CN107420378A - A kind of hydraulic press drive system matches power save mode - Google Patents
A kind of hydraulic press drive system matches power save mode Download PDFInfo
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- CN107420378A CN107420378A CN201710507911.7A CN201710507911A CN107420378A CN 107420378 A CN107420378 A CN 107420378A CN 201710507911 A CN201710507911 A CN 201710507911A CN 107420378 A CN107420378 A CN 107420378A
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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
- F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B30—PRESSES
- B30B—PRESSES IN GENERAL
- B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
- B30B15/16—Control arrangements for fluid-driven presses
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B30—PRESSES
- B30B—PRESSES IN GENERAL
- B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
- B30B15/16—Control arrangements for fluid-driven presses
- B30B15/166—Electrical control arrangements
-
- 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
- F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
- F15B21/08—Servomotor systems incorporating electrically operated control means
- F15B21/087—Control strategy, e.g. with block diagram
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/205—Systems with pumps
- F15B2211/20507—Type of prime mover
- F15B2211/20515—Electric motor
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/205—Systems with pumps
- F15B2211/2053—Type of pump
- F15B2211/20546—Type of pump variable capacity
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/205—Systems with pumps
- F15B2211/20576—Systems with pumps with multiple pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/265—Control of multiple pressure sources
- F15B2211/2656—Control of multiple pressure sources by control of the pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/265—Control of multiple pressure sources
- F15B2211/2658—Control of multiple pressure sources by control of the prime movers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/80—Other types of control related to particular problems or conditions
- F15B2211/88—Control measures for saving energy
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Analytical Chemistry (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- General Engineering & Computer Science (AREA)
- Fluid-Pressure Circuits (AREA)
- Press Drives And Press Lines (AREA)
Abstract
The invention discloses a kind of hydraulic press drive system to match power save mode, it is characterized in that design corresponds the drive system of composition with the higher multiple electric-motor pumps of load matched degree in the hydraulic press work period；According to the pressure in each stage in the hydraulic press work period and duration demand, flow under the pressure with reference to needed for all variable pumps in selected pump set in each working stage of hydraulic press, the combination of multiple variable pumps is selected, makes the composite index for being in unloading condition variable pump in the work period minimum；According to selected variable pump, matching motor is selected, each motor is at least in the load factor scope of setting in two working stages.Wherein, for the system pressure relatively low stage, the load factor of asynchronous motor is improved by lifting variable pump operating pressure, further reduces its energy loss.The present invention can effectively reduce drive system total rated power, reduce the energy consumption of one work period of hydraulic press, improve more motor pump group hydraulic press energy efficiencies, reduce use cost.
Description
Technical field
The present invention relates to a kind of hydraulic press power-economizing method, more particularly to a kind of hydraulic press drive system matching power save mode,
For improving hydraulic press drive system and the matching degree of load, the energy efficiency of hydraulic press drive system is lifted.
Background technology
Forming has the advantages that production efficiency is high, crudy is good, saves material, is widely used in production.Liquid
The advantages of press is with its stable drive, control is simple, large carrying capacity, turn into the important type of belt drive of Forming Equipments.
But it is limited to the load characteristic and driving feature of hydroforming equipment, the drive system rated power of existing hydraulic press selects
It is excessive, the energy loss for causing hydroforming to be equipped is high, and efficiency is even as low as less than 50%.Hydraulic press is in a work period
In, drive system is less than 30% in the efficiency of fast drop, slow drop, off-load and standby phase, and returns to and return stage hydraulic press slowly
Drive system and load matched effect it is also poor；And compacting process hydraulic press drive-train efficiency is up to 85% or so.Volume
Determine the excessive drive system of power add fast drop, slow drop, off-load, slow time, return to energy consumption with standby phase, cause hydraulic press
A work period in have lost substantial amounts of energy.
The content of the invention
The present invention is to avoid the weak point present in above-mentioned prior art, there is provided a kind of hydraulic press drive system matching
Power save mode, with design and the higher drive system of hydraulic press workload matching degree, reduce the general power of drive system, carry
The energy efficiency of hydraulic press is risen, reduces the energy loss in one work period of hydraulic press.
The present invention adopts the following technical scheme that to solve technical problem：
The characteristics of hydraulic press drive system of the present invention matching power save mode is：
Corresponded by asynchronous motor and variable pump and form driver element, the hydraulic press drive system is driven by m groups
Moving cell is collectively as the power source of hydraulic press, and m is not less than 2；The pump set element number of available variable pump is set as n,
The correlation of variable pump output flow and pressure in the pump set and hydraulic press respectively flow needed for action and pressure it is related
Property is consistent；
One work period of the hydraulic press is divided into r working stage, the r working stage and hydraulic press
Variant action corresponds；It in pressure needed for jth working stage is p to set the hydraulic pressj, when a length of tj, piston displacement be
lj, oil suction chamber piston area Aj, j=1,2 ..., r；
Definition：K-th of variable pump in n variable pump is in pressure p needed for hydraulic press jth working stagejUnder flow be qk
(pj), k=1,2 ..., n；For the pump set, the quantity for choosing k-th of variable pump is set as ak, akBe comprising zero it is just whole
Number, and meet：
According to the required pressure and duration demand of each working stage in one work period of hydraulic press, for m variable pump
Selection should cause the composite index T of all variable pumps for being in unloading condition in a work period be it is minimum,
M0jTo be in the product of the flow of each variable pump of unloading condition and off-load duration in the hydraulic press jth working stage；
For T ≠ 0, it is desirable to which m variable pump for forming hydraulic press drive system is full in a work period of hydraulic press
The traffic demand that sufficient formula (1) is characterized：
And meet the synthesis of all variable pumps for being in unloading condition in one work period of hydraulic press that formula (2) is characterized
Index T is minimum：
For the m variable pump chosen, each asynchronous motor of corresponding selection as follows：
Definition：I-th of variable pump is p in pressure needed for hydraulic press jth working stage in m variable pumpjWhen flow
For qi(pj), then in jth working stage, the power output P of i-th of variable pumpi(pj) be：
Pi(pj)=qi(pj)×pj/ 60,
In jth working stage, the load factor β of i-th of the motor to match with i-th of variable pumpi(pj) be：
βi(pj)=Pi(pj)/(ηpi(pj)×PNi),
ηPi(pj) represent that i-th of variable pump is in the efficiency of jth working stage, P in hydraulic press drive systemNiChoose
The rated power of i-th of variable pump in m variable pump；
The load factor of each at least two working stages of asynchronous motor in the hydraulic press drive system is set to set
Fixed section, it is real to cause efficiency of each asynchronous motor at least in two working stages not less than the efficiency value of setting
Existing high-efficiency operation.
The characteristics of hydraulic press drive system matching power save mode of the present invention, lies also in：
If T=0, show to be not located in each working stage of the hydraulic press drive system in a work period
The variable pump of unloading condition, its composite index T are minimum, then m variable pump for requiring to form hydraulic press drive system is in hydraulic pressure
Meet the traffic demand that formula (3) is characterized in one work period of machine：
The total rated power P of the variable pump for the composition hydraulic press drive system that formula (4) is characterized is required to meet simultaneouslyNTFor most
It is small：
PNkRepresent the rated power of k-th of variable pump in the pump set.
The characteristics of hydraulic press drive system matching power save mode of the present invention, lies also in：
It is if using variable displacement with constant power pump in the hydraulic press drive system, then unified for the hydraulic press drivetrain
In the operating pressure relatively low stage in the individual work period, the load factor of asynchronous motor is improved by lifting variable pump operating pressure,
To reduce energy loss.
Compared with the prior art, the present invention has the beneficial effect that：
1st, the present invention is optimized the combination of electric-motor pump in drive system, made by the working condition according to needed for hydraulic press
The composite index minimum of unloading condition variable pump is in one work period, each motor is at least two working stages
In the range of the higher load factor of energy efficiency, the total rated power of drive system is reduced, improves hydraulic press in a work
Make the energy efficiency in the cycle；
2nd, the present invention drives hydraulic press by multiple threephase asynchronouses, reduces system in the fallback period
Input improves drive system and the matching degree of load with exporting unmatched degree；
3rd, the present invention improves the load factor of motor by way of improving pressure, and it is relatively low to further reduce hydraulic press pressure
Stage energy loss.
Brief description of the drawings
Fig. 1 is hydraulic press system schematic diagram；
Fig. 2 is the flow chart that hydraulic press drive system of the present invention matches power save mode；
Fig. 3 is that the general power of input-driven system when the pump of hydraulic press is variable displacement with constant power pump is bent with pump work pressure change
Line chart.
Embodiment
Hydraulic press drive system matching power save mode is in the present embodiment：
Form driver element as shown in figure 1, being corresponded by asynchronous motor and variable pump, hydraulic press drive system be by
M groups driver element is collectively as the power source of hydraulic press, and m is not less than 2；Set the pump set element number of available variable pump
For n, the correlation of variable pump output flow and pressure in pump set and hydraulic press respectively flow needed for action and pressure it is related
Property is consistent.
One work period of hydraulic press is divided into r working stage, r working stage and the variant of hydraulic press move
Correspond；Setting hydraulic press is p in pressure needed for jth working stagej, when a length of tj, piston displacement lj, oil suction chamber live
Fill in area Aj, j=1,2 ..., r.
Definition：K-th of variable pump in n variable pump is in pressure p needed for hydraulic press jth working stagejUnder flow be qk
(pj), k=1,2 ..., n；For pump set, the quantity for choosing k-th of variable pump is set as ak, akBe include zero positive integer,
And meet：
According to the required pressure and duration demand of each working stage in one work period of hydraulic press, for m variable pump
Selection should cause the composite index T of all variable pumps for being in unloading condition in a work period be it is minimum,
M0jTo be in the product of the flow of each variable pump of unloading condition and off-load duration in hydraulic press jth working stage.
As shown in Fig. 2 for T ≠ 0, it is desirable to form a work of the m variable pump in hydraulic press of hydraulic press drive system
Make to meet the traffic demand that formula (1) is characterized in the cycle：
And meet the synthesis of all variable pumps for being in unloading condition in one work period of hydraulic press that formula (2) is characterized
Index T is minimum：
For the m variable pump chosen, each asynchronous motor of corresponding selection as follows：
Definition：I-th of variable pump is p in pressure needed for hydraulic press jth working stage in m variable pumpjWhen flow
For qi(pj), then in jth working stage, the power output P of i-th of variable pumpi(pj) be：
Pi(pj)=qi(pj)×pj/60；
In jth working stage, the load factor β of i-th of the motor to match with i-th of variable pumpi(pj) be：
βi(pj)=Pi(pj)/(ηpi(pj)×PNi),
ηPi(pj) represent that i-th of variable pump is each variable pump in the efficiency of jth working stage in hydraulic press drive system
Corresponding point in the performance curve of pressure-flow given when dispatching from the factory, PNiFor i-th variable pump in m variable pump having chosen
Rated power.
The load factor of at least two working stages of each asynchronous motor in hydraulic press drive system is set in setting
Section, to cause efficiency of each asynchronous motor at least in two working stages not less than the efficiency value of setting, to realize high
Efficiency is run.Calculate selected each asynchronous motor is in r load factor, judgement corresponding to r working stage of hydraulic press
It is no to meet condition：The load factor of at least two working stages of each asynchronous motor is in the section of setting, if satisfied, then completing
The selection of m asynchronous motor, if not satisfied, asynchronous motor is then reselected, until meeting condition.
If T=0, show to be not located in off-load in each working stage of the hydraulic press drive system in a work period
The variable pump of state, its composite index T are minimum, then m variable pump for requiring to form hydraulic press drive system is in hydraulic press
Meet the traffic demand that formula (3) is characterized in one work period：
The total rated power P of the variable pump for the composition hydraulic press drive system that formula (4) is characterized is required to meet simultaneouslyNTFor most
It is small：
PNkRepresent the rated power of k-th of variable pump in pump set.
As shown in figure 3, for hydraulic press drive system matching power save mode in the present invention, if in hydraulic press drive system
It is middle to use variable displacement with constant power pump, then for the relatively low stage of operating pressure in the unified work period of hydraulic press drivetrain, pass through
The load factor that variable pump operating pressure improves asynchronous motor is lifted, to reduce energy loss.Variable displacement with constant power pump refers to：Work as change
Amount pump work pressure is in one section of relatively low scope (a, c), and the output flow of variable pump is constant, and input hydraulic pressure machine is total
Power reduces with the increase of pressure in the pressure limit (a, b), until be minimum in b points, in pressure limit (b, c) with
The reduction of pressure and increase；Such as：When hydraulic press jth working stage pressure between (a, b) when, increase hydraulic press exist
The pressure of jth working stage, it is allowed to level off to b point pressures, now the variable pump output flow of hydraulic press drive system is constant, bears
Carry and increase, the efficiency of the load factor of the asynchronous motor of hydraulic press drive system and the variable pump of hydraulic press drive system all increases
Greatly, the gross efficiency increase of hydraulic press drive system, meets to make input hydraulic pressure machine while hydraulic press jth working stage job requirement
General power reduce, reduce energy consumption of the hydraulic press in jth working stage.
By taking the hydraulic press of the quick hydraulic sheet metal drawing press of certain company as an example, the hydraulic press has 7 in a work period
Working stage, it is respectively：Fast depression of order section, slow depression of order section, pressing stage, off-load stage, the slowly stage of returning to, time stage and standby rank
Section.Its drive system includes：Five groups of one-to-one M1Type asynchronous motor and P1Type variable pump, and one group of M2The asynchronous electricity of type
Motivation and P2Type and P3Type variable pump.Its drive system total rated power is 465kW, wherein P3The main function of type variable pump is
Open and close the hydraulic control one-way valve between replenishing valve and hydraulic cylinder, its hydraulic cylinder include the identical piston hydraulic cylinder of two parameters and
One plunger piston fluid pressure cylinder.The hydraulic press parameter request is as shown in table 1.
Table 1
| Hydraulic press acts | Fast drop | Slow drop | Compacting | Off-load | Return to | It is slow to return | It is standby |
| Working stage j | 1 | 2 | 3 | 4 | 5 | 6 | 7 |
| Time (s) | 0-2.3 | 2.3-4 | 4-7.3 | 7.3-10.1 | 10.1-12.7 | 12.7-13.8 | 13.8-25 |
| Inlet pressure (MPa) | 0.1 | 0.1 | 19 | 0 | 6.43 | 6.43 | 0 |
| Oil suction chamber flow (L/min) | 18000 | 414 | 920 | 0 | 1730 | 430 | 0 |
Then with driving of the hydraulic press drive system matching power save mode of the present invention to the quick hydraulic sheet metal drawing press
System re-starts apolegamy, then it is to correspond structure by asynchronous motor and variable pump by m groups to set the hydraulic press drive system
Into driver element collectively as hydraulic press power source, m be not less than 2.As shown in Table 1, the flow and pressure needed for the hydraulic press
The correlation of power is negative correlation, and the flow of PV series axial plunger type variable capacity pumps and the correlation of pressure are also negative correlation, then
The selected PV series axial plunger type variable capacity pump comprising 54 variable pumps is pump set, then n=54.
One work period of the hydraulic press is divided into 7 stages, the action different from 7 of hydraulic press of this 7 stages
Correspond；It in pressure needed for jth working stage is p to set the hydraulic pressj, when a length of tj, displacement lj, oil suction chamber piston area
Product Aj, j=1,2 ..., 7.
K-th of variable pump in 54 variable pumps is defined in pressure p needed for hydraulic press jth working stagejUnder flow be qk
(pj), k=1,2 ..., 54；For said pump set, the quantity for choosing k-th of variable pump is set as ak, akIt is to include zero just
Integer, and meet：
During the quick thin plate stretch forming of the hydraulic press, hydraulic press drive system in the 4th and the 7th working stage all
In unloading condition, then in one work period of the hydraulic press all variable pumps for being in unloading condition composite index T ≠ 0,
Therefore the combination of m variable pump is selected to make the composite index of all variable pumps for being in unloading condition in a work period most
It is small.The flow of 1st working stage of the hydraulic press is mainly provided by replenishing valve, and the 1st and the 2nd working stage is mainly in cunning
Completed under the gravity of block, therefore the drive system of the hydraulic press can be equal to system in the 1st and the 2nd working stage and unloaded
Lotus, and drive system in the 4th and the 7th working stage all in idling conditions, therefore select drive system variable pump when master
Consider flow, pressure and the time requirement of the working stage of the 3rd, the 5th and the 6th.In the oil-feed of the working stage of the 3rd, the 5th and the 6th
Mouth pressure is larger, flow is smaller, can ignore the pressure drop of this process and the energy consumption as caused by pressure drop, can be according to the parameter of table 1
The combination of m variable pump is selected in selected pump set, and requires that this forms m variable pump of hydraulic press drive system in liquid
Meet traffic requirement in one work period of press：
b1×q2(pj)+b2×q2(pj)+…+b54×q54(pj)≥Aj×lj/tj,
And the composite index T of all variable pumps for being in unloading condition is minimum：
It is as shown in table 2 then to choose result.
Table 2
Obtained by table 2, m=8, selected 8 variable pumps are satisfied by the flow that the working stage of the 3rd, the 5th and the 6th provides
The requirement of the hydraulic press, wherein P5Type variable pump only plays the hydraulic control opened between replenishing valve and hydraulic cylinder in the 5th working stage
The effect of check valve, the flow of backhaul is not provided for hydraulic press, in the Opening pressure of the working stage hydraulic control one-way valve of hydraulic press the 5th
For 12MPa, now P5The flow of type variable pump is 130L/min.And the total rated power of 8 hydraulic pumps is 365kW, than original
Reduce 100kW, and the combination of this 8 variable pumps makes the hydraulic press be in unloading condition pump in whole forming process
Composite index is minimum.
For 8 variable pumps chosen, one-to-one asynchronous motor therewith is selected.According to 8 changes chosen
The pressure needed for 7 working stages of the performance curve of pressure-flow and hydraulic press of pump is measured, draws each variable pump in 7 works
Make the output flow and power output in stage, pressure-efficiency characteristic and institute further according to 8 variable pumps chosen
The asynchronous motor one-to-one therewith chosen, draws load factor of each motor in 7 working stages.Selected is each
Asynchronous electric is confidential to meet condition：The load factor of at least two working stages is otherwise chosen again in section [0.4,1.0]
Asynchronous motor, until meeting condition so that each efficiency of the asynchronous motor at least in two working stages is not less than
80%, realize high-efficiency operation.8 three-phase AC asynchronous motors then selected are as shown in table 3.
Table 3
| Model | M3 | M4 | M5 | M6 |
| Matching variable pump | P4 | P5 | P6 | P7 |
| Rated power (kW) | 75 | 45 | 37 | 22 |
| Quantity (individual) | 2 | 1 | 4 | 1 |
| 3rd stage load factor | 0.87 | 0.77 | 0.91 | 0.81 |
| 3rd stage efficiency | 0.93 | 0.92 | 0.92 | 0.92 |
| 5th stage load factor | 0.90 | 0.58 | 0.45 | 0.76 |
| 5th stage efficiency | 0.93 | 0.93 | 0.91 | 0.92 |
It can be obtained by table 3, the threephase asynchronous total rated power of selection is 365kW, and each motor is in the 3rd and
The load factor of 5 working stages is in section [0.4,1.0], and efficiency is all not less than 90%, meets this matching power save mode
It is required that.
The hydraulic press drive system chosen according to drive system matching power save mode meets the normal work of the hydraulic press
Needing, the total rated power of former drive system is 465kW, and what the hydraulic press drive system matching power save mode of the present invention was chosen
The total rated power of drive system is 365kW, reduces 21.51%.And in hydraulic press the 1st, the 2nd, the 4th, the 7th this four works
Making the idle running energy consumption in stage reduces 21.51%；It is similar to the efficiency of former drive system in the 3rd working stage its efficiency, at this
One working stage energy consumption is approximate to maintain an equal level；In the 5th working stage, drive system and load matched degree are improved, improves driving
The efficiency of system, big energy is saved, reduced idle capacity in the 6th working stage.Then in a job of the hydraulic press
In cycle, for the hydraulic press drive system according to this matching power save mode selection compared with former drive system, its energy efficiency is higher.
In addition, this 8 incomplete same electric-motor pumps can adapt to a variety of loads with appropriately combined, and load is set to match journey with drive system
Degree is higher, improves the flexibility of whole hydraulic press.
Claims (3)
1. a kind of hydraulic press drive system matches power save mode, it is characterized in that：
Corresponded by asynchronous motor and variable pump and form driver element, the hydraulic press drive system is to drive list by m groups
Member is collectively as the power source of hydraulic press, and m is not less than 2；The pump set element number of available variable pump is set as n, it is described
The correlation of variable pump output flow and pressure in pump set and the correlation phase of flow and pressure needed for each action of hydraulic press
Unanimously；
One work period of the hydraulic press is divided into r working stage, the r working stage and hydraulic press it is each not
Corresponded with action；It in pressure needed for jth working stage is p to set the hydraulic pressj, when a length of tj, piston displacement lj、
Oil suction chamber piston area Aj, j=1,2 ..., r；
Definition：K-th of variable pump in n variable pump is in pressure p needed for hydraulic press jth working stagejUnder flow be qk
(pj), k=1,2 ..., n；For the pump set, the quantity for choosing k-th of variable pump is set as ak, akBe comprising zero it is just whole
Number, and meet：
According to the required pressure and duration demand of each working stage in one work period of hydraulic press, the choosing for m variable pump
Select should so that in a work period all variable pumps for being in unloading condition composite index T for minimum,M0j
To be in the product of the flow of each variable pump of unloading condition and off-load duration in the hydraulic press jth working stage；
For T ≠ 0, it is desirable to which m variable pump for forming hydraulic press drive system meets formula in a work period of hydraulic press
(1) traffic demand characterized：
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<munderover>
<mi>&Sigma;</mi>
<mrow>
<mi>j</mi>
<mo>=</mo>
<mn>1</mn>
</mrow>
<mi>r</mi>
</munderover>
<msub>
<mi>M</mi>
<mrow>
<mn>0</mn>
<mi>j</mi>
</mrow>
</msub>
<mo>)</mo>
</mrow>
<mrow>
<mi>m</mi>
<mi>i</mi>
<mi>n</mi>
</mrow>
</msub>
<mo>-</mo>
<mo>-</mo>
<mo>-</mo>
<mrow>
<mo>(</mo>
<mn>2</mn>
<mo>)</mo>
</mrow>
<mo>,</mo>
</mrow>
For the m variable pump chosen, each asynchronous motor of corresponding selection as follows：
Definition：I-th of variable pump is p in pressure needed for hydraulic press jth working stage in m variable pumpjWhen flow be qi
(pj), then in jth working stage, the power output P of i-th of variable pumpi(pj) be：
Pi(pj)=qi(pj)×pj/ 60,
In jth working stage, the load factor β of i-th of the motor to match with i-th of variable pumpi(pj) be：
βi(pj)=Pi(pj)/(ηpi(pj)×PNi),
ηPi(pj) represent that i-th of variable pump is in the efficiency of jth working stage, P in hydraulic press drive systemNiFor m chosen
The rated power of i-th of variable pump in variable pump；
The load factor of each at least two working stages of asynchronous motor in the hydraulic press drive system is set in setting
Section, to cause efficiency of each asynchronous motor at least in two working stages not less than the efficiency value of setting, to realize high
Efficiency is run.
2. hydraulic press drive system according to claim 1 matches power save mode, it is characterized in that：
If T=0, show to be not located in off-load in each working stage of the hydraulic press drive system in a work period
The variable pump of state, its composite index T are minimum, then m variable pump for requiring to form hydraulic press drive system is in hydraulic press
Meet the traffic demand that formula (3) is characterized in one work period：
<mrow>
<munderover>
<mo>&Sigma;</mo>
<mrow>
<mi>k</mi>
<mo>=</mo>
<mn>1</mn>
</mrow>
<mi>n</mi>
</munderover>
<mrow>
<mo>(</mo>
<msub>
<mi>a</mi>
<mi>k</mi>
</msub>
<mo>&times;</mo>
<msub>
<mi>q</mi>
<mi>k</mi>
</msub>
<mo>(</mo>
<msub>
<mi>p</mi>
<mi>j</mi>
</msub>
<mo>)</mo>
<mo>)</mo>
</mrow>
<mo>=</mo>
<msub>
<mi>A</mi>
<mi>j</mi>
</msub>
<mo>&times;</mo>
<msub>
<mi>l</mi>
<mi>j</mi>
</msub>
<mo>/</mo>
<msub>
<mi>t</mi>
<mi>j</mi>
</msub>
<mo>-</mo>
<mo>-</mo>
<mo>-</mo>
<mrow>
<mo>(</mo>
<mn>3</mn>
<mo>)</mo>
</mrow>
<mo>,</mo>
</mrow>
The total rated power P of the variable pump for the composition hydraulic press drive system that formula (4) is characterized is required to meet simultaneouslyNTFor minimum：
<mrow>
<msub>
<mi>P</mi>
<mrow>
<mi>N</mi>
<mi>T</mi>
</mrow>
</msub>
<mo>=</mo>
<msub>
<mrow>
<mo>(</mo>
<munderover>
<mo>&Sigma;</mo>
<mrow>
<mi>k</mi>
<mo>=</mo>
<mn>1</mn>
</mrow>
<mi>n</mi>
</munderover>
<mo>(</mo>
<mrow>
<msub>
<mi>a</mi>
<mi>k</mi>
</msub>
<mo>&times;</mo>
<msub>
<mi>P</mi>
<mrow>
<mi>N</mi>
<mi>k</mi>
</mrow>
</msub>
</mrow>
<mo>)</mo>
<mo>)</mo>
</mrow>
<mi>min</mi>
</msub>
<mo>-</mo>
<mo>-</mo>
<mo>-</mo>
<mrow>
<mo>(</mo>
<mn>4</mn>
<mo>)</mo>
</mrow>
<mo>,</mo>
</mrow>
PNkRepresent the rated power of k-th of variable pump in the pump set.
3. hydraulic press drive system according to claim 1 matches power save mode, it is characterized in that：
If using variable displacement with constant power pump in the hydraulic press drive system, then for unified work of the hydraulic press drivetrain
Make the relatively low stage of operating pressure in the cycle, the load factor of asynchronous motor is improved by lifting variable pump operating pressure, to subtract
Few energy loss.
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| CN110242531A (en) * | 2019-06-14 | 2019-09-17 | 合肥工业大学 | A kind of invariable power plunger variable pump group drive system Energy Saving Control strategy |
| CN110513346A (en) * | 2019-09-18 | 2019-11-29 | 济宁海推重工科技有限公司 | A kind of excavator hydraulic control system and method |
| CN110968059A (en) * | 2019-12-04 | 2020-04-07 | 合肥工业大学 | Design method of multi-machine sharing drive system of production line |
| CN113898620A (en) * | 2021-07-22 | 2022-01-07 | 浙江大学 | Flexible loading and unloading method for large-flow pump station |
| US11803167B2 (en) | 2019-12-04 | 2023-10-31 | Hefei University Of Technology | Energy service system of multi-machine production line and design method of shared drive system |
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|---|---|
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