CN101473138A - Fluid pressure drive device - Google Patents
Fluid pressure drive device Download PDFInfo
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- CN101473138A CN101473138A CNA2007800222965A CN200780022296A CN101473138A CN 101473138 A CN101473138 A CN 101473138A CN A2007800222965 A CNA2007800222965 A CN A2007800222965A CN 200780022296 A CN200780022296 A CN 200780022296A CN 101473138 A CN101473138 A CN 101473138A
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- hydraulic pump
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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
- F04B23/04—Combinations of two or more pumps
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- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02F—DREDGING; SOIL-SHIFTING
- E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
- E02F9/20—Drives; Control devices
- E02F9/22—Hydraulic or pneumatic drives
- E02F9/2246—Control of prime movers, e.g. depending on the hydraulic load of work tools
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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
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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
- F04B49/02—Stopping, starting, unloading or idling control
- F04B49/03—Stopping, starting, unloading or idling control by means of valves
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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
- F04B49/06—Control using electricity
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
- F05B2210/00—Working fluid
- F05B2210/10—Kind or type
- F05B2210/11—Kind or type liquid, i.e. incompressible
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
- F05B2270/00—Control
- F05B2270/30—Control parameters, e.g. input parameters
- F05B2270/301—Pressure
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10S417/00—Pumps
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Fluid-Pressure Circuits (AREA)
- Mining & Mineral Resources (AREA)
- Civil Engineering (AREA)
- Structural Engineering (AREA)
- Details Of Reciprocating Pumps (AREA)
- Control Of Positive-Displacement Pumps (AREA)
Abstract
A fluid pressure drive device having a small inexpensive structure and achieving both control of high pressure and control of a large flow rate at the same time. Tandem hydraulic pumps that are a first fixed displacement hydraulic pump (1) with a medium displacement and a second fixed displacement hydraulic pump (2) with a small displacement are driven by a servo motor (3). Hydraulic oil from the first and second fixed displacement hydraulic pumps (1, 2) is controlled by a four-port three-position type electromagnetic switchover valve (5). The electromagnetic switchover valve (5) has a first position (S1) at which first and second input ports (P1, P2) are communicated with an output port (A) and a return port (R) is closed, a second position (S2) at which the first input port (P1) is communicated with the output port (A) and the second input port (P1) is communicated with the return port (R), and a third position (S3) at which the first input port (P1) is communicated with the return port (R) and the second input port (P2) is communicated with the output port (A).
Description
Technical field
The present invention relates to be suitable for for example fluid pressure drive device of injection moulding machine, lathe, Architectural Equipment etc.
Background technique
In the past, as fluid pressure drive device, existence is with lower device: utilize a fixed capacity formula of driven by servomotor oil hydraulic pump, control described actuating motor (Japan Patent discloses communique the 2000-No. 320466) by controller according to detected pressure value, flow detection value, pressure instruction value and flow instruction value simultaneously.
But in above-mentioned fluid pressure drive device in the past, owing to utilize a fixed capacity formula of driven by servomotor oil hydraulic pump, the needed axle of this actuating motor moment of torsion is directly proportional with the capacity of load pressure and fixed capacity formula oil hydraulic pump.Therefore, when the big flow of needs, use jumbo fixed capacity formula oil hydraulic pump, then load pressure raises, and the needed axle of actuating motor moment of torsion, driving current become greatly, correspondingly actuating motor and the controller very big price of the volume costliness again that becomes.
On the other hand, when the needs high pressure, use the fixed capacity formula oil hydraulic pump of small capacity to reduce the needed axle of actuating motor moment of torsion, then when the big flow of needs, can not satisfy its requirement.
Like this, in above-mentioned fluid pressure drive device in the past, existence can not utilize the little and low-cost structure of volume to realize the problem of high voltage control and big flow control.
Summary of the invention
Problem of the present invention provides a kind of fluid pressure drive device that can utilize the little and low-cost structure of volume to realize high voltage control and big flow control.
In order to solve above-mentioned problem, fluid pressure drive device of the present invention is characterised in that this fluid pressure drive device has:
The 2nd fixed capacity formula oil hydraulic pump of the 1st fixed capacity formula oil hydraulic pump of the interconnected twin intermediate size of axle and the small capacity littler than described intermediate size;
Four ports, three position model electromagnetic switching valves, it has the 1st input port that is connected with the exhaust port of described the 1st fixed capacity formula oil hydraulic pump, the 2nd input port that is connected with the exhaust port of described the 2nd fixed capacity formula oil hydraulic pump, with load pipeline output port that is connected and the port that returns that is connected with fuel tank, and have: the described the 1st and the 2nd input port is communicated with output port, and make the 1st position of returning port shutdown, described the 1st input port is communicated with output port, and make described the 2nd input port and return the 2nd position that port is communicated with and make described the 1st input port and return port and be communicated with, and the 3rd position that described the 2nd input port is communicated with output port;
Actuating motor, it drives described the 1st fixed capacity formula oil hydraulic pump and the 2nd fixed capacity formula oil hydraulic pump;
Pressure transducer, it directly or indirectly detects the pressure of described load pipeline;
The flow detection sensor, it detects the rotational position or the speed of described actuating motor; And
Controller, it accepts the output of described pressure transducer and flow detection usefulness sensor, and accept pressure instruction and flow instruction, control described actuating motor and make the pressure of described load pipeline and flow become pressure and the flow corresponding with described pressure instruction and flow instruction.
According to the fluid pressure drive device of said structure, when carrying out the control of low pressure and mass flow, described controller makes described four ports, three position model electromagnetic switching valves be positioned at the 1st position.
Like this, flow into from the 1st fixed capacity formula oil hydraulic pump of described intermediate size electromagnetic switching valve the 1st input port intermediate flow liquid, flow into the liquid interflow of small flow of the 2nd input port of electromagnetic switching valve with the 2nd fixed capacity formula oil hydraulic pump from small capacity, the liquid of big flow is provided to the load pipeline from output port.
At this moment, described controller is according to the flow instruction of the pressure instruction of representing low pressure, the big flow of expression, from the signal of pressure transducer with from the signal of flow detection with sensor, control the rotational speed of described actuating motor, make the pressure of load pipeline and flow reach described low pressure and big flow.
Like this, when described electromagnetic switching valve is positioned at the 1st position, the load pipeline is carried out the control of low pressure and mass flow.
On the other hand, during the control of underway pressure intermediate flow, described controller makes described electromagnetic switching valve be positioned at the 2nd position.
Like this, flow into the liquid of small flow of the 2nd input port of electromagnetic switching valve from the 2nd fixed capacity formula oil hydraulic pump of described small capacity, be discharged to the fuel tank the 2nd fixed capacity formula oil hydraulic pump off-load from returning port.But, flow into the liquid of intermediate flow of the 1st input port of electromagnetic switching valve from described the 1st fixed capacity formula oil hydraulic pump, offered the load pipeline from output port.
At this moment, described controller is according to the flow instruction of the pressure instruction of pressing in the expression, expression intermediate flow, from the signal of pressure transducer with from the signal of flow detection with sensor, control the rotational speed of described actuating motor, make the pressure of load pipeline and flow reach described middle the pressure and intermediate flow.
Like this, when described electromagnetic switching valve is positioned at the 2nd position, the load pipeline is carried out middle control of pressing intermediate flow.
And when carrying out the control of high-pressure low-flow, described controller makes described electromagnetic switching valve be positioned at the 3rd position.
Like this, flow into the liquid of intermediate flow of the 1st input port of electromagnetic switching valve from the 1st fixed capacity formula oil hydraulic pump of described intermediate size, be discharged to the fuel tank the 1st fixed capacity formula oil hydraulic pump off-load from returning port.But, flow into the liquid of small flow of the 2nd input port of electromagnetic switching valve from described the 2nd fixed capacity formula oil hydraulic pump, offered the load pipeline from output port.
At this moment, described controller is according to the flow instruction of the pressure instruction of representing high pressure, expression small flow, from the signal of pressure transducer with from the signal of flow detection with sensor, control the rotational speed of described actuating motor, make the pressure and the flow of load pipeline reach described high pressure and small flow.
Like this, when described electromagnetic switching valve is positioned at the 3rd position, the load pipeline is carried out the control of high-pressure low-flow.
Like this, only use one four port, three position model electromagnetic switching valves and above-mentioned linkage structure, can select low pressure and mass flow, middle pressure intermediate flow, the operation mode in these three kinds of stages of high-pressure low-flow, and can reduce the needed axle of actuating motor moment of torsion.
Therefore,, can realize high voltage control and big flow control, and can reduce actuating motor and the needed current value of controller, can make actuating motor and controller miniaturization, low cost according to the present invention.
In addition, for example in fluid pressure drive device of injection moulding machine and punch machines etc., have and want the demand that under high pressure keep-ups pressure for a long time, still, actuating motor and controller were because big electric current made heating increase in the past, and existence can not be satisfied the problem of this demand.But, in the fluid pressure drive device of said structure, owing to current value reduces, so can under high pressure keep-up pressure for a long time.
A kind of fluid pressure drive device of mode of execution has:
The 1st one-way valve, it is connected between the 1st input port of the exhaust port of described the 1st fixed capacity formula oil hydraulic pump and described electromagnetic switching valve and between the described load pipeline, is used to make the mobile forward that becomes towards described load pipeline;
The 2nd one-way valve, it is connected between the 2nd input port of the exhaust port of described the 2nd fixed capacity formula oil hydraulic pump and described electromagnetic switching valve and between the described load pipeline, is used to make the mobile forward that becomes towards described load pipeline.
According to above-mentioned mode of execution, suppose electromagnetic switching valve for example since dust etc. be lockable, and stop between the 1st position and the 2nd position or between the 1st position and the 3rd position, make when closing between the 1st input port and the 2nd input port and the output port, can make liquid from the 1st and the 2nd fixed capacity formula oil hydraulic pump in described electromagnetic switching valve bypass, offer the load pipeline by the 1st one-way valve and the 2nd one-way valve.Like this, when described electromagnetic switching valve fault, can utilize described the 1st one-way valve and the 2nd one-way valve in the electromagnetic switching valve bypass, so can prevent breakages such as pipe arrangement pipeline and hydraulic equipment.
In addition, a kind of fluid pressure drive device of mode of execution has the relief valve that is connected with described load pipeline.
According to above-mentioned mode of execution,, can prevent that pressure is excessive, and prevent the equipment breakage because the liquid that provides from the described the 1st and the 2nd one-way valve when making that the pressure of load pipeline will be excessive, can utilize described relief valve that liquid is discharged in the fuel tank.
In addition, in a kind of fluid pressure drive device of mode of execution, described controller has:
Pressure control portion, it accepts described pressure instruction and from the pressure detecting signal of described pressure transducer, according to the deviation delivery pressure control signal between described pressure instruction and the described pressure detecting signal;
Limitation part, it accepts pressure controling signal and flow instruction from described pressure control portion, and output applies the restriction corresponding with described flow instruction to described pressure controling signal and the restriction control signal that generates; And
The rotational speed control device, its basis is from the restriction control signal of described limitation part with from the flow detection signal of described flow detection with sensor, generation is used for the pressure of described load pipeline and flow control are the pressure corresponding with described pressure instruction and flow instruction and the rotational speed control signal of flow, and exports to described actuating motor.
According to above-mentioned mode of execution, by limitation part to pressure controling signal based on the deviation between pressure instruction and the pressure detecting signal from the output of described pressure control portion, apply the restriction corresponding (limiting control), and generate the restriction control signal with flow instruction.And, the rotational speed control device is according to this restriction control signal with from the flow detection signal of flow detection with sensor, generation is used for the pressure and the flow control of load pipeline are become the rotational speed control signal of pressure and the flow corresponding with pressure instruction and flow instruction, and exports to actuating motor.
Like this, pressure controling signal is applied the restriction corresponding with flow instruction and generate the restriction control signal, come pilot pressure and flow, so can be accurately and carry out pressure control and flow control swimmingly according to this restriction control signal by limitation part.
According to the present invention, a kind of fluid pressure drive device can be provided, it can utilize the little and low-cost structure of volume to suppress motor shaft moment of torsion and controller output current smaller, thereby can realize high voltage control and big flow control.
Description of drawings
Fig. 1 is the circuit diagram of the fluid pressure drive device of one embodiment of the present invention.
Embodiment
Below, specify the present invention with reference to illustrated mode of execution.
As shown in Figure 1, this fluid pressure drive device has: interconnected twin the 1st fixed capacity formula oil hydraulic pump 1 of axle and the 2nd fixed capacity formula oil hydraulic pump 2; Drive the actuating motor 3 of the 1st and the 2nd fixed capacity formula oil hydraulic pump 1,2; Control is from four ports, the three position model electromagnetic switching valves 5 of the working oil of the described the 1st and the 2nd fixed capacity formula oil hydraulic pump 1,2; Controller 6 with the described actuating motor 3 of control.
In addition, the 1st and the 2nd fixed capacity formula oil hydraulic pump 1,2 is examples of the 1st and the 2nd fixed capacity formula oil hydraulic pump.
Described the 1st fixed capacity formula oil hydraulic pump 1 is an intermediate size, and the 2nd fixed capacity formula oil hydraulic pump 2 is the little small capacities of intermediate size than the 1st fixed capacity formula oil hydraulic pump 1.
Described electromagnetic switching valve 5 has the 1st input port P1, the 2nd input port P2, output port A and returns port R.
And described electromagnetic switching valve 5 has: the described the 1st and the 2nd input port P1, P2 are communicated with output port A and make and return the 1st position S1 that port R seals; Described the 1st input port P1 is communicated with output port A and makes described the 2nd input port P1 and return the 2nd position S2 that port R is communicated with; With make described the 1st input port P1 and return the 3rd position S3 that port R is communicated with and described the 2nd input port P2 is communicated with output port A.
In addition, described electromagnetic switching valve 5 has electromagnetic coil a, b, with electromagnetic coil a, b demagnetization the time, described electromagnetic switching valve 5 is positioned at i.e. the 1st position S1 in neutral position, only to electromagnetic coil a excitation the time, described electromagnetic switching valve 5 is positioned at the 2nd position S2, and only to electromagnetic coil b excitation the time, described electromagnetic switching valve 5 is positioned at the 3rd position S3.
The exhaust port of described the 1st fixed capacity formula oil hydraulic pump 1 is connected with the 1st input port P1 of electromagnetic switching valve 3 via the 1st discharge conduit 11, and the exhaust port of described the 2nd fixed capacity formula oil hydraulic pump 2 is connected with the 2nd input port P2 of electromagnetic switching valve 3 via the 2nd discharge conduit 12.In addition, the output port A of described electromagnetic switching valve 5 is connected with load pipeline 15, and this load pipeline 15 leads to main frame oil hydraulic circuit 16.The port R that returns of described electromagnetic switching valve 5 is connected with fuel tank T.
Between described the 1st discharge conduit 11 and load pipeline 15, be connected with the 1st one-way valve 21, be used to make the mobile forward that becomes towards this load pipeline 15.And, between described the 2nd discharge conduit 12 and load pipeline 15, be connected with the 2nd one-way valve 22, be used to make the mobile forward that becomes towards this load pipeline 15.In addition, on described load pipeline 15, be connected with relief valve 23.
And, on described load pipeline 15, be connected with pressure transducer 25, utilize the pressure of these pressure transducer 25 direct detection load pipelines 15.
On the other hand, described actuating motor 3 is provided with the position detector 26 that the encoder by the rotational position that detects this actuating motor 3 constitutes.This position detector 26 is used for the flow of indirect detection twin the 1st and the 2nd fixed capacity formula oil hydraulic pump 1,2, is the example of flow detection with sensor.
And, described controller 6 is accepted the output of described pressure transducer 25 and position detector 26, accept pressure instruction and flow instruction simultaneously, control described actuating motor 3, so that the pressure of described load pipeline 15 and flow become pressure and the flow corresponding with described pressure instruction and flow instruction.
Specifically, described controller 6 comprises pressure control portion 31, limitation part 32 and rotational speed control device 33.These pressure control portions 31, limitation part 32 and rotational speed control device 33 are made of the software of microcomputer, hardware etc.
Described pressure control portion 31 accepts described pressure instructions and from the pressure detecting signal Pf of described pressure transducer 25, output is based on the pressure controling signal Vp of the deviation between described pressure instruction and the described pressure detecting signal Pf.This pressure control portion 31 is converted to pressure controling signal to pressure divergence by so-called PID (proportional/integral/derivative) control.
Described limitation part 32 has and the limiting circuit identical functions, acceptance is from the pressure controling signal Vp and the flow instruction of described pressure control portion 31, at described pressure controling signal Vp during greater than the predetermined value corresponding with flow instruction, apply the restriction corresponding, the restriction control signal VL that generation and output are corresponding with desired rotational speed with described flow instruction.
Described controller 6 is not shown, it determines that according to predefined benchmark flow instruction represents any flow in big flow, intermediate flow or the small flow, then, according to this big flow, intermediate flow and small flow of determining, be used to make electromagnetic switching valve 5 to be positioned at the control signal of the 1st position S1, the 2nd position S2 and the 3rd position S3 to electromagnetic coil a, b output.
And, described rotational speed control device 33 for example according to the quantity of the testing signal that receives from position detector 26 in the time per unit, be the rotational speed of actuating motor 3 and by position S1, S2 or the S3 of the determined electromagnetic switching valve 5 of described control signal, be the work oil mass that each of actuating motor 3 offers load pipeline 15 when deciding angle of swing, detect flow.
In addition, described rotational speed control device 33 generates the rotational speed control signal, and export to described actuating motor 3, is the pressure of described load pipeline 15 and flow control pressure and the flow corresponding with described pressure instruction and flow instruction, wherein, this rotational speed control signal corresponding to and desired flow correspondence from the restriction control signal VL of limitation part 32 and the deviation between the above-mentioned detected flow.This rotational speed control device 33 has the function as driver, and described rotational speed control signal is the AC Motor Control electric current.
The fluid pressure drive device of said structure is according to following described action.
Now, be made as according to pressure instruction and flow instruction and carry out the control of low pressure and mass flow.At this moment, described controller 6 makes described four ports, three position model electromagnetic switching valves 5 be positioned at the 1st position S1.
Like this, flow into from the 1st fixed capacity formula oil hydraulic pump 1 of intermediate size electromagnetic switching valve 5 the 1st input port P1 intermediate flow working oil, flow into the working oil interflow of small flow of the 2nd input port P2 of electromagnetic switching valves 5 with the 2nd fixed capacity formula oil hydraulic pump 2 from small capacity, the liquid of big flow is provided to load pipeline 15 from output port A.
At this moment, described controller 6 is according to the flow instruction of the pressure instruction of expression low pressure, the big flow of expression, from the signal of pressure transducer 25 with from the signal of position detector 26, control the rotational speed of described actuating motor 3, so that the pressure of load pipeline 15 and flow reach described low pressure and big flow.
Like this, when described electromagnetic switching valve 5 is positioned at the 1st position S1, load pipeline 15 is carried out the control of low pressure and mass flow.
Specifically, by 32 pairs of limitation part from pressure control portion 31 outputs of described controller 6, based on the pressure controling signal Vp of the deviation between pressure instruction and the pressure detecting signal, apply the restriction corresponding, and generate restriction control signal VL with flow instruction.And, rotational speed control device 33 is according to this restriction control signal VL and be used to from the signal of position detector 26 and represent the flow that the control signal of described the 1st position S1 calculates, generation is used for the pressure and the flow control of load pipeline 15 are become the rotational speed control signal of pressure and the flow corresponding with pressure instruction and flow instruction, and exports to actuating motor 3.
Like this, apply the restriction corresponding and generate restriction control signal VL, come pilot pressure and flow, so can be accurately and carry out pressure control and flow control swimmingly according to this restriction control signal VL with flow instruction by 32 couples of pressure controling signal Vp of limitation part.
Then, be made as the control of pressing intermediate flow in carrying out according to pressure instruction and flow instruction.
At this moment, described controller 6 makes described four ports, three position model electromagnetic switching valves 5 be positioned at the 2nd position S2.
Like this, the working oil of intermediate flow that flows into the 1st input port P1 of electromagnetic switching valve 5 from the 1st fixed capacity formula oil hydraulic pump 1 of intermediate size is offered load pipeline 15 from output port A, and flow into the working oil of small flow of the 2nd input port P2 of electromagnetic switching valves 5 from the 2nd fixed capacity formula oil hydraulic pump 2 of small capacity, be discharged to the fuel tank T 2 off-loads of the 2nd fixed capacity formula oil hydraulic pump from returning port R.
At this moment, described controller 6 is according to the flow instruction of the pressure instruction of pressing in the expression, expression intermediate flow, from the signal of pressure transducer 25 with from the signal of position detector 26, control the rotational speed of described actuating motor 3, so that the pressure of load pipeline 15 and flow reach described middle the pressure and intermediate flow.
Like this, when described electromagnetic switching valve 5 is positioned at the 2nd position S2, load pipeline 15 is carried out middle control of pressing intermediate flow.
Specifically, by 32 pairs of limitation part from pressure control portion 31 outputs of described controller 6, based on the pressure controling signal Vp of the deviation between pressure instruction and the pressure detecting signal, apply the restriction corresponding, and generate restriction control signal VL with flow instruction.And, rotational speed control device 33 is according to this restriction control signal VL and be used to from the signal of position detector 26 and represent the flow that the control signal of described the 2nd position S2 calculates, generation is used for the pressure and the flow control of load pipeline 15 are become the medium pressure corresponding with pressure instruction and flow instruction and the rotational speed control signal of intermediate flow, and exports to actuating motor 3.
Like this, apply the restriction corresponding and generate restriction control signal VL, come pilot pressure and flow, so can be accurately and carry out pressure control and flow control swimmingly according to this restriction control signal VL with flow instruction by 32 couples of pressure controling signal Vp of limitation part.
Then, be made as according to pressure instruction and flow instruction and carry out the control of high-pressure low-flow.
At this moment, described controller 6 makes described four ports, three position model electromagnetic switching valves 5 be positioned at the 3rd position S3.
Like this, flow into the working oil of intermediate flow of the 1st input port P1 of electromagnetic switching valve 5 from the 1st fixed capacity formula oil hydraulic pump 1 of intermediate size, be discharged to the fuel tank T from returning port R, 1 off-load of the 1st fixed capacity formula oil hydraulic pump, and flow into the working oil of small flow of the 2nd input port P2 of electromagnetic switching valves 5 from the 2nd fixed capacity formula oil hydraulic pump 2 of small capacity, offered load pipeline 15 from output port A.
At this moment, described controller 6 is according to the flow instruction of the pressure instruction of expression high pressure, expression small flow, from the signal of pressure transducer 25 with from the signal of position detector 26, control the rotational speed of described actuating motor 3, so that the pressure and the flow of load pipeline 15 reach described high pressure and small flow.
Like this, when described electromagnetic switching valve 5 is positioned at the 3rd position S3, load pipeline 15 is carried out the control of high-pressure low-flow.
Specifically, by 32 pairs of limitation part from pressure control portion 31 outputs of described controller 6, based on the pressure controling signal Vp of the deviation between pressure instruction and the pressure detecting signal, apply the restriction corresponding, and generate restriction control signal VL with flow instruction.And, rotational speed control device 33 is according to this restriction control signal VL and be used to from the signal of position detector 26 and represent the flow that the control signal of described the 3rd position S3 calculates, generation is used for the pressure and the flow control of load pipeline 15 are become the rotational speed control signal of pressure and the flow corresponding with pressure instruction and flow instruction, and exports to actuating motor 3.
Like this, apply the restriction corresponding and generate restriction control signal VL, come pilot pressure and flow, so can be accurately and carry out pressure control and flow control swimmingly according to this restriction control signal VL with flow instruction by 32 couples of pressure controling signal Vp of limitation part.
Like this, only use one four port, three position model electromagnetic switching valves 5 and above-mentioned linkage structure, can select low pressure and mass flow, middle pressure intermediate flow, the operation mode in these three kinds of stages of high-pressure low-flow, make two suitably off-loads of pump, interflow, reduce 3 needed moments of torsion of actuating motor thus.
Therefore,, can realize high voltage control and big flow control, and can reduce actuating motor 3 and controller 6 needed current values, can make actuating motor 3 and controller 6 miniaturizations, low cost according to this fluid pressure drive device.
In addition, in above-mentioned fluid pressure drive device, owing to current value reduces, so when selecting the control of high pressure low volume, can under high pressure keep-up pressure for a long time.
Then, be made as described electromagnetic switching valve 5 for example since dust etc. be lockable, and stop between the 1st position S1 and the 2nd position S2 or between the 1st position S1 and the 3rd position S3, make the 1st input port P1 and the 2nd input port P2 and output port A and returning between the port R be closed.
At this moment, the pressure of discharge conduit 11,12 will rise, but the 1st one-way valve 21 and the 2nd one-way valve 22 are open, in described electromagnetic switching valve 5 bypass, and offer load pipeline 15 from the working oil of the 1st and the 2nd fixed capacity formula oil hydraulic pump 1,2.Like this, when described electromagnetic switching valve 5 faults, working oil by the 1st one-way valve 21 and the 2nd one-way valve 22 in electromagnetic switching valve 5 bypass, so can prevent breakages such as pipe arrangement pipeline and hydraulic equipment.
In addition, because the working oil that provides from the described the 1st and the 2nd one- way valve 21,22 when making that the pressure of load pipeline 15 will be excessive, can utilize relief valve 23 that working oil is discharged among the fuel tank T, can prevent that pressure is excessive, and prevent the equipment breakage.
In the above-described embodiment, utilize the pressure of pressure transducer 25 direct detection load pipelines 15, but also can utilize current sensor senses to flow to the current value of actuating motor 3, according to this current value indirect detection pressure.
In addition, in the above-described embodiment, with a routine use position detector of sensor, detect flow according to the rotational position and time of actuating motor 3, but the rotational speed that also can directly detect actuating motor 3 detects flow as flow detection.
In addition, the controller that the present invention uses is not limited to the controller 6 of above-mentioned mode of execution, it for example also can be the controller that Japan Patent discloses Fig. 4 record of the 2000-No. 320466 communique with difference selection portion, as long as can come pilot pressure and flow, then can be the controller of any way according to pressure instruction and flow instruction.
Claims (4)
1. a fluid pressure drive device is characterized in that, this fluid pressure drive device has:
The 2nd fixed capacity formula oil hydraulic pump (2) of the 1st fixed capacity formula oil hydraulic pump (1) of the interconnected twin intermediate size of axle and the small capacity littler than described intermediate size;
Four ports, three position model electromagnetic switching valves (5), it has the 1st input port (P1) that is connected with the exhaust port of described the 1st fixed capacity formula oil hydraulic pump (1), the 2nd input port (P2) that is connected with the exhaust port of described the 2nd fixed capacity formula oil hydraulic pump (2), with the output port (A) that is connected of load pipeline (15) be connected with fuel tank (T) return port (R), and have: make the described the 1st and the 2nd input port (P1, P2) be communicated with output port (A), and make and return the 1st position (S1) that port (R) is closed, described the 1st input port (P1) is communicated with output port (A), and make described the 2nd input port (P2) and return the 2nd position (S2) that port (R) is communicated with and make described the 1st input port (P1) and return port (R) and be communicated with, and the 3rd position (S3) that described the 2nd input port (P2) is communicated with output port (A);
Actuating motor (3), it drives described the 1st fixed capacity formula oil hydraulic pump (1) and the 2nd fixed capacity formula oil hydraulic pump (2);
Pressure transducer (25), it directly or indirectly detects the pressure of described load pipeline (15);
Flow detection sensor (26), it detects the rotational position or the speed of described actuating motor (3); And
Controller (6), it accepts the output of described pressure transducer (25) and flow detection usefulness sensor (26), and accept pressure instruction and flow instruction, control described actuating motor (3) and make the pressure of described load pipeline (15) and flow become pressure and the flow corresponding with described pressure instruction and flow instruction.
2. fluid pressure drive device according to claim 1 is characterized in that, this fluid pressure drive device has:
The 1st one-way valve (21), it is connected between the 1st input port (P1) of the exhaust port of described the 1st fixed capacity formula oil hydraulic pump (1) and described electromagnetic switching valve (5) and between the described load pipeline (15), is used to make the mobile forward that becomes towards described load pipeline (15);
The 2nd one-way valve (22), it is connected between the 2nd input port (P2) of the exhaust port of described the 2nd fixed capacity formula oil hydraulic pump (2) and described electromagnetic switching valve (5) and between the described load pipeline (15), is used to make the mobile forward that becomes towards described load pipeline (15).
3. fluid pressure drive device according to claim 1 and 2 is characterized in that, this fluid pressure drive device has the relief valve (23) that is connected with described load pipeline (15).
4. fluid pressure drive device according to claim 1 and 2 is characterized in that, described controller (6) has:
Pressure control portion (31), it accepts described pressure instruction and from the pressure detecting signal of described pressure transducer, according to the deviation delivery pressure control signal (Vp) between described pressure instruction and the described pressure detecting signal;
Limitation part (32), it accepts pressure controling signal and flow instruction from described pressure control portion (31), and output applies the restriction corresponding with described flow instruction to described pressure controling signal and the restriction control signal (VL) that generates; And
Rotational speed control device (33), its basis is from the restriction control signal of described limitation part (32) with from the flow detection signal of described flow detection with sensor (26), generation is used for the pressure of described load pipeline (15) and flow control are the pressure corresponding with described pressure instruction and flow instruction and the rotational speed control signal of flow, and exports to described actuating motor (3).
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP181628/2006 | 2006-06-30 | ||
| JP2006181628A JP4089738B2 (en) | 2006-06-30 | 2006-06-30 | Hydraulic drive device |
| PCT/JP2007/062381 WO2008001657A1 (en) | 2006-06-30 | 2007-06-20 | Fluid pressure drive device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101473138A true CN101473138A (en) | 2009-07-01 |
| CN101473138B CN101473138B (en) | 2011-01-19 |
Family
ID=38845424
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2007800222965A Expired - Fee Related CN101473138B (en) | 2006-06-30 | 2007-06-20 | Fluid pressure drive device |
Country Status (5)
| Country | Link |
|---|---|
| JP (1) | JP4089738B2 (en) |
| KR (1) | KR100984142B1 (en) |
| CN (1) | CN101473138B (en) |
| TW (1) | TW200801335A (en) |
| WO (1) | WO2008001657A1 (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102022400A (en) * | 2009-09-21 | 2011-04-20 | 邵阳维克液压有限责任公司 | System for switching to reserve pump in hydraulic system of ordinary power station |
| CN103568236A (en) * | 2012-08-10 | 2014-02-12 | 三菱重工塑胶科技股份有限公司 | Hydraulic source control device and injection moulding device |
| CN103628723A (en) * | 2013-07-01 | 2014-03-12 | 梁崇彦 | Vehicle bearing plate falling prevention device of mechanical parking equipment |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP5229092B2 (en) * | 2009-04-28 | 2013-07-03 | ダイキン工業株式会社 | Hydraulic control system, injection molding machine and controller |
| CN104122034A (en) * | 2013-04-24 | 2014-10-29 | 哈尔滨飞机工业集团有限责任公司 | Helicopter main blade dynamic balancing test bed hydraulic drive system |
| KR200470454Y1 (en) * | 2013-05-10 | 2013-12-18 | 주식회사 티에이치에스 | motor integrated pump |
| JP6950596B2 (en) * | 2018-03-13 | 2021-10-13 | 宇部興産機械株式会社 | Hydraulic supply system for injection molding machines |
Family Cites Families (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS4910717Y1 (en) * | 1970-04-03 | 1974-03-14 | ||
| JPS6246617A (en) * | 1985-08-26 | 1987-02-28 | Meiki Co Ltd | Controlling of intensified clamping pressure of injection molder |
| JPS6396614A (en) | 1986-10-13 | 1988-04-27 | Ricoh Co Ltd | Ccd integration circuit for autofocus camera |
| JPH0734215Y2 (en) * | 1988-07-21 | 1995-08-02 | 日産自動車株式会社 | Variable displacement radial piston pump |
| JPH02308989A (en) * | 1989-05-22 | 1990-12-21 | Nissan Motor Co Ltd | Variable displacement pump |
| JP2814208B2 (en) * | 1995-02-28 | 1998-10-22 | 日精樹脂工業株式会社 | Control valve and hydraulic drive circuit |
| JP3989991B2 (en) | 1996-10-31 | 2007-10-10 | 株式会社トキメック | Servo motor controller for hydraulic pump drive |
| JP3639754B2 (en) * | 1999-09-24 | 2005-04-20 | ダイキン工業株式会社 | Hydraulic device |
| JP4182896B2 (en) * | 2004-02-20 | 2008-11-19 | トヨタ自動車株式会社 | Pump device and its discharge flow rate control device |
-
2006
- 2006-06-30 JP JP2006181628A patent/JP4089738B2/en active Active
-
2007
- 2007-06-20 WO PCT/JP2007/062381 patent/WO2008001657A1/en active Application Filing
- 2007-06-20 CN CN2007800222965A patent/CN101473138B/en not_active Expired - Fee Related
- 2007-06-20 KR KR1020087027197A patent/KR100984142B1/en active IP Right Grant
- 2007-06-28 TW TW096123552A patent/TW200801335A/en not_active IP Right Cessation
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102022400A (en) * | 2009-09-21 | 2011-04-20 | 邵阳维克液压有限责任公司 | System for switching to reserve pump in hydraulic system of ordinary power station |
| CN103568236A (en) * | 2012-08-10 | 2014-02-12 | 三菱重工塑胶科技股份有限公司 | Hydraulic source control device and injection moulding device |
| CN103568236B (en) * | 2012-08-10 | 2016-08-10 | 三菱重工塑胶科技股份有限公司 | Hydraulic pressure source control device and injection molding device |
| US9657569B2 (en) | 2012-08-10 | 2017-05-23 | Mitubishi Heavy Industries Plastic Technology Co., Ltd. | Hydraulic source control device, injection molding apparatus, and method of controlling hydraulic source |
| CN103628723A (en) * | 2013-07-01 | 2014-03-12 | 梁崇彦 | Vehicle bearing plate falling prevention device of mechanical parking equipment |
Also Published As
| Publication number | Publication date |
|---|---|
| TW200801335A (en) | 2008-01-01 |
| WO2008001657A1 (en) | 2008-01-03 |
| TWI335382B (en) | 2011-01-01 |
| CN101473138B (en) | 2011-01-19 |
| KR20080106987A (en) | 2008-12-09 |
| KR100984142B1 (en) | 2010-09-28 |
| JP4089738B2 (en) | 2008-05-28 |
| JP2008008258A (en) | 2008-01-17 |
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