CN102639873A - System and method for controlling linear pump system - Google Patents
System and method for controlling linear pump system Download PDFInfo
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- CN102639873A CN102639873A CN2010800543756A CN201080054375A CN102639873A CN 102639873 A CN102639873 A CN 102639873A CN 2010800543756 A CN2010800543756 A CN 2010800543756A CN 201080054375 A CN201080054375 A CN 201080054375A CN 102639873 A CN102639873 A CN 102639873A
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
- F04B17/03—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors
- F04B17/04—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors using solenoids
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B11/00—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation
- F04B11/005—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation using two or more pumping pistons
- F04B11/0058—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation using two or more pumping pistons with piston speed control
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B23/00—Pumping installations or systems
- F04B23/02—Pumping installations or systems having reservoirs
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
- F04B49/20—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by changing the driving speed
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
- F04B9/08—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid
- F04B9/10—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid
- F04B9/109—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers
- F04B9/111—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers with two mechanically connected pumping members
- F04B9/113—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers with two mechanically connected pumping members reciprocating movement of the pumping members being obtained by a double-acting liquid motor
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Reciprocating Pumps (AREA)
- Control Of Positive-Displacement Pumps (AREA)
- Electromagnetic Pumps, Or The Like (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
Systems and methods for operating a linear pump system involve operating a linear motor system; reciprocating a linear pump and a motor control module that issues commands and a control logic input to the linear motor system. The linear motor system is operated to reciprocate an output shaft between first and second reversal positions. The linear pump is reciprocated with the output shaft to produce a flow of material. A pump reversal command reverses direction of the output shaft. A torque command controls speed of the output shaft. The control logic input reciprocates the output shaft at speeds to produce a constant output condition of the flow of material. The motor control module adjusts the torque command to operate the output shaft at an increased speed above what is necessary for the constant output condition for a temporary time period beginning when the reversal command is issued.
Description
Quoting each other of related application
The application requires the U.S. Provisional Application sequence number No.61/267 that is entitled as " MINIMIZING PRESSURE DROP DURING PUMP REVERSAL IN A LINEAR PUMP SYSTEM (in the pump Umklapp process at linear pumping system pressure drop being minimized) " in submission on December 8th, 2009 by inventor Christopher Blackson (Christoffer cloth Rec is gloomy), Nick Long (Ni Kelong) and Roger Blough (Luo Jie Blaw) according to 35U.S.C. § 120; 509 preference, its content is included in this reference.
The application requires the preference in the PCT patent application serial numbers PCT/2010/__ that is entitled as " SYSTEM AND METHOD FOR CONTROLLING LINEAR PUMP SYSTEM (linear pump system and the method that is used to control linear pumping system) " of submission on December 8th, 2010 by inventor Christopher Blackson (Christoffer cloth Rec is gloomy), Nick Long (Ni Kelong) and Roger Blough (Luo Jie Blaw) according to 35U.S.C. § 119, and its content is included in this reference.
Technical field
The present invention is broadly directed to a kind of pump control system.More particularly, the present invention relates to reduce pressure drop in the linear pump.
Background technique
Linear pump is included in the housing pistons reciprocating and passes through housing with propelling fluid.Traditional linear pump withdrawn fluid in return stroke gets into housing, and in forward stroke, fluid is released housing.Valve is used to prevent flow through blowback.Valve also can be configured in each return stroke and forward stroke process suction fluid and pumping fluid on the relative both sides of piston, to provide the stable flow of liquid of self-pumping.Yet, when the piston reverse directions, having the intrinsic decline of pump pressure, it causes the variation of distributing fluids amount.When needing the flow of accurate measurement, this variation is especially worthless.For example, in the double-component metering system, resin material and catalyst material are side by side discharged from the mixing head of dispensing gun.The mixing of two kinds of materials produces chemical reaction, and chemical reaction starts process of setting, causes solidifying fully the after-hardening material.Advantageously, in whole allocation process, the steady stream of resin material and catalyst material is provided, to guarantee the proper proportion of resin and catalyzer, so that mixture suitably solidifies.Therefore, need to reduce and the relevant pressure loss of employed linear pump in list and double-component metering system.
Summary of the invention
The present invention relates to operate the method and system of linear pumping system.
Operate the method for linear pumping system, comprise linear motor system of operation and to-and-fro motion linear pump.The linear motor system is operated with to-and-fro motion output shaft between first and second backward positions.Linear pump uses the output shaft to-and-fro motion of linear motor system to produce material stream.The linear motor system is driven with the speed that constant material stream output state is provided.When the output shaft reverse directions, the linear motor system is driven by interim with the speed of the increase on the required speed of constant output state.
The linear pump system comprises linear motor system, linear material pump and motor control module.The linear motor system produces the to-and-fro motion of output shaft between first and second backward positions.The linear material pump is connected to output shaft to produce the output stream of material.Motor controller sends inverted command, torque command and control logic and is input to the linear motor system.Send the direction of inverted command with the counter-rotating output shaft.Send the speed of torque command with the control output shaft.Send the speed to-and-fro motion output shaft of control logic input with the constant output state of generation material stream.Motor control module adjustment torque command is used at the interim time durations that when inverted command is sent, begins, with the speed operation output shaft of the increase on the required speed of constant output state.
Description of drawings
Fig. 1 shows the double-component pumping system with pump unit, component material container and dispensing gun.
Fig. 2 shows the schematic diagram of the double-component pumping system of the Fig. 1 with the linear component pump of independent control.
Fig. 3 shows the flow chart of method of the linear component pump of control graph 2.
Embodiment
Fig. 1 shows double-component pumping system 10, has pump unit 12, component material container 14A and 14B and dispensing gun 16.Pump unit 12 comprises hydraulic power bag 18, display modular 20, fluid manifold 22, the first linear pump 24A, the second linear pump 24B, hydraulic fluid reservior 26 and distribution box 28.As shown in Figure 2, the electric motor, dual output selector valve, hydraulic linear motor, gear pump and the motor control module (MCM) that are used for each linear pump 24A and 24B all are located in the hydraulic power bag 18.Dispensing gun 16 comprises distributing head 32 and is connected to the first linear pump 24A and the second linear pump 24B respectively through flexible pipe 34A and 34B. Flexible pipe 36A and 36B are connected feed pump 38A and 38B respectively to linear pump 24A and 24B.Pressurized air is fed to feed pump 38A and 38B and dispensing gun 16 through flexible pipe 40A, 40B and 406 respectively.
When user's operated allocated rifle 16, the pressurized component material that is fed to manifold 22 by linear pump 24A and linear pump 24B is pushed to mixing head 32.Mixing head 32 mixes first and second component materials to start process of setting, and process of setting is for example accomplished when mixed component material is sprayed the entering mould.First and second component materials distribute from rifle 16 with constant output state usually.For example, the user can provide input to distribute component material with control MCM with constant pressure or constant flow rate at display modular 20 places.MCM cooperates electric motor and dual output selector valve to use the control logic input and output, among miscellaneous part, so that constant output state to be provided.Yet,, when pressure in the pump descends at the rollback point place, slight variation is arranged in the constant output state because linear pump 24A and linear pump 24B comprise the piston of necessary reverse directions.The present invention provides a kind of control system and method, is used to reduce the variation in pressure that is assigned with component material, and this variation in pressure results from the pressure that produces at the rollback point place of linear pump 24A and pump 24B and falls.
Fig. 2 shows the schematic representation of double-component pumping system 10 of Fig. 1 of linear component pump 24A with control independently and 24B.Pumping system 10 comprises pump unit 12, dispensing gun 16, the first linear pump 24A, the second linear pump 24B, hydraulic fluid reservoir 26A, the second hydraulic fluid reservoir 26B, motor control module (MCM) 42A and 42B, electric motor 44A and 44B, gear pump 46A and 46B, dual output selector valve 48A and 48B, hydraulic linear motor 50A and 50B, pressure sensor output 52A and 52B and speed linear position sensor 54A and 54B.Hydraulic reservoir 26A and 26B also comprise Decompression valves 56A and 56B, filter 58A and 58B, liquid level indicator 60A and 60B and pressure transducer 62A and 62B respectively.
Hydraulic fluid reservoir 26A, MCM42A, motor 44A, gear pump 46A, dual output selector valve 48A and hydraulic linear motor 50A are positioned in the hydraulic power bag 18, and comprise first 64A of linear motor system.Likewise, hydraulic fluid reservoir 26B, MCM42B, electric motor 44B, gear pump 46B, dual output selector valve 48B and hydraulic linear motor 50B are positioned at hydraulic power bag 18, and comprise second 64B of linear motor system.In other embodiment of the present invention, linear motor system shared components is such as electric motor, gear pump and hydraulic fluid reservoir.
Under the situation of filling of pump unit and activation, first and second component materials of pressurization are provided to linear pump 24A and 24B respectively by feed pump 38A and 38B (as shown in Figure 1) respectively. Feed pump 38A and 38B are operated by pressurized air.Linear pump 24A and 24B by first and second 64A of linear motor system and 64B operation with first and second component materials that pressurization is provided to dispensing gun 16.In addition, pressurized air is provided to dispensing gun 16 and gets into mixing head 32 and discharge rifle 16 to discharge the pressurized component material with operating pumps or valve system.
64A of linear motor system and 64B are respectively by motor control module (MCM) 42A and 42B control.MCMS 42A and 42B are to equate operating linear motor system 64A and 64B with same way as, so that the component material of proportional amount is provided to dispensing gun 16.The explanation of operating linear motor system 64A and 64B will be concerned about the 64A of linear motor system, the 64B of linear motor system operation in a similar manner, and same parts is correspondingly numbered.
Motor 44A receives the electric power from distribution box 28 (Fig. 1).In one embodiment, motor 44A comprises direct current (DC) motor.MCM 42A sends torque command C
T, torque command C
TReceive speed by motor 44A with controlling and driving axle 66A.Live axle 66A is connected to gear pump 46A, and gear pump 46A is immersed in the hydraulic fluid among the hydraulic fluid reservoir 26A.Gear pump 46A is used to from the rotation of motor 44A input, with from storage 26A suction fluid, and in circuit 68A, produces pressurized hydraulic flow.Hydraulic fluid reservoir 26A comprises liquid level indicator 60A, and liquid level indicator 60A is used to confirm the amount of the fluid in storage 26A.Pressure transducer 62A can be used for confirming the not filling situation in the storage 26A.In other embodiments, live axle 66A is used to drive the other types positive-displacement pump, and positive-displacement pump will rotate input and convert flow of pressurized fluid to, such as sliding vane rotary pump or peristaltic pump.
Come the pressurized hydraulic flow of self-pumping 46A to cross Decompression valves 56A and arrive dual output selector valve 48A.When having superfluous pressure condition, Decompression valves 56A provides the device that allows superfluous pressurized hydraulic fluid to turn back to storage 26A.Will discuss as following, selector valve 48A uses the hydraulic fluid of pressurization with to-and-fro motion linear motor 50A.After passing through filter 58A, pressurized hydraulic fluid turns back to storage 26A from the selector valve 48A among circuit 70A.Filter 58A removes impurity from hydraulic fluid.Therefore, between storage 26A, gear pump 46A, selector valve 48A and linear motor 50A, form the closed-loop path stream of hydraulic fluid.
As known in the art, dual output selector valve 48A is according to traditional selector valve design structure.Dual output selector valve 48A receives the continuous-flow of pressurized hydraulic fluid and turns to fluid to flow to linear motor 50A.Specifically, selector valve 48A comprises the input that is connected to circuit 68A and is connected to the output of circuit 70A and is connected to two ports of circuit 72A and 74A.Pressure fluid alternately supplies to circuit 72A and 74A, and circuit 72A and 74A are used for driving linear motor 50A.
Linear motor 50A comprises piston 76A, slides in the housing 78A of piston 76A between two fluid chamber.Each fluid chamber receives respectively the flow of pressurized fluid from circuit 72A and 72B.For example, selector valve 48A in primary importance, circuit 72A provide pressure fluid to first Room in housing 78A with downward (about Fig. 2) mobile piston 76A.Simultaneously, be pushed out linear motor 50A and turn back to selector valve 48A and leave at other indoor fluids of housing 78A and arrive circuit 70A through circuit 74A.MCM42A sends inverted command C
R, inverted command C
RReceive by selector valve 48A, start the time of reverse directions with control linear motor 50A.Receive inverted command C
RAfter, selector valve 48A switches to the second place, so that pressure fluid is supplied to housing 78A through circuit 74A, and removes through circuit 72A from the fluid of housing 78A.Therefore, reciprocating piston 76A between inherent two backward positions of the operation housing 78A of selector valve 48A, it is to-and-fro motion output shaft 80A also.Speed linear position sensor 54A is connected to a 80A, and based on the speed that piston 76A moves the indication of moving of MCM 42A piston 76A and speed is provided.Especially, when output shaft 80A moved away from one of backward position, position transducer 54A provided position signal S
POGive MCM 42A.
The output shaft 80A of linear motor 50A directly is mechanically connected to the piston shaft 82A of linear pump 24A.Piston 84A in the axle 82A drive shell 86A.Piston 84A extracts component material from container 14A and gets into housing 86A, as being provided by feed pump 38A (Fig. 1).Linear pump 24A comprises double action pump, and in double action pump, component material pushes circuit 88A in upstroke (with reference to figure 2), and pushes route road 89A in down stroke (with reference to figure 2).Specifically; In upstroke; Valve 90A opens extracting component material and to get into housing 86A from feed pump 38A through manifold 22 (as shown in Figure 1), and valve 92A opens to allow piston 84A to promote material and get into dispensing gun 16 through circuit 88A, and valve 94A and 96A are closed.At downward stroke, valve 90A and 92A near, and valve 94A opens extracting component material and to get into housing 86A from feed pump 38A through manifold 22 (like Fig. 1), and valve 96A opens to allow piston 84A to promote material and gets into dispensing gun 16 through circuit 89A.Two actions of linear pump 24A keep the continuous and approaching constant supply of component material in operating process.Yet, as previously mentioned, at the rollback point place of piston shaft 82A slight pressure drop appears.The pressure drop that the present invention alleviates experience through near accelerating piston axle 82A rollback point.
Component material from circuit 88A, 89A pushes dispensing gun 16 through the pressure from linear pump 24A, and it mixed in mixing head 32 with component material from linear pump 24B before spraying from rifle 16.The pressure of the component material in the pressure transducer 52A detection line 88A and with pressure signal S
PrSend to MCM 42A.Optional heater 98A can be connected to circuit 88A, with heat contents material before distributing from mixing head 32, for example, with the viscosity of reduction component material or the reaction and the curing of promotion and other component materials.
MCM 42A receiving position signal S
POWith pressure signal S
PrAnd send inverted command C
RWith torque command C
TUse position signal S
POWith pressure signal S
Pr, MCM 42A coordinates inverted command C
RWith torque command C
T, to control linear motor system at the constant output state.For example; The operator of double-component pumping system 10 can specify input in display modular 20 (Fig. 1); Pump unit 12 will be operated with first and second component materials that constant pressure is provided to manifold 22 (omit among Fig. 2, be presented among Fig. 1), or the constant flow rate of component material outputs to manifold 22.MCM 42A controls logic, constantly adjusts inverted command C
RWith torque command C
T, to keep the constant output state.Torque command C
TConfirm how fast rotational axle 66A of motor 44A, how fast this be directly connected to chamber fill fluid in the housing 78A of linear motor 50A.Inverted command C
RConfirm the time of selector valve 48A switching position.Inverted command C
RSend coordination and how to fill housing 78A inner room fast so that selector valve 48A can switch fluids flows into the direction of housing 78A.Control logic keeps the speed of motor 44A consistent with the switch speed of selector valve 48A, to keep required constant output state.As will discuss with reference to figure 3, the present invention operates linear motor system 64A, descends with minimize pressure when the piston shaft 82A reverse directions.
Fig. 3 flow for displaying figure, the linear component pump 24A of caption control graph 2 and the method for 24B.At first step 100 places, motor control module (MCM) 42A uses the control logic input, and for example, the input of programming or the input that gets at display modular 20 places are operated linear pumping system 64A, so that linear pump 24A operates at constant output state place.Specifically, MCM 42A adjusts to the torque command C of electric motor 44A
TSpeed with Control Shaft 66A.
At step 110 place, when pump shaft 82A reached its end of advancing at the rollback point place, MCM 42A sent inverted command C
RThe control logic of form outputs to the part of selector valve 48A as control logic.Next, at step 120 place, MCM 42A closing control logic is so that MCM 42A no longer constantly upgrades torque command C
TWith inverted command C
RTo produce the constant output state.At step 130 place, MCM 42A sends torque command C
TTo motor 44A,, thereby increase the output that hydraulic fluid flows to dual output selector valve 48A with the speed of increase axle 66A.Correspondingly, MCM 42A sends inverted command C
RTo the direction of selector valve 48A, match with the flow of pressurized hydraulic fluid with counter-rotating pump output shaft 80A.Specifically, selector valve 48A must operate to allow the chamber in the housing 78A in linear motor 50A to be filled and to be found time by the flow velocity that pump 46A provides equaling.Therefore, after execution in step 130, the speed moment ground of output shaft 80A increases the speed of having carried out at step 100 place above before, to realize the constant output state.When axle 82A in housing 86A during the backward position place, output shaft 80A thereby with the axle 82A of the speed operation linear pump 24A that increases descends with the pressure that is reduced among the linear pump 24A.Output shaft 80A and piston shaft 82A thereby than the reverse directions quickly that under the control logic pattern, will take place.
At step 140 place, control logic detects the direction counter-rotating of output shaft 80A from linear position sensor 54A.Subsequently, at step 150 place, to the torque command C of motor 44A
TBe lowered to and be lower than at step 130 place through changing torque command C
TThe level of indication.Generally, speed is held in higher more a certain amount of than the speed of under control logic, being ordered.Yet if necessary, speed can be reduced to the speed that is lower than at step 100 place, to destroy the constant output state with minimizing.At step 160 place, reset mode is to be detected, so that control logic can be opened at step 170 place.For example, when the pressure in circuit 88A was detected as increase, reset mode can be determined, and showed that a 82A and an axle 78A have accomplished Umklapp process.Step 170 can take place later on during preset time immediately, is generally a few tens of milliseconds, so that reduce the constant output state that destroys as far as possible.Therefore, as the pressure signal S of MCM 42A reception from pressure transducer 52A
PrThe time, control logic can be rebuild, so that motor 44A and selector valve 48A operation under the constant output state once more, as accomplishing at step 100 place.In other embodiments, reset mode can be set up according to predetermined amount of time, accomplishes the predicted time that Umklapp process spent like linear motor 50A according to step 130 and 150 pump speed.
The present invention is provided for reducing the system and method for the variation in pressure in the operating process of linear pump system.As stated, when the piston reverse directions, linear pump itself produces delivery pressure and descends.For the embodiment who is disclosed, the delivery pressure of pump is directly proportional with piston movement speed, and its speed by the electric motor that drives the linear motor that activates linear pump is confirmed.Therefore, when piston stopped with reverse directions, the pressure of pump descended.When the constant output state be the institute take, the decline of pump pressure is particularly disadvantageous.In addition, roughly constant to the input speed maintenance of the electric motor that drives linear motor under the constant output state, even under the constant pressure output state, the delivery pressure of linear pump shows slight waveform pattern.In one embodiment of the invention, the speed of electric motor was increased near the moment rollback point of linear motor provides on the necessary speed of constant output state.Just because of this, the slight waveform pattern of delivery pressure reduces.
Though the present invention describes about controlling linear pumping system based on the speed of electric motor or moment of torsion, the present invention can be applied to the linear pump system of other types, maybe can be used for otherwise controlling described system.Hydraulic fluid pressure can use fluid pressure governor control able to programme, rather than the speed of control electric motor, and the speed of fluid pressure governor control linear motor able to programme replaces selector valve 48A.Specifically, pressure regulator will be supplied the pressurized hydraulic fluid that combines from electric motor and gear pump, and with accommodating fluid to linear motor or get back to fluid storage.Pressure regulator will programme or control then, to change linear motor and the ratio that is supplied the hydraulic fluid of getting back to storage of getting into.Generally, control logic will be used to the constant output state of working pressure regulator control.Yet control logic can be suspended temporarily, and at linear motor during at the backward position place or near backward position, pressure regulator will increase to the output of linear motor.Alternatively, the embodiment's of description hydraulic system and fluid pressure governor can be replaced by pneumatic system, pneumatic pressure regulator.
Though the embodiment with reference to example describes the present invention, it will be understood by those skilled in the art that and to make various modifications under the situation that does not depart from scope of the present invention, and equivalent can replace its element.In addition, under the situation that does not depart from its base region, can make many modifications and give instruction of the present invention to adapt to particular case or material.Therefore, the concrete embodiment that expectation the invention is not restricted to disclose, but the present invention will comprise the whole embodiments in the scope that falls into attached claim.
Claims (20)
1. linear pump system comprises:
The linear motor system makes output shaft to-and-fro motion between first backward position and second backward position;
The linear material pump is connected to output shaft to produce material stream; With
The motor control module:
Send inverted command to the linear motor system, with the direction of counter-rotating output shaft;
Send torque command to the linear motor system, with the speed of control output shaft; With
Send control logic and be input to the linear motor system, be used for speed to-and-fro motion output shaft with the constant output state that produces material stream;
Wherein said motor control module is adjusted said torque command, is used at the interim time durations that when inverted command is sent, begins, with the speed operation output shaft of increase, and the speed of said increase is on the required speed of constant output state.
2. linear pump according to claim 1 system, wherein said linear motor system also comprises:
Linear hydraulic motor comprises output shaft;
Electric motor receives the torque command from the motor control module;
By the rotating hydraulic pump of electrical motor driven, pressurized hydraulic flow that the speed with electric motor matches is provided, with the speed of control output shaft; With
Hydraulic Double output selector valve is connected to linear hydraulic motor, and in response to receiving inverted command from the motor control module, receives pressurized hydraulic flow from the rotating hydraulic pump, with the direction of the output shaft that hydraulically reverses.
3. linear pump according to claim 1 system, wherein the motor control module is in response to the input of adjustment torque command closing control logic, and simultaneously with the speed operation output shaft on the required speed of constant output state.
4. linear pump according to claim 3 system, wherein the linear motor system also comprises:
Be connected to the position transducer of linear hydraulic motor, move away from a backward position, send position signal in response to output shaft;
Wherein the motor control module changes controlled torque command, to reduce the speed of the said increase of output shaft in response to the receiving position signal.
5. said control logic input is opened by linear pump according to claim 3 system, wherein said motor control module after said interim time durations stops.
6. linear pump according to claim 5 system, wherein said interim time durations stops when reset mode is detected.
7. linear pump according to claim 5 system, wherein said linear motor system also comprises:
Pressure transducer is used for the pressure that test material flows;
Wherein said reset mode comprises that pressure to be detected rises.
8. linear pump according to claim 1 system, wherein said constant output state comprises constant pressure output or constant flow rate output.
9. a method of operating linear pumping system comprises the steps:
Operate linear motor system, so that output shaft to-and-fro motion between first backward position and second backward position;
Use the output shaft of said linear motor system to make the linear pump to-and-fro motion, to produce material stream;
Speed driving linear motor system with constant output state that material stream is provided;
Start the direction counter-rotating of output shaft; With
In the interim time durations that when starting the direction counter-rotating of output shaft, begins, the speed driving linear motor system to increase, the speed of said increase is on the required speed of said constant output state.
10. the method for the linear pumping system of operation according to claim 9 also comprises the steps:
Operation has the linear hydraulic motor of output shaft;
The operation electric motor;
With electric motor operated rotating hydraulic pump, be used to provide pressurized hydraulic flow arrive linear hydraulic motor, with the speed of control output shaft; With
Operation Hydraulic Double output selector valve, said Hydraulic Double output selector valve is connected to linear hydraulic motor and receives the direction of pressurized hydraulic flow with the counter-rotating output shaft.
11. the method for the linear pumping system of operation according to claim 10 also comprises the steps:
The motor control module is coordinated the operation of electric motor and Hydraulic Double output selector valve, wherein:
Said linear motor system responses is in receiving the control logic input from the motor control module, being driven with the speed that the constant output state is provided;
Receive inverted command in response to Hydraulic Double output selector valve, start the direction counter-rotating of output shaft from the motor control module;
Receive torque command in response to electric motor, with the speed driving linear motor system that increases from the motor control module.
12. the method for the linear pumping system of operation according to claim 11 also comprises the steps:
Closing control logic input when sending torque command, the while is with the speed operation of said increase.
13. the method for the linear pumping system of operation according to claim 12 also comprises the steps:
Detection is in the position of the output shaft at backward position place; With
In response to detecting backward position, change torque command to reduce the speed of said increase.
14. the method for the linear pumping system of operation according to claim 12 also comprises the steps:
After said interim time durations stops, open said control logic input.
15. the method for the linear pumping system of operation according to claim 14 also comprises the steps:
Detect the pressure of output material stream;
When detecting the pressure rising, stop said interim time durations.
16. the method for the linear pumping system of operation according to claim 9, wherein the constant output state comprises constant pressure output or constant flow rate output.
17. a method of operating linear pumping system comprises the steps:
Operate linear motor system, so that output shaft to-and-fro motion between first backward position and second backward position;
Use the output shaft of linear motor system to make the linear pump to-and-fro motion, to produce material stream;
Speed driving linear motor system with constant output state that material stream is provided; With
When the output shaft reverse directions, drive linear motor system with the speed that increases temporarily, the speed of said increase is on the required speed of constant output state.
18. method according to claim 17, the step that wherein drives linear pump comprises:
The direction of counter-rotating output shaft;
The speed of control output shaft; With
Wherein use the direction and the speed of control logic control output shaft, so that the constant output state to be provided, when linear pump is driven with the speed of said increase, suspend control logic temporarily.
19. method according to claim 18 also comprises the steps:
Detect the position of output shaft; With
When detecting output shaft when backward position moves away, reduce the speed of said increase.
20. method according to claim 19 also comprises the steps:
Pressure in the test material stream; With
When rising, pressure starts said control logic when detecting.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US26750909P | 2009-12-08 | 2009-12-08 | |
| US61/267,509 | 2009-12-08 | ||
| PCT/US2010/003120 WO2011071528A2 (en) | 2009-12-08 | 2010-12-08 | System and method for controlling linear pump system |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN102639873A true CN102639873A (en) | 2012-08-15 |
| CN102639873B CN102639873B (en) | 2015-08-12 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201080054375.6A Expired - Fee Related CN102639873B (en) | 2009-12-08 | 2010-12-08 | For the system and method for control linear pumping system |
Country Status (7)
| Country | Link |
|---|---|
| US (1) | US20130039778A1 (en) |
| EP (1) | EP2510237A4 (en) |
| JP (1) | JP5735532B2 (en) |
| CN (1) | CN102639873B (en) |
| AU (1) | AU2010328641B2 (en) |
| BR (1) | BR112012013732A2 (en) |
| WO (1) | WO2011071528A2 (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106255826A (en) * | 2014-04-23 | 2016-12-21 | 塞阿姆斯特朗有限公司 | For the integrating device used at pumping plant |
| US10413924B2 (en) | 2013-07-19 | 2019-09-17 | Graco Minnesota Inc. | Proportioning cylinder for spray system |
| CN115106020A (en) * | 2021-03-17 | 2022-09-27 | 固瑞克明尼苏达有限公司 | System for dispensing abrasive material |
Families Citing this family (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2965313B1 (en) * | 2010-09-29 | 2012-09-07 | Exel Ind | METHOD, DEVICE AND MEANS FOR DRIVING ALTERNATIVE LINEAR MOVEMENT DUAL EFFECT PUMP |
| WO2015010029A1 (en) * | 2013-07-19 | 2015-01-22 | Graco Minnesota Inc. | Pump changeover algorithm for spray system |
| US9192953B2 (en) * | 2013-12-04 | 2015-11-24 | Pioneer Industrial Systems, Llc | Precision fluid delivery system |
| US10954931B2 (en) * | 2014-12-12 | 2021-03-23 | Dh Technologies Development Pte. Ltd. | Linear displacement pump with position sensing and related systems and methods |
| US10550676B2 (en) * | 2015-06-01 | 2020-02-04 | Baker Hughes Incorporated | Systems and methods for determining proper phase rotation in downhole linear motors |
| JP6401683B2 (en) | 2015-09-25 | 2018-10-10 | 株式会社スギノマシン | Fluid pressure generation method and fluid pressure generator |
| DE102016005319A1 (en) * | 2016-05-02 | 2017-11-02 | Inka-Systems Gmbh & Co. Kg | Device for filling a tank of a motor vehicle with a liquid or gaseous operating medium, in particular for initial industrial filling on the assembly line of the manufacturer |
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2010
- 2010-12-08 JP JP2012543083A patent/JP5735532B2/en not_active Expired - Fee Related
- 2010-12-08 EP EP10836313.6A patent/EP2510237A4/en not_active Withdrawn
- 2010-12-08 US US13/514,449 patent/US20130039778A1/en not_active Abandoned
- 2010-12-08 CN CN201080054375.6A patent/CN102639873B/en not_active Expired - Fee Related
- 2010-12-08 AU AU2010328641A patent/AU2010328641B2/en not_active Ceased
- 2010-12-08 WO PCT/US2010/003120 patent/WO2011071528A2/en active Application Filing
- 2010-12-08 BR BR112012013732A patent/BR112012013732A2/en not_active IP Right Cessation
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| US5151015A (en) * | 1990-05-15 | 1992-09-29 | L'oreal | Compression device, particularly for the pressure filling of a container |
| US6227807B1 (en) * | 1999-02-02 | 2001-05-08 | Eric Chase | Constant flow fluid pump |
| US20040001765A1 (en) * | 2001-07-31 | 2004-01-01 | Wood Nigel Charles | Pumping arrangement |
| JP2007263001A (en) * | 2006-03-29 | 2007-10-11 | Yamada Corporation | Linear actuator for pump |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| US10413924B2 (en) | 2013-07-19 | 2019-09-17 | Graco Minnesota Inc. | Proportioning cylinder for spray system |
| CN106255826A (en) * | 2014-04-23 | 2016-12-21 | 塞阿姆斯特朗有限公司 | For the integrating device used at pumping plant |
| CN115106020A (en) * | 2021-03-17 | 2022-09-27 | 固瑞克明尼苏达有限公司 | System for dispensing abrasive material |
| US11971022B2 (en) | 2021-03-17 | 2024-04-30 | Graco Minnesota Inc. | System for dispensing abrasive material |
Also Published As
| Publication number | Publication date |
|---|---|
| WO2011071528A2 (en) | 2011-06-16 |
| WO2011071528A3 (en) | 2011-10-13 |
| JP5735532B2 (en) | 2015-06-17 |
| BR112012013732A2 (en) | 2016-03-22 |
| US20130039778A1 (en) | 2013-02-14 |
| AU2010328641B2 (en) | 2015-04-09 |
| JP2013513069A (en) | 2013-04-18 |
| EP2510237A2 (en) | 2012-10-17 |
| AU2010328641A1 (en) | 2012-06-21 |
| EP2510237A4 (en) | 2015-11-25 |
| CN102639873B (en) | 2015-08-12 |
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