries out the HCD (driver (HCD (Host of console controller with power loss
Control Driver))) design, and select most simple submodel.The hydraulic control system model of extrusion process is as shown in Figure 3.
Plunger variable pump model：The pump housing is oblique tray type axial plunger piston variable pump, mainly includes valve plate 21, plunger cavity volume
25th, swash plate plunger connector 26 and swash plate controller 27, single plunger discharge model are as shown in Figure 4.Four of wherein valve plate 21
Port represents oil-in 22, oil-out 23, plunger hydraulic fluid port 24 and cylinder body corner respectively, its oil-in 22, oil-out 23 respectively with
The high pressure chest of valve plate 21, low pressure chamber are connected, and cylinder body is rotated one week, and plunger completes an oil suction and oil extraction.Plunger cavity volume 25 by
Plunger 29, hydraulic pressure cavity volume 30 and secondary leakage hole 28 are constituted, and 25 one end of plunger cavity volume connects plunger hydraulic fluid port 24, and the other end connects swash plate
Plunger connector 26.The power transmission shaft inertia input connection motor of swash plate plunger connector 26, when cylinder body is rotated, swash plate plunger connects
Connecing device 26 can drive piston reciprocation to move, and realize oil suction and oil extraction function according to output corner.Swash plate controller 27 connects
The swash plate inertia input of swash plate plunger connector 26, can be used to adjust swashplate angle, the discharge capacity of controlling pump.
The volumetric loss of the consideration pump housing, including plunger pair leakage, Slipper coupling leakage, it is considered to the compressibility of fluid, you can
Volume compression losses is arrived, the Port Plate Pair leakage sum of each plunger represents that at pump housing outlet the mechanical loss of the pump housing is damped by band
Rotary load torque model represent that the parameter of variable pump is expressed as follows：Plunger radial position 0.04m, diameter of plunger 28mm, post
Plug number 9, diameter of plunger gap 0.01mm, plunger, cylinder body contact length 68.4mm, system pressure 400Mpa, maximum swash plate incline
Angle 20degree, pressure-control valve diameter 6mm, Slipper coupling flow leak 5.6e-2*dpL/min, and Port Plate Pair flow leaks 1e-2*
DpL/min, Coulomb friction torque lose 7mm, and moment of rolling friction loses 3mm, cylinder body rotary inertia 0.02Kgm2, rotating speed
2100rev/min.
Squeeze cylinder model：Using HCD storehouses and the signal library of AMESim, structural principle and the power loss according to squeeze cylinder is built
Vertical squeeze cylinder model[4], mechanical friction respectively between consideration piston rod and piston cylinder, the internal leakage of auxiliary cylinder, piston rod fortune
Dynamic kinetic energy potential energy and load, the parameter for arranging each element are as follows：Master cylinder：Piston diameter 730mm, diameter of piston rod
730mm, dead-center position 150mm, dead volume 50000cm3；Auxiliary cylinder：Piston diameter 200mm, diameter of piston rod 150mm,
Dead-center position 30mm, dead volume 1000cm3, module gap diameter 0.1mm is revealed, module gap length 100mm is revealed；Extruding
Bar：Gross mass 5x106kg；Load therein is obtained by industry spot gathered data.
Inserted valve model：Inserted valve includes valve body and valve seat, is designed by HCD storehouses[6], it is considered to the local pressure of valve
Loss, each component parameters information are as follows：Valve latus rectum 40mm, area compare 14.3:1null, valve port diameter 38.5mm, valve element matter
Amount 0.4kg, -10～10m of valve element, spring rate 1N/mm, pretightning force 1N.
Simulation results show：Setting simulation time is 69s, and the commitment defini interval time is 0.01s, runs and check emulation knot
Really, the extrusion speed curve of extrusion process is obtained, and by post processing, the power characteristic for obtaining each dissipative cell of extrusion process is bent
Line, in order to verify that the validity of model, simulation result are contrasted with experimental data, as shown in Figure 5,6, emulation is squeezed with actual
The pressure deadline is respectively 63s and 66s, and the deadline of extruding is basically identical；Due to more satisfactoryization of emulation consideration, emulation
Speed and power input to machine although there is error, but the general trend of curve is more or less the same, can further analysis model
Energy consumption.
Energy consumption analysis：Energy consumption analysis are carried out to the dissipative cell of model, its power consumption and power loss is analyzed, including post
The output energy consumption of plug variable pump and loss energy consumption, the local pressure loss energy consumption of inlet valve, the spill losses energy consumption of relief valve, crowded
The output energy consumption of cylinder pressure is with loss energy consumption as shown in Figure 7,8.
According to simulation result above, energy ezpenditure and the damage of each dissipative cell of extrusion process can be clearly reflected
Mistake situation, by further calculating, it is known that total energy consumption is 1.17kW, and the useful work of squeeze cylinder output accounts for the 71.2% of total energy consumption,
What energy loss was maximum is that spill losses accounts for 17.1%, and the energy loss of variable pump accounts for 9.15%, and the energy loss of squeeze cylinder is accounted for
2.1%, unknown losses accounts for 0.45%.
Carry out energy consumption improvement：According to the quantization profile data for obtaining, specific aim improvement is carried out, improve energy consumption efficiency.
The operation principle and hydraulic system energy consumption of extrusion process are analyzed, on AMESim platforms, set up system emulation
Model, demonstrates the correctness of model.And the energy consumption curve of extrusion process dissipative cell is obtained, quantify energy distribution, drawn
Crowded overflow energy loss is to cause to extrude inefficient main cause, can reduce relief valve spillway discharge or adopt accumulator
Reclaim the energy of loss；Next to that variable pump is inefficient, other variable-flow kinds of drive can be adopted to reduce system energy
Consumption, the research method and simulation result have certain theoretical foundation to extruder energy saving research.
In sum, as embodiment of the present invention content, and obviously embodiments of the present invention are not limited to which can
According to different application environment, corresponding demand is realized using the feature of the present invention.
Claims (5)
1. extruder extrusion process hydraulic system modeling and energy consumption analysis method, comprise the steps：
The first step：Carry out extrusion process energy consumption analysis, plunger variable pump energy consumption analysis, inserted valve valve block energy consumption analysis and squeeze cylinder
Energy consumption analysis；
Extrusion process energy consumption analysis：Related to energy conversion, the energy loss element of observation, including plunger variable pump, inserted valve,
Master cylinder, the input, output energy consumption relation according to element, sets up the power balance equation of system：Pp=ηpPpi=Pc+Pv；Wherein,
Ppi、Pp、ηpInput power, power output and the efficiency of hydraulic pump, P are represented respectivelycFor the power output of master cylinder (1), PvFor inserting
The power loss of valve valve block；
Plunger variable pump energy consumption analysis：Different leakage forms are set as follows：Pump plunger pair leakage loss qpp, Slipper coupling leakage damage
Lose qps, Port Plate Pair leakage loss qpv, volume compression losses qpc；Additionally, by tripartite for mechanical efficiency loss：Inside pump
The Coulomb friction torque loss T that relative motion causes between partps, the torque loss T that bearing element friction is producedpr；Pump inner fluid
The torque loss T that viscous damping causespv；
The energy consumption relation of plunger variable pump sets as follows：qpa=qpt-Δqp=qpt-(qpp+qps+qpv+qpc), Tpi=Tpa+ΔTp
=Tpa+Tps+Tpr+Tpv；
The power loss formula of plunger variable pump：ΔPp=Ppi-Pp=2 π nTpi-ppaqpa；Wherein, qpa、qptIt is hydraulic pressure respectively
Actual flow and theoretical delivery, Tpi、TpaThe motor of respectively hydraulic pressure supplies torque and input torque；ppaIt is expressed as plunger variable
The outlet pressure of pump；
The power loss of inserted valve valve block：The power loss of inserted valve shows as local pressure loss, when fluid enters valve port,
Area of passage at valve element diminishes rapidly, forms pressure reduction, and consumed energy, wherein pressure reduction are had with the opening degree and inlet pressure of valve
Close, because the power loss that pressure reduction is caused can be represented with below equation：Pv=Δ pAqvA；Wherein, Δ pAFor valve port pressure reduction, qvAFor stream
Flow through primary valve；
Squeeze cylinder energy consumption analysis：The power loss Δ P of squeeze cylindercMechanical friction loss P having between piston rod and piston cylindercf、
Because of the volumetric loss P that cylinder internal leakage is formedckAnd kinetic energy losses of potential energy P that piston rod movement is causedcr, the output work of squeeze cylinder
Rate is Pco, obtain the power balance equation of squeeze cylinder：Pc=Pco+ΔPc=Pco+Pcf+Pck+Pcr；
Second step：Set up Simulation Model；
Extrusion process hydraulic system modeling is emulated：The hydraulic control system model of extrusion process is set；
Plunger variable pump model is set up；
Squeeze cylinder model is set up；
Inserted valve model is set up；
3rd step：Carry out simulation results show；
Simulation results show：Setting simulation time is 69s, and the commitment defini interval time is 0.01s, and moving model simultaneously checks emulation knot
Really, the extrusion speed curve of extrusion process is obtained, and by processing, the power characteristic for obtaining each dissipative cell of extrusion process is bent
Line, the then energy consumption of further analysis model；
4th step：Carry out energy consumption analysis；
Energy consumption analysis：Energy consumption analysis are carried out to the dissipative cell of model, its power consumption and power loss is analyzed, is become including plunger
The output energy consumption of amount pump and loss energy consumption, the local pressure loss energy consumption of inlet valve, the spill losses energy consumption of relief valve, squeeze cylinder
Output energy consumption and loss energy consumption, and curve map is set up to above-mentioned energy consumption and is contrasted, quantify energy distribution；
5th step：Energy consumption improvement is carried out based on energy consumption analysis；Carry out energy consumption improvement：According to the quantization energy distribution data for obtaining,
Specific aim improvement is carried out, energy consumption efficiency is improved.
2. extruder extrusion process hydraulic system modeling according to claim 1 and energy consumption analysis method, it is characterised in that
In described second step, plunger variable pump model foundation is carried out：The pump housing is oblique tray type axial plunger piston variable pump, including valve plate,
Plunger cavity volume, four part of swash plate plunger connector and swash plate controller；Wherein, it is that valve plate arranges four ports, represents respectively
Oil-in, oil-out, plunger hydraulic fluid port and cylinder body corner, its oil-in, oil-out high pressure chest respectively with valve plate, low pressure chamber phase
Even, cylinder body is rotated one week, and plunger completes an oil suction and oil extraction；Plunger cavity volume is made up of plunger, hydraulic pressure cavity volume and leakage hole, and one
End connection plunger hydraulic fluid port, the other end connect swash plate plunger connector；The power transmission shaft inertia input connection of swash plate plunger connector
Motor, when cylinder body is rotated, swash plate plunger connector can drive piston reciprocation to move, and realize oil suction and row according to output corner
Oily function；Swash plate controller connects the swash plate inertia input of swash plate plunger connector, can be used to adjust swashplate angle, controlling pump
Discharge capacity.
3. extruder extrusion process hydraulic system modeling according to claim 2 and energy consumption analysis method, it is characterised in that
The parameter of the variable pump is expressed as follows：Plunger radial position 0.04m, diameter of plunger 28mm, plunger number 9, between diameter of plunger
Gap 0.01mm, plunger, cylinder body contact length 68.4mm, system pressure 400Mpa, maximum swashplate angle 20degree, Stress control
Valve diameter 6mm, Slipper coupling flow leak 5.6e-2*dpL/min, and Port Plate Pair flow leaks 1e-2*dpL/min, Coulomb friction power
Square loses 7mm, and moment of rolling friction loses 3mm, cylinder body rotary inertia 0.02Kgm2, rotating speed 2100rev/min；Wherein, e is certainly
Truth of a matter e of right logarithm, dp is differential.
4. extruder extrusion process hydraulic system modeling according to claim 1 and energy consumption analysis method, it is characterised in that
In described second step, squeeze cylinder model foundation is carried out：The parameter for arranging each element is as follows：Master cylinder：Piston diameter
730mm, diameter of piston rod 730mm, dead-center position 150mm, dead volume 50000cm3；Auxiliary cylinder：Piston diameter 200mm,
Diameter of piston rod 150mm, dead-center position 30mm, dead volume 1000cm3, module gap diameter 0.1mm is revealed, module seam is revealed
Gap length 100mm；Pressure ram：Gross mass 5x106kg；Load therein is obtained by collection in worksite data.
5. extruder extrusion process hydraulic system modeling according to claim 1 and energy consumption analysis method, it is characterised in that
In described second step, inserted valve model foundation is carried out：Each component parameters information is as follows：Valve latus rectum 40mm, area ratio
14.3:1, valve port diameter 38.5mm, valve element quality 0.4kg, -10～10m of valve element, spring rate 1N/mm, pretightning force 1N.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510208297.5A CN104785568B (en) | 2015-04-28 | 2015-04-28 | Extruder extrusion process hydraulic system modeling and energy consumption analysis method |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510208297.5A CN104785568B (en) | 2015-04-28 | 2015-04-28 | Extruder extrusion process hydraulic system modeling and energy consumption analysis method |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN104785568A CN104785568A (en) | 2015-07-22 |
| CN104785568B true CN104785568B (en) | 2017-03-15 |
Family
ID=53551010
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201510208297.5A Active CN104785568B (en) | 2015-04-28 | 2015-04-28 | Extruder extrusion process hydraulic system modeling and energy consumption analysis method |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN104785568B (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112161803B (en) * | 2020-09-16 | 2022-09-13 | 上海市轴承技术研究所 | Rolling bearing life-span energy consumption testing machine under combined load |
Family Cites Families (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4793954A (en) * | 1987-08-17 | 1988-12-27 | The B. F. Goodrich Company | Shear processing thermoplastics in the presence of ultrasonic vibration |
| FR2821175A1 (en) * | 2001-02-19 | 2002-08-23 | Solvay | METHOD FOR REGULATING A PROPERTY OF A PRODUCT RESULTING FROM A CHEMICAL TRANSFORMATION |
| CN101712207A (en) * | 2009-09-08 | 2010-05-26 | 广东工业大学 | High performance and energy-saving double-acting hydrostatic press driven by servo motor |
| CN103745279B (en) * | 2014-01-24 | 2016-04-27 | 广东工业大学 | A kind of energy consumption method for monitoring abnormality and device |
-
2015
- 2015-04-28 CN CN201510208297.5A patent/CN104785568B/en active Active
Also Published As
| Publication number | Publication date |
|---|---|
| CN104785568A (en) | 2015-07-22 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN107269609B (en) | Combining hydraulic system in load-sensitive valve | |
| CN100589968C (en) | Hydraulic control system of multi-point driving large hydraulic press | |
| CN108386398B (en) | Pump control hydraulic system for controlling position of compound hydraulic cylinder | |
| CN102582098A (en) | Dual-station pneumatic stamping machine | |
| CN105570240A (en) | Direct-driven hydropress electro-hydraulic servo system | |
| CN202946472U (en) | Small-flow fast-moving oil cylinder | |
| CN104785568B (en) | Extruder extrusion process hydraulic system modeling and energy consumption analysis method | |
| Yan et al. | Energy optimization of main hydraulic system in a forging press by simulation and experimental methods | |
| CN103994042B (en) | Piston type hydraulic pump with crank connecting rod structure | |
| CN104564862B (en) | A kind of combined pump control cylinder electrohydraulic control system | |
| CN103670999B (en) | A kind of piston valving double-action linear electric motor drive reciprocating pump | |
| CN102179950A (en) | Novel oil press | |
| CN104454489A (en) | Integrated compact type constant power variable device | |
| CN203335520U (en) | Hydraulic cylinder with oil hole sets formed in cylinder barrel side wall | |
| CN115795723B (en) | Optimal design method and system for high-efficiency low-pulsation cycloid motor flow distribution system | |
| CN105864620B (en) | Three-stage becomes displacement oil pump | |
| CN108252967A (en) | A kind of Hydraulic system and control method for being used to control energy-saving pump | |
| CN102536924A (en) | Single-hydraulic cylinder single-acting hydraulic system of supercharger | |
| CN106321535A (en) | Hydraulic unit for mutually using potential energy in pairwise mode | |
| CN106128813B (en) | Portable hydraulic operating mechanism and the high-tension switch gear for using the operating mechanism | |
| CN201535282U (en) | Double-tapping large-travel oil cylinder | |
| CN212376802U (en) | High viscosity oil injection pump | |
| CN205991041U (en) | A kind of horizontal movement control system of rock drill | |
| CN204419540U (en) | Integrated compact type variable displacement with constant power device | |
| CN203627121U (en) | Reciprocated plunger pump driven by plunger assignment double-acting linear motor |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| EXSB | Decision made by sipo to initiate substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| TR01 | Transfer of patent right | ||
| TR01 | Transfer of patent right |
Effective date of registration: 20170426 Address after: 510006 Panyu District, Guangzhou, Guangzhou University,, West Ring Road, No. 100 Co-patentee after: Foshan Dingxing Technology Co., Ltd. Patentee after: Guangdong University of Technology Address before: 510006 Dongfeng Road, Guangzhou, Guangdong, No. 729, No. Patentee before: Guangdong University of Technology |