CN105298782A - Closed hydraulic circuit system - Google Patents

Closed hydraulic circuit system Download PDF

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Publication number
CN105298782A
CN105298782A CN201510671507.4A CN201510671507A CN105298782A CN 105298782 A CN105298782 A CN 105298782A CN 201510671507 A CN201510671507 A CN 201510671507A CN 105298782 A CN105298782 A CN 105298782A
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CN
China
Prior art keywords
pump
port
pressure
pipeline
oil hydraulic
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
CN201510671507.4A
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Chinese (zh)
Inventor
寺田真司
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Sumitomo Heavy Industries Ltd
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Sumitomo Heavy Industries Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from JP2011243809A external-priority patent/JP5628134B2/en
Priority claimed from JP2011243810A external-priority patent/JP5859279B2/en
Application filed by Sumitomo Heavy Industries Ltd filed Critical Sumitomo Heavy Industries Ltd
Publication of CN105298782A publication Critical patent/CN105298782A/en
Pending legal-status Critical Current

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Classifications

    • 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
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/20—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F04B1/22—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block having two or more sets of cylinders or pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/003—Systems with load-holding valves
    • 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
    • F04B49/10—Other safety measures
    • 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
    • F15B20/00—Safety arrangements for fluid actuator systems; Applications of safety devices in fluid actuator systems; Emergency measures for fluid actuator systems
    • F15B20/005—Leakage; Spillage; Hose burst
    • 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
    • F15B2211/20561—Type of pump reversible
    • 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
    • F15B2211/27—Directional control by means of the pressure source
    • 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
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50518—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using pressure relief valves
    • 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
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50563—Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure
    • F15B2211/50581—Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure using counterbalance valves
    • F15B2211/5059—Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure using counterbalance valves using double counterbalance valves
    • 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
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/61—Secondary circuits
    • F15B2211/613—Feeding circuits
    • 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
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7051—Linear output members
    • F15B2211/7053—Double-acting output members
    • F15B2211/7054—Having equal piston areas

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Fluid-Pressure Circuits (AREA)

Abstract

The invention provides a closed hydraulic circuit system. A closed hydraulic circuit system (100) capable of driving a hydraulic cylinder (3) having a first port (3b) and a second port (3c) comprises: a hydraulic pump (1) which has a first pump port (1a) hydraulically connected to the first port (3b) through a first conduit (C1) and which also has a second pump port (1b) hydraulically connected to the second port (3c) through a second conduit (C2); an electric motor (2) which controls the rotation of the hydraulic pump (1); an electric motor control unit (11) which feedback-controls a value relating to an input to the hydraulic motor (2) on the basis of a value relating to an output from the electric motor (2); and a pump state determination section (13) which determines the state of the hydraulic pump (1) on the basis of the value relating to the input to the electric motor (2) and on the basis of the value relating to the output from the electric motor (2).

Description

Hydraulic pressure closed-loop system
The divisional application that the application is the applying date is on September 14th, 2012, application number is 201280044650.5, name is called the Chinese invention patent application of " hydraulic pressure closed-loop system ".
Technical field
The present invention relates to a kind of hydraulic pressure closed-loop system that can drive oil hydraulic cylinder or oil hydraulic motor, particularly relate to a kind of hydraulic pressure closed-loop system possessing oil hydraulic pump by motoring.
Background technique
Conventionally, there is known driven the fluid pressure drive device (such as referenced patent document 1) of oil hydraulic motor by bidirectional hydraulic pump.
In this hydraulic pressure installation, be configured at configuration 4 one-way valves around the bidirectional hydraulic pump between service tank and selector valve.By this structure, fluid pressure drive device realizes following hydraulic pressure open system, even if namely its bidirectional hydraulic pump rotates to any direction, the working oil sucked from service tank also can be made to flow into selector valve with same paths.
22 of being configured at bidirectional hydraulic pump respectively in 4 above-mentioned one-way valves, between port and service tank, prevent the adverse current from bidirectional hydraulic pump to service tank.Its result, when the bidirectional hydraulic pump rotated stops, the pressure more than pressure in each pressure maintenance work oil tank in 2 ports of bidirectional hydraulic pump.
Conventional art document
Patent documentation
Patent documentation 1: Japanese Unexamined Patent Publication 8-310267 publication
Summary of the invention
The technical task that invention will solve
But the device recorded in patent documentation 1 cannot judge that bidirectional hydraulic pump has fault-free.
Further, the configuration of 4 one-way valves recorded in patent documentation 1, only so that working oil can be made to be flowed into for the purpose of selector valve by same port all the time, is not started for the purpose of the rising characteristic of flow when rotating and pressure to improve bidirectional hydraulic pump.Therefore, the device recorded in patent documentation 1 does not have the mechanism of each pressure in 2 ports of the bidirectional hydraulic pump when bidirectional hydraulic pump controlling to rotate stops, and cannot be desired pressure by each Stress control in 2 ports yet.Therefore, the device recorded in patent documentation 1 cannot improve the rising characteristic that bidirectional hydraulic pump starts flow when rotating and pressure.
Point in view of the above problems, the object of the present invention is to provide a kind of hydraulic pressure closed-loop system of the oil hydraulic pump that can more effectively utilize in hydraulic pressure closed-loop system.
For the means of technical solution problem
To achieve these goals, hydraulic pressure closed-loop system involved by embodiments of the invention is can drive to have the oil hydraulic cylinder of the 1st port and the 2nd port or the hydraulic pressure closed-loop system of oil hydraulic motor, wherein, possess: oil hydraulic pump, be there is the 1st pump port be communicated with described 1st port flow by the 1st pipeline and the 2nd pump port be communicated with described 2nd port flow by the 2nd pipeline; Electric motor, controls the rotation of described oil hydraulic pump; Electric motor control unit, carries out feedback control according to the value relevant to the output of the described electric motor pair value relevant with the input of described electric motor; And pump condition judgement portion, the state of described oil hydraulic pump is judged according to the value relevant to the input of described electric motor and the value of being correlated with the output of described electric motor.
And, hydraulic pressure closed-loop system involved by embodiments of the invention is can drive to have the oil hydraulic cylinder of the 1st port and the 2nd port or the hydraulic pressure closed-loop system of oil hydraulic motor, wherein, possess: oil hydraulic pump, be there is the 1st pump port be communicated with described 1st port flow by the 1st pipeline and the 2nd pump port be communicated with described 2nd port flow by the 2nd pipeline; Electric motor, controls the rotation of described oil hydraulic pump; Relief valve, is configured at described 1st pipeline and described 2nd pipeline respectively; And one-way valve, be connected in parallel with described relief valve respectively, and stop working oil from described oil hydraulic pump to described oil hydraulic cylinder or described hydraulic motors.
Invention effect
According to above-mentioned means, the present invention can provide a kind of hydraulic pressure closed-loop system of the oil hydraulic pump that can more effectively utilize in hydraulic pressure closed-loop system.
Accompanying drawing explanation
Fig. 1 is the synoptic diagram of the structure example of the hydraulic pressure closed-loop system represented involved by the 1st embodiment of the present invention.
Fig. 2 is the functional block diagram of the structure example representing control gear.
Fig. 3 is the flow chart of the flow process representing electric motor control treatment.
Fig. 4 is the flow chart of the flow process representing the process of pump condition judgement.
Fig. 5 be the relation represented between the measured value being applicable to the current instruction value of electric motor and the travelling speed of piston figure (one of).
Fig. 6 is the flow chart of the flow process representing the 2nd pump condition judgement process.
Fig. 7 is the figure (two) of the relation represented between the measured value being applicable to the current instruction value of electric motor and the travelling speed of piston.
Fig. 8 is the synoptic diagram of the structure example of the hydraulic pressure closed-loop system represented involved by the 2nd embodiment of the present invention.
Fig. 9 is the figure of the state of the hydraulic pressure closed-loop system represented when the oil hydraulic pump of Fig. 8 is rotated.
Figure 10 is the figure of the state of the hydraulic pressure closed-loop system of the oil hydraulic pump represented in the rotation that makes in Fig. 9 when stopping.
Figure 11 is the sectional view that the cross section of the oil hydraulic pump represented with single dotted broken line Figure 12 is observed in the direction represented from arrow IV.
Figure 12 is the figure that the slip surface of the valve plate comprised in the face represented with single dotted broken line Figure 11 is observed in the direction represented from arrow V.
Figure 13 is the figure of the change of the rise time of the pressure that spues that the oil hydraulic pump produced due to the difference of the setting pressure of relief valve is described.
Figure 14 is the synoptic diagram of the structure example of the hydraulic pressure closed-loop system represented involved by the 3rd embodiment of the present invention.
Embodiment
Below, with reference to accompanying drawing, embodiments of the invention are described.
Embodiment 1
Fig. 1 is the synoptic diagram of the structure example of the hydraulic pressure closed-loop system 100 represented involved by the 1st embodiment of the present invention.
Hydraulic pressure closed-loop system 100 utilizes to rotate by electric motor 2 system that the oil hydraulic pump 1 controlled drives oil hydraulic cylinder 3.Oil hydraulic cylinder 3 such as uses as by the worktable of the large load capacity hydraulic drive type Large Plane Grinder of control device in order to mobile.
In the present embodiment, hydraulic pressure closed-loop system 100 is formed primarily of oil hydraulic pump 1, electric motor 2, oil hydraulic cylinder 3, safety valve 4L, 4R, reciprocable valve 7, output detections sensor 9, control gear 10, input device 15, display unit 16 and instantaneous speech power 17.
Oil hydraulic pump 1 is the device driving oil hydraulic cylinder 3, such as, be fixed capacity type bidirectional hydraulic pump.In addition, oil hydraulic pump 1 can be variable displacement pump.
Electric motor 2 is the device of the rotation of hydraulic control pump 1, such as, be the AC servomotor of variable speed.
Oil hydraulic cylinder 3 is for having the hydraulic unit driver of the 1st grease chamber 3L and the 2nd grease chamber 3R separated by piston 3a.1st grease chamber 3L is communicated with the 1st pump port one a fluid of oil hydraulic pump 1 by the 1st port 3b and pipeline C1, and the 2nd grease chamber 3R is communicated with the 2nd pump port one b fluid of oil hydraulic pump 1 by the 2nd port 3c and pipeline C2.In the present embodiment, the double piston-rod cylinder of 2 bars that oil hydraulic cylinder 3 extends for the both sides possessed along piston 3a, one or two and surface grinding machine worktable (not shown) in 2 bars combine.In addition, oil hydraulic cylinder 3 can be the single piston rod cylinder of 1 bar of the one-sided extension possessed along piston 3a, also can be surface grinding machine worktable be directly combined with piston 3a without bar structure.
Safety valve 4L is the valve of releasing the working oil in pipeline C1 when becoming more than authorized pressure for the pressure in pipeline C1 to service tank T1.Further, safety valve 4R is the valve of releasing the working oil in pipeline C2 when becoming more than authorized pressure for the pressure in pipeline C2 to service tank T1.
Safety valve 4L is configured at and links on the pipeline C4 of pipeline C3 and the pipeline C1 be communicated with service tank T1 fluid, and safety valve 4R is configured on the pipeline C5 of link pipeline C3 and pipeline C2.
Reciprocable valve 7 is the valve of the flowing of pilot line C1 or the working oil between pipeline C2 and service tank T1, has 1 a first side port 7a and 2 secondary port 7b, 7c.
First side port 7a is communicated with service tank T1 fluid via pipeline C11, and a 7b in secondary port is communicated with pipeline C1 fluid via pipeline C7, and another 7c in secondary port is communicated with pipeline C2 fluid via pipeline C8.
Specifically, when the pressure of the pressure in pipeline C1 lower than service tank T1, reciprocable valve 7 imports the working oil of service tank T1 in pipeline C1 by secondary port 7b.Further, when the pressure of the pressure in pipeline C2 lower than service tank T1, reciprocable valve 7 imports the working oil of service tank T1 in pipeline C2 by secondary port 7c.The deficiency of the working oil in this pipeline C1 be rotation etc. in order to make up due to oil hydraulic pump 1 and produce or pipeline C2.
Output detections sensor 9 is the sensor detecting the value relevant to the output of electric motor 2, such as, comprise: the 2nd discharge-amount sensor 9c2 etc. detecting the position transducer 9a of the position of piston 3a, detect the turn-sensitive device 9b of the rotation of oil hydraulic pump 1, detect the 1st discharge-amount sensor 9c1 of the discharge-amount of the 1st pump port one a from oil hydraulic pump 1 and detect from the discharge-amount of the 2nd pump port one b of oil hydraulic pump 1.Further, the value that goes out of output detections sensor 9 pairs of control gear 10 output detections.
Control gear 10 is the device for hydraulic control closed-loop system 100, such as, for possessing the computer of CPU, RAM, ROM, input/output interface etc.
Further, control gear 10, according to the input of the operator inputted via input device 15, determines the distance (distance of current location to target location) of the required movement of surface grinding machine worktable, namely determines the distance of the required movement of piston 3a.And, the distance of control gear 10 movement needed for determined piston 3a determines the target travelling speed (movement direction of piston 3a is represented by the positive and negative of value of target travelling speed) of piston 3a, and exports the control command corresponding with determined target travelling speed to electric motor 2.Specifically, control gear 10 controls to be that the distance of movement needed for piston 3a more general objective travelling speed more becomes large.Further, control gear 10 controls to be, along with the diminishing of distance of movement needed for piston 3a, namely along with close target location, target travelling speed is slowed down.
Further, control gear 10, according to the output of position transducer 9a, monitors the position of piston 3a, i.e. the position of surface grinding machine worktable, and judges whether surface grinding machine worktable arrives target location.
When being judged to be that surface grinding machine worktable has arrived target location, control gear 10 pairs of electric motors 2 export the control command of the rotation being used for stop solution press pump 1.
Input device 15 is operator can input various information devices to control gear 10, such as, be hardware button, keyboard, mouse, touch panel etc.
Display unit 16 is the device showing the various information exported by control gear 10, such as, be liquid crystal display, LED etc.
Instantaneous speech power 17 is the device of the various information that voice output is exported by control gear 10, such as, be loudspeaker, buzzer etc.
Then, with reference to figure 2, the various function important documents that control gear 10 has are described.In addition, Fig. 2 is the functional block diagram of the structure example representing control gear 10.
Control gear 10 reads the program corresponding with each function important document in electric motor control unit 11, pump efficiency calculating part 12 and pump condition judgement portion 13 from ROM and launches to RAM, makes the process that CPU execution is corresponding with each program.
Electric motor control unit 11 is the function important document controlling electric motor 2, such as, generate the control command for controlling electric motor 2 according to various information, and electric motor 2 is exported to the control command generated.
At this, with reference to figure 3, the flow process of the process (hereinafter referred to as " electric motor control treatment ") that electric motor control unit 11 pairs of electric motors 2 control is described.In addition, Fig. 3 is the flow chart of the flow process representing electric motor control treatment, and electric motor control unit 11 performs this electric motor control treatment repeatedly with specified period.
First, electric motor control unit 11 determines the control objectives value (step S1) of electric motor 2 according to the target travelling speed of piston 3a.In the present embodiment, the numerical value that control gear 10 such as inputs via input device 15 according to operator determines the distance of movement needed for the piston 3a as control objectives value.And the distance of control gear 10 movement needed for piston 3a determines the target travelling speed of piston 3a.
Afterwards, electric motor control unit 11 obtains the measured value (step S2) corresponding with control objectives value exported by output detections sensor 9.In the present embodiment, electric motor control unit 11 obtains the actual travelling speed of piston 3a according to the output of position transducer 9a.
Afterwards, in order to offset the difference of control objectives value and the measured value corresponding with this control objectives value, electric motor control unit 11 generates control command value (step S3) by feedback control, and electric motor 2 is exported to the control command value (step S4) generated.In the present embodiment, in order to offset the difference of the actual measurement travelling speed (displacement distance of time per unit) of the output of target travelling speed and position-based sensor 9a, electric motor control unit 11 formation speed command value, and electric motor 2 is exported to the speed value generated.
With this, electric motor control unit 11 is controlled by the rotating speed of feedback to electric motor 2 of the travelling speed of piston 3a.In addition, electric motor control unit 11 can according to speed value calculating torque command value (current instruction value), and control the torque of electric motor 2, so that by feeding back the output of the galvanometer (not shown) being determined at the electric current flowed in electric motor 2, the difference of cancellation current command value and measured current value.
Its result, the state of the constitutive requirements no matter electric motor control unit 11 exists between piston 3a and electric motor 2 how, namely regardless of the quality of the state of oil hydraulic pump 1, by controlling electric motor 2, can realize the desired travelling speed of piston 3a.Therefore, such as, even if the actual discharge-amount of the oil hydraulic pump 1 corresponding with the rotating speed that electric motor 2 gives is less than the discharge-amount of expection, electric motor control unit 11 operator also can not be made to find this state moves with desired travelling speed with regard to making piston 3a.This is because in order to realize the stability controlled, the discharge-amount that the rising along with the rotating speed of electric motor 2 makes up oil hydraulic pump 1 is automatically not enough.
In addition, in the present embodiment, electric motor control unit 11 adopts the target travelling speed of piston 3a as control objectives value, but the target discharge-amount of the rotating speed of target of oil hydraulic pump 1 or oil hydraulic pump 1 also can be adopted to be used as control objectives value.Now, electric motor control unit 11 obtains the rotating speed of the oil hydraulic pump 1 exported by turn-sensitive device 9b or is used as the measured value corresponding with control objectives value by the discharge-amount of the oil hydraulic pump 1 of the 1st discharge-amount sensor 9c1 or the 2nd discharge-amount sensor 9c2 output.
Pump efficiency calculating part 12 is the function important document of the pump efficiency calculating oil hydraulic pump 1.
" pump efficiency " refers to the efficiency that spues of oil hydraulic pump 1, such as, calculate according to the value relevant to the input of electric motor 2 and the value relevant with the output of electric motor 2.Substantially, pump efficiency is the value declined through the deterioration year in year out namely along with oil hydraulic pump 1 along with the time, during lower than specified value, represents and needs to change or maintenance (hereinafter referred to as " replacing ") oil hydraulic pump 1.
In the present embodiment, pump efficiency adopts by electric motor 2 according to the actual value of travelling speed divided by its control command value rotating the piston 3a realized of the control command value being input to electric motor 2.
Pump condition judgement portion 13 is the function important document of the state judging oil hydraulic pump 1, such as, judge whether the state of current oil hydraulic pump 1 is suitable for continuing to use.
At this, with reference to figure 4 and Fig. 5, pump condition judgement portion 13 is judged to the flow process of the process (hereinafter referred to as " process of pump condition judgement ") of the state of oil hydraulic pump 1 is described.In addition, Fig. 4 is the flow chart of the flow process representing the process of pump condition judgement, and pump condition judgement portion 13 performs this pump condition judgement process repeatedly with specified period.Further, Fig. 5 is the figure of the relation between the measured value of the travelling speed representing current instruction value and the piston 3a being applicable to electric motor 2, and transverse axis represents current instruction value, and the longitudinal axis represents the measured value of the travelling speed of piston 3a.
First, pump condition judgement portion 13 obtains the control command value exported by electric motor control unit 11 pairs of electric motors 2 and is used as the value (step S11) relevant to the input of electric motor 2.In the present embodiment, pump condition judgement portion 13 obtains the current instruction value D1 as control command value.
Afterwards, pump condition judgement portion 13 obtains the value (step S12) relevant to the output of the electric motor 2 realized because this control command value is applicable to electric motor 2.In the present embodiment, pump condition judgement portion 13 obtains the actual travelling speed V1 of piston 3a according to the output of position transducer 9a, and the actual travelling speed of described piston is applicable to electric motor 2 by current instruction value D1 and causes the rotating speed of electric motor 2 to change and realize.
Afterwards, pump condition judgement portion 13 is according to by the control command value being applicable to electric motor 2 and the measured value produced obtains reference instruction value (step S13).In the present embodiment, pump condition judgement portion 13 obtains reference instruction value Ds according to the actual travelling speed V1 by the current instruction value D1 and the piston 3a produced that are applicable to electric motor 2.
" reference instruction value " refers to the control command value as benchmark needed to realize the regulation measured value relevant to the output of electric motor 2.In the present embodiment, when reference instruction value is such as equivalent to use hydraulic pressure closed-loop system 100 in the early stage, in order to realize the regulation travelling speed of piston 3a and the current instruction value needed.Reference instruction value is such as associated with each value of the travelling speed of piston 3a and is pre-stored within the form of corresponding table in the ROM of control gear 10.The dotted line of Fig. 5 is the line segment representing the benchmark pump efficiency determined by the travelling speed of reference instruction value and piston 3a.Represent in Fig. 5 that the line segment of benchmark pump efficiency represents, suppose that current instruction value D1 is reference instruction value, then can realize the travelling speed V2 of piston 3a.On the other hand, the solid line of Fig. 5 is the line segment representing the current pump efficiency inferred by the actual travelling speed V1 of current current instruction value D1 and piston 3a.Further, the single dotted broken line of Fig. 5 represents according to allowing the line segment of allowing lower limit pump efficiency that the travelling speed of maximum command value with the piston 3a be suitable for when this allows maximum command value determines.
" allow maximum command value " and refer to realize the regulation measured value relevant to the output of electric motor 2 and maximum control command value applicatory.In the present embodiment, allow that maximum command value is such as equivalent to regulation travelling speed in order to realize piston 3a and maximum current command value applicatory.When needing to exceed the current instruction value of allowing maximum command value to realize the regulation travelling speed of piston 3a, namely pump efficiency is lower than when allowing lower limit pump efficiency, can be inferred as in oil hydraulic pump 1 and have exception.In addition, the diagonal line hatches region representation pump efficiency of Fig. 5 is lower than the region of allowing lower limit pump efficiency.
Specifically, pump condition judgement portion 13 with reference to be stored in the ROM of control gear 10, store the travelling speed of piston 3a and the corresponding table of the relation between reference instruction value, obtain the travelling speed V1 in order to realize piston 3a and the reference instruction value Ds that needs.
Afterwards, pump condition judgement portion 13 calculates the difference Δ D (step S14) of acquired reference instruction value Ds and current current instruction value D1, compares (step S15) the poor Δ D calculated and defined threshold Δ Dmax.In addition, defined threshold Δ dmax is such as associated with reference instruction value Ds for the allowable maximum as the difference relative to reference instruction value Ds and is pre-stored within the value in the ROM of control gear 10, prepares value corresponding with each reference instruction value respectively in advance.
Further, the value becoming the poor Δ D of comparison other can be momentary value, also can be based in specified time limit the statistical value (being such as mean value, median, minimum value, maximum value, mode etc.) of the value of the multiple poor Δ D continuing to calculate.
When being judged as that the value of difference Δ D exceedes defined threshold Δ Dmax (step S15 is), pump condition judgement portion 13 is judged to be that the state of current oil hydraulic pump 1 is unsuitable for continuing to use.
Now, at least one in 13 pairs, pump condition judgement portion display unit 16 and instantaneous speech power 17 exports control signal, notify that the state of current oil hydraulic pump 1 is unsuitable for continuing to use (step S16) to operator, terminate this pump condition judgement process afterwards.
On the other hand, when the value being judged as difference Δ D is defined threshold below Δ Dmax (step S15's is no), pump condition judgement portion 13 is judged to be that the state of current oil hydraulic pump 1 is suitable for continuing to use.
Now, pump condition judgement portion 13 does not export to display unit 16 and instantaneous speech power 17 the pump condition judgement process that control signal just terminates this.
In addition, pump condition judgement portion 13 can judge the state of oil hydraulic pump 1 respectively for each sense of rotation of oil hydraulic pump 1.This is because the state of oil hydraulic pump 1 likely only becomes abnormal in specific sense of rotation, therefore carries out the judgement of above-mentioned all directions to can more early detect this abnormal state.
So, the difference of the reference instruction value Ds that hydraulic pressure closed-loop system 100 derives with the travelling speed V1 of the piston 3a from the value of being correlated with as the output with electric motor 2 according to the current instruction value D1 as the value relevant to the input of electric motor 2, judges the state of oil hydraulic pump 1.Its result, hydraulic pressure closed-loop system 100 also can judge the state of oil hydraulic pump 1 at the operating environment During of oil hydraulic pump 1.Further, hydraulic pressure closed-loop system 100 can more early detect following problem: the increase of the energy loss of the reduction of the pump efficiency of the oil hydraulic pump 1 that adjoint deterioration year in year out etc. causes.Further, hydraulic pressure closed-loop system 100 more early can notify to operator the necessity changing oil hydraulic pump 1 grade, and can realize reduction etc. that is energy-conservation, operating cost.
And, hydraulic pressure closed-loop system 100 only arranges oil hydraulic pump 1 as the main composition important document existed between electric motor 2 and oil hydraulic cylinder 3, and one is set up to oil hydraulic pump 1 and oil hydraulic cylinder 3, the travelling speed of piston 3a is adopted thus as the value relevant to the output of electric motor 2.Its result, hydraulic pressure closed-loop system 100 can detect the value relevant to the output of electric motor 2 like a cork.
Then, with reference to figure 6 and Fig. 7, other embodiments (hereinafter referred to as " the 2nd pump condition judgement process ") of pump condition judgement process are described.In addition, Fig. 6 is the flow chart of the flow process representing the 2nd pump condition judgement process, and pump condition judgement portion 13 performs the 2nd pump condition judgement process repeatedly with specified period.Further, Fig. 7 is the figure of the relation of the measured value of the travelling speed representing current instruction value and the piston 3a being applicable to electric motor 2, corresponding with Fig. 5.
First, pump condition judgement portion 13 obtains the control command value exported by electric motor control unit 11 pairs of electric motors 2 and is used as the value (step S21) relevant to the input of electric motor 2.In the present embodiment, pump condition judgement portion 13 obtains the current instruction value as control command value.
Afterwards, pump condition judgement portion 13 obtains the value (step S22) relevant to the output of the electric motor 2 realized because this control command value is applicable to electric motor 2.In the present embodiment, pump condition judgement portion 13 obtains according to the output of position transducer 9a and causes the rotating speed of electric motor 2 to change and the actual travelling speed V1 of the piston 3a realized because current instruction value D1 is applicable to electric motor 2.
Afterwards, pump condition judgement portion 13 obtains by pump efficiency calculating part 12 according to the control command value being applicable to electric motor 2 and the pump efficiency (step S23) calculated by the measured value of this control command value generation.In the present embodiment, pump condition judgement portion 13 obtains the pump efficiency θ (=travelling speed V1 ÷ current instruction value D1) calculated according to the actual travelling speed V1 of the current instruction value D1 and piston 3a that are applicable to electric motor 2 by pump efficiency calculating part 12.
Afterwards, to acquired pump efficiency θ and regulation, pump condition judgement portion 13 allows that lower limit pump efficiency θ min compares (step S24).In addition, regulation allow lower limit pump efficiency θ min such as according to allowing maximum command value and being suitable for the value of travelling speed decision of piston 3a when this allows maximum command value, it is pre-stored within the ROM of control gear 10.Further, the pump efficiency θ becoming comparison other can be momentary value, also can be based in specified time limit the statistical value (being such as mean value, median, minimum value, maximum value, mode etc.) of the multiple pump efficiency continuing to calculate.
Be judged as acquired pump efficiency θ lower than regulation allow lower limit pump efficiency θ min time (step S24 is), pump condition judgement portion 13 is judged to be that the state of current oil hydraulic pump 1 is unsuitable for continuing to use.
Now, at least one in 13 pairs, pump condition judgement portion display unit 16 and instantaneous speech power 17 exports control signal, notify that the state of current oil hydraulic pump 1 is unsuitable for continuing to use (step S25) to operator, terminate this 2nd pump condition judgement process afterwards.
On the other hand, be judged as acquired pump efficiency θ be regulation allow lower limit more than pump efficiency θ min time (step S24's is no), pump condition judgement portion 13 is judged to be that the state of current oil hydraulic pump 1 is suitable for continuing to use.
Now, pump condition judgement portion 13 does not export to display unit 16 and instantaneous speech power 17 the 2nd pump condition judgement process that control signal just terminates this.
In addition, pump condition judgement portion 13 also can judge the state of oil hydraulic pump 1 respectively for each sense of rotation of oil hydraulic pump 1.This is because the state of oil hydraulic pump 1 likely only becomes abnormal in specific sense of rotation, therefore carries out the judgement of above-mentioned all directions to can more early detect this abnormal state.
So, hydraulic pressure closed-loop system 100, according to from the current instruction value D1 as the value relevant to the input of the electric motor 2 and pump efficiency θ that derives as the travelling speed V1 of the piston 3a of the value of being correlated with the output of electric motor 2 and comparing of allowing that lower limit pump efficiency θ min carries out, judges the state of oil hydraulic pump 1.Its result, hydraulic pressure closed-loop system 100 also can judge the state of oil hydraulic pump 1 at the operating environment During of oil hydraulic pump 1.Further, hydraulic pressure closed-loop system 100 more early can detect the following problem of companion: the increase of the energy loss of the reduction of the pump efficiency of the oil hydraulic pump 1 caused with deterioration year in year out.Further, hydraulic pressure closed-loop system 100 more early can notify to operator the necessity changing oil hydraulic pump 1 grade, can realize reduction etc. that is energy-conservation, operating cost.
And, hydraulic pressure closed-loop system 100 only arranges oil hydraulic pump 1 as the main composition important document existed between electric motor 2 and oil hydraulic cylinder 3, and one is set up to oil hydraulic pump 1 and oil hydraulic cylinder 3, the travelling speed of piston 3a is adopted thus as the value relevant to the output of electric motor 2.Its result, hydraulic pressure closed-loop system 100 can detect the value relevant to the output of electric motor 2 like a cork.
Embodiment 2
Fig. 8 is the synoptic diagram of the structure example of the hydraulic pressure closed-loop system 100A represented involved by the 2nd embodiment of the present invention.In addition, in Fig. 8, in order to make figure more clear, omit the diagram of input device 15, display unit 16, instantaneous speech power 17, speed probe 9b, the 1st discharge-amount sensor 9c1 and the 2nd discharge-amount sensor 9c2.Further, hydraulic pressure closed-loop system 100A can be the structure without input device 15, display unit 16, instantaneous speech power 17, speed probe 9b, the 1st discharge-amount sensor 9c1 and the 2nd discharge-amount sensor 9c2.
Hydraulic pressure closed-loop system 100A utilizes to rotate by electric motor 2 system that the oil hydraulic pump 1 controlled drives oil hydraulic cylinder 3.Oil hydraulic cylinder 3 is such as in order to drive the worktable of large load capacity hydraulic drive type Large Plane Grinder to use.
In the present embodiment, hydraulic pressure closed-loop system 100A is formed primarily of oil hydraulic pump 1, electric motor 2, oil hydraulic cylinder 3, safety valve 4L, 4R, reciprocable valve 7, sensor 9, control gear 10, relief valve 20L, 20R and one-way valve 21L, 21R.
Oil hydraulic pump 1 is the device driving oil hydraulic cylinder 3, such as, be the ramp type bi-directional axial reciprocating pump of fixed capacity type or variable capacity type.In addition, oil hydraulic pump 1 can be the angletype axial piston pump of fixed capacity type or variable capacity type, also can be the radial piston pump of fixed capacity type or variable capacity type.
Electric motor 2 is the device of the rotation of hydraulic control pump 1, such as, be AC servomotor.Specifically, the rotating speed of electric motor 2 such as variable hydraulic control pump 1.
Oil hydraulic cylinder 3 is for having the hydraulic unit driver of the 1st grease chamber 3L and the 2nd grease chamber 3R separated by piston 3a.1st grease chamber 3L is communicated with the 1st pump port one a fluid of oil hydraulic pump 1 by the 1st port 3b and pipeline C1, and the 2nd grease chamber 3R is communicated with the 2nd pump port one b fluid of oil hydraulic pump 1 by the 2nd port 3c and pipeline C2.In the present embodiment, the double piston-rod cylinder of 2 bars that oil hydraulic cylinder 3 extends for the both sides possessed along piston 3a, one or two and surface grinding machine worktable (not shown) in 2 bars combine.In addition, oil hydraulic cylinder 3 can be the single piston rod cylinder of 1 bar of the one-sided extension possessed along piston 3a, also can be surface grinding machine worktable be directly combined with piston 3a without bar structure.
Safety valve 4L is the valve of releasing the working oil in pipeline C1 when becoming more than authorized pressure for the pressure in pipeline C1 to service tank T1.Further, safety valve 4R is the valve of releasing the working oil in pipeline C2 when becoming more than authorized pressure for the pressure in pipeline C2 to service tank T1.
Safety valve 4L is configured at and links on the pipeline C4 of pipeline C3 and the pipeline C1 be communicated with service tank T1 fluid, and safety valve 4R is configured on the pipeline C5 of link pipeline C3 and pipeline C2.
Reciprocable valve 7 is the valve of the flowing of pilot line C1 or the working oil between pipeline C2 and service tank T1, has 1 a first side port 7a and 2 secondary port 7b, 7c.
First side port 7a is communicated with service tank T1 fluid via pipeline C11, and a 7b in secondary port is communicated with pipeline C1 fluid via pipeline C7, and another 7c in secondary port is communicated with pipeline C2 fluid via pipeline C8.
Specifically, when the pressure of the pressure in pipeline C1 lower than service tank T1, reciprocable valve 7 imports the working oil of service tank T1 in pipeline C1 by secondary port 7b.Further, when the pressure of the pressure in pipeline C2 lower than service tank T1, reciprocable valve 7 imports the working oil of service tank T1 in pipeline C2 by secondary port 7c.
So, when oil hydraulic pump 1 rotates, when the pressure of the working oil in pipeline C1 and pipeline C2 becomes the pressure lower than the working oil in service tank T1, when namely working oil is not enough, reciprocable valve 7 is compensated its defect by the working oil in service tank T1.
Sensor 9a is the sensor of the operating state detecting oil hydraulic cylinder 3, such as, for detecting the position transducer of the displacement of piston 3a.The value that sensor 9a goes out control gear 10 output detections.
Control gear 10 is the device for hydraulic control closed-loop system 100A, such as, for possessing the computer of CPU, RAM, ROM, input/output interface etc.
Further, control gear 10 determines the distance (distance of current location to target location) of movement needed for surface grinding machine worktable according to the input of user, i.e. the distance of the required movement of piston 3a.And the distance of control gear 10 movement needed for determined piston 3a determines sense of rotation and the rotating speed of oil hydraulic pump 1, and exports the control signal corresponding with the sense of rotation of determined oil hydraulic pump 1 and rotating speed to electric motor 2.Specifically, control gear 10 more becomes with the rotating speed of the larger oil hydraulic pump of distance 1 of movement needed for piston 3a the rotating speed that large mode determines oil hydraulic pump 1.Further, control gear 10 determines the rotating speed of oil hydraulic pump 1, so that along with the reducing of distance of movement needed for piston 3a, namely along with near target location, and the spin down of oil hydraulic pump 1.
Further, control gear 10 monitors the position of piston 3a according to the output of sensor 9a, i.e. the position of surface grinding machine worktable, and judges whether surface grinding machine worktable arrives target location.
When being judged to be that surface grinding machine worktable has arrived target location, control gear 10 pairs of electric motors 2 export the control signal of the rotation being used for stop solution press pump 1.
Relief valve 20L is arranged on pipeline C1, when the pressure of the working oil of first side (part of the pipeline C1 between oil hydraulic pump 1 and relief valve 20L) be the setting specified press above time valve opening, the valve closing when setting pressure lower than regulation of the pressure of the working oil of first side.
Relief valve 20R is arranged on pipeline C2, when the pressure of the working oil of first side (part of the pipeline C2 between oil hydraulic pump 1 and relief valve 20R) be the setting specified press above time valve opening, the valve closing when setting pressure lower than regulation of the pressure of the working oil of first side.
In addition, the setting pressure of the regulation of relief valve 20L is installed with the setting of the regulation of relief valve 20R and is decided to be identical value.Further, the setting of the regulation of relief valve 20L, 20R is installed with the value of the setting pressure of the regulation be decided to be lower than safety valve 4L, 4R.
One-way valve 21L is the valve of the flowing of working oil in pilot line C1.Specifically, one-way valve 21L be configured at the first side of relief valve 20L is communicated with second side (part of the pipeline C1 between relief valve 20L with oil hydraulic cylinder 3) fluid pipeline C12 on.And, one-way valve 21L forbids that working oil flows from the first side of relief valve 20L to the second side of relief valve 20L, only when pressure lower than the second side of relief valve 20L of the pressure of the first side of relief valve 20L, the first side to relief valve 20L imports the working oil of the second side of relief valve 20L.
One-way valve 21R is the valve of the flowing of working oil in pilot line C2.Specifically, one-way valve 21R be configured at the first side of relief valve 20R is communicated with second side (part of the pipeline C2 between relief valve 20R with oil hydraulic cylinder 3) fluid pipeline C13 on.And, one-way valve 21R forbids that working oil flows from the first side of relief valve 20R to the second side of relief valve 20R, only when pressure lower than the second side of relief valve 20R of the pressure of the first side of relief valve 20R, the first side to relief valve 20R imports the working oil of the second side of relief valve 20R.
Then, with reference to figure 9, the state of hydraulic pressure closed-loop system 100A when rotating making oil hydraulic pump 1 is described.In addition, in Fig. 9, black heavy line represents the state of the pressure in pipeline C1, C4, C7 and C12 higher than the setting pressure of relief valve 20L.Further, grey heavy line represents the state of the pressure in pipeline C2, C5, C8 and C13 lower than the setting pressure of relief valve 20R.In addition, in Fig. 9, in order to make figure more clear, omit the diagram of sensor 9a and control gear 10.
As shown in Figure 9, hydraulic pressure closed-loop system 100A makes oil hydraulic pump 1 rotate according to the input of operator by electric motor 2, and to make piston 3a (surface grinding machine worktable) drive to the mode of the direction movement represented with arrow A R4 oil hydraulic cylinder 3.
If oil hydraulic pump 1 is rotated by electric motor 2, then oil hydraulic pump 1 to spue working oil from the 1st pump port one a, is formed towards the flowing of the working oil of relief valve 20L (reference arrow AR1).In addition in pipeline C12, due to the existence of one-way valve 21L, the flowing of working oil can not be formed.
Its result, the degree of compression of the working oil of the first side of relief valve 20L increases and pressure increase, if this first side pressure reaches the setting pressure of relief valve 20L, then relief valve 20L valve opening.
On the other hand, if oil hydraulic pump 1 is rotated by electric motor 2, then oil hydraulic pump 1 makes working oil enter the 2nd pump port one b, and forms the flowing (reference arrow AR9) from relief valve 20R and one-way valve 21R towards the working oil of oil hydraulic pump 1.
When oil hydraulic pump 1 starts to rotate, the introduction volume of the 2nd pump port one b of oil hydraulic pump 1 exceedes the discharge of the working oil of the 2nd port 3c by oil hydraulic cylinder 3 described later.Its result, the degree of compression of the working oil of the first side of relief valve 20R reduces and pressure drop.If the pressure of the working oil of the first side of relief valve 20R is lower than the setting pressure of relief valve 20R, then relief valve 20R valve closing.
If relief valve 20L valve opening, then in oil hydraulic pump 1, to spue working oil from the 1st pump port one a, form the flowing (reference arrow AR2 and AR3) towards the working oil of the 1st port 3b of oil hydraulic cylinder 3 via relief valve 20L thus.In addition, in pipeline C4, the flowing of working oil can not be formed due to the existence of safety valve 4L, in pipeline C7, also can not form the flowing of working oil due to the existence of reciprocable valve 7.
If working oil flows into the 1st grease chamber 3L by the 1st port 3b of oil hydraulic cylinder 3, then the direction that the piston 3a of oil hydraulic cylinder 3 increases to the volume of the 1st grease chamber 3L is moved, and namely moves (reference arrow AR4) to the right direction in figure.
If piston 3a right direction moves, then the volume of the 2nd grease chamber 3R reduces, and the working oil in the 2nd grease chamber 3R is flowed out to pipeline C2 by the 2nd port 3c.
With this, oil hydraulic pump 1 forms the flowing (reference arrow AR5 and AR6) from the 2nd port 3c of oil hydraulic cylinder 3 towards the working oil of relief valve 20R and one-way valve 21R.In addition, relief valve 20R switches valve opening, valve closing according to the pressure of its first side, but can not switch valve opening, valve closing according to the pressure of its second side.Further, when pressure lower than the second side of relief valve 20R of the pressure of the first side of relief valve 20R, one-way valve 21R imports the working oil of the second side of relief valve 20R to the first side of relief valve 20R.In addition, the working oil in pipeline C2 introduces oil hydraulic pump 1 by the rotation of oil hydraulic pump 1, and therefore the pressure of the first side of relief valve 20R becomes the second side lower than relief valve 20R.
Its result, oil hydraulic pump 1 forms the flowing (reference arrow AR5 ~ AR8) of the working oil of the 2nd port 3c by pipeline C13 and one-way valve 21R towards the 2nd pump port one b of oil hydraulic pump 1 from oil hydraulic cylinder 3.In addition, in Fig. 9, the pressure of the first side of relief valve 20R is lower than the setting pressure of relief valve 20R.Therefore, can not be formed by relief valve 20R, from the second side of relief valve 20R towards the flowing of the working oil of the first side of relief valve 20R.But, when the pressure of the first side of relief valve 20R is higher than setting pressure, formed by relief valve 20R, from the second side of relief valve 20R towards the flowing of the working oil of the first side of relief valve 20R.
In addition, if the pressure in pipeline C2 is lower than the pressure of service tank T1, then reciprocable valve 7 supplies the working oil of service tank T1 to pipeline C2 by secondary port 7c and pipeline C8.The pressure be flowing in pipeline C2 of this working oil disappears when reaching the pressure of service tank T1.
And, in Fig. 9, representatively exemplify the state of hydraulic pressure closed-loop system 100A when piston 3a is moved to the right, but when making piston 3a move to the left, except working oil flowing direction contrary with about its pressure state except, also can be suitable for same explanation.
Then, with reference to Figure 10 ~ Figure 12, the state of hydraulic pressure closed-loop system 100A during oil hydraulic pump 1 in the rotation that stopped in Fig. 9 is described.In addition, Tu10Zhong, the thick dotted line of black represents that pressure in pipeline C1, C4, C7 and C12 and oil hydraulic pump 1 press equal state with the pressure between relief valve 20R with one-way valve 21R with the setting of relief valve 20L, 20R.Further, grey heavy line represents pressure in pipeline C5 and C8 and oil hydraulic cylinder 3 and the pressure between relief valve 20R and the one-way valve 21R state lower than the setting pressure of relief valve 20R.In addition, Tu10Zhong, in order to make figure more clear, omits the diagram of sensor 9a and control gear 10.
Figure 11 and Figure 12 is the synoptic diagram of the structure for illustration of oil hydraulic pump 1, Figure 11 is the sectional view that the cross section of the oil hydraulic pump 1 represented with single dotted broken line Figure 12 is observed in the direction represented from arrow IV, and Figure 12 is the figure that the slip surface 40a of the valve plate 40 comprised in the face represented with single dotted broken line Figure 11 is observed in the direction represented from arrow V.In addition, the oil hydraulic pump 1 shown in Figure 11 and Figure 12 is in rotation status, and the 1st pump port one a forms the port that spues, and the 2nd pump port one b forms inhalation port.Further, the highdensity dot pattern in Figure 11 and Figure 12 represents that the situation that the pressure ratio of the working oil of the 1st pump port one a is higher, low-density dot pattern represent the situation that the pressure ratio of the working oil of the 2nd pump port one b is lower.
As shown in FIG. 11 and 12, oil hydraulic pump 1 is formed primarily of valve plate 40, cylinder block 41, piston 43, brake shoe 45 and swash plate 46.
Valve plate 40 is the on-rotatably moving part being formed with the 1st pump port one a and the 2nd pump port one b in inside.In the present embodiment, valve plate 40 is cylindrical shape, and have can with the slip surface 40a of cylinder block 41 sliding contact.Further, the 1st pump port one a and the 2nd pump port one b forms arc-shaped opening respectively on slip surface 40a.
Cylinder block 41 is the rotary component being formed with multiple piston chamber 42 and multiple piston port 44 in inside.In the present embodiment, cylinder block 41 possesses 9 piston chamber 42-1 ~ 42-9 and 9 piston port 44-1 ~ 44-9, rotates around pump running shaft 1X.
Piston 43 is to the parts that the direction parallel with pump running shaft 1X moves back and forth in the piston chamber 42 of cylinder block 41.Further, piston 43 and cylinder block 41 together rotate around pump running shaft 1X.In the present embodiment, piston 43 is made up of 9 the piston 43-1 ~ 43-9 being contained in 9 piston chamber 42-1 ~ 42-9 respectively.
Brake shoe 45 is the one end that can be connected to piston 43 around 3 axles rotationally, and by can the parts of the mode of circumferentially sliding of the circle centered by pump running shaft 1X on the slip surface 46a of swash plate 46 and the combination of swash plate 46.Further, brake shoe 45 together rotates around pump running shaft 1X with cylinder block 41 and piston 43.In the present embodiment, brake shoe 45 is roughly hemisphere, is made up of 9 the brake shoe 45-1 ~ 45-9 be connected with 9 piston 43-1 ~ 43-9 respectively.
Swash plate 46 is the on-rotatably moving part of the stroke determining piston 43, provides the slip surface 46a that can slide for brake shoe 45.In the present embodiment, swash plate 46 is configured to, the tiltangleθ of the angle formed relative to pump running shaft 1X by slip surface 46a and determine that the tiltangleθ of the stroke of piston 43 is set to fixed value, and oil hydraulic pump 1 becomes fixed capacity type thus.
Shown in Figure 12 9 broken circle represents 9 piston port 44-1 ~ 44-9 current locations separately respectively.Further, Figure 12 represents that 4 piston port 44-4 ~ 44-7 are communicated with the 1st pump port one a fluid, the state that 3 piston port 44-1,44-2 and 44-9 and 2 piston port 44-3 and 44-8 part is separately communicated with the 2nd pump port one b fluid.
As represented with arrow A R10 in Figure 12,9 piston port 44-1 ~ 44-9 are respectively to rotate around pump running shaft 1X along the mode of the 1st pump port one a and the 2nd pump port one b arc-shaped overthe openings separately.In the present embodiment, from be connected with the piston port of the overthe openings by the 1st pump port one a piston chamber spue than the working oil of higher pressure to the 1st pump port one a, introduce the working oil of the comparison low pressure from the 2nd pump port one b in the piston chamber be connected with the piston port of the overthe openings by the 2nd pump port one b.
Further, valve plate 40 has in slip surface 40a upper shed and the aperture 50 be connected with the inwall of the 1st pump port one a.Aperture 50 changes for relaxing the pressure sharply of piston port when fluid is connected to the opening of the 2nd pump port one b (inhalation port) be connected with the open fluid of the 1st pump port one a (spue port).Specifically, as represented with piston port 44-8 in Figure 12, when a part of piston port 44-8 is connected with the 2nd pump port one b fluid, imported the working oil (reference arrow AR1) of the 1st pump port one a to the 2nd pump port one b by aperture 50.Thus, before piston port 44-8 perfect fluid is connected to the 1st pump port one a, increase the pressure of the working oil compared in the 2nd pump port one b of low pressure.
Further, valve plate 40 has in slip surface 40a upper shed and the aperture 51 be connected with the inwall of the 2nd pump port one b.Aperture 51 changes for relaxing the pressure sharply of piston port when fluid is connected to the opening of the 1st pump port one a (spue port) be connected with the open fluid of the 2nd pump port one b (inhalation port).Specifically, when a part for piston port is connected with the 1st pump port one a fluid, imported the working oil of the 1st pump port one a to the piston chamber of correspondence and the 2nd pump port one b by aperture 51.Thus, before this piston port perfect fluid is connected to the 1st pump port one a, increase the pressure of the working oil in the piston chamber and the 2nd pump port one b comparing the correspondence of low pressure.
In addition, although not shown, when oil hydraulic pump 1 rotates in the opposite direction to the side represented with arrow A R10, valve plate 40 possesses other apertures with aperture 50,51 same function.
Utilize these apertures 50,51, oil hydraulic pump 1 prevents the pressure of the working oil in piston port and piston chamber from sharply changing and producing the phenomenons such as pulsation.
At this, refer again to Figure 10, when the rotation of oil hydraulic pump 1 stops, the pressure in pipeline C1, C4, C7, C12 of the 1st pump port one a (spue port) side is in the state higher than the pressure in pipeline C2, C5, C8, C13 of the 2nd pump port one b (inhalation port) side.In addition, this state from Figure 10 with the thick dotted line of black and the pressure state that represents with grey heavy line different.Further, the pressure of the 1st pump port one a side is higher than the setting pressure of relief valve 20L, and therefore relief valve 20L is valve opening state.On the other hand, the pressure of the 2nd pump port one b side is lower than the setting pressure of relief valve 20R, and therefore relief valve 20R becomes valve closing state.
Afterwards, the pressure of the 1st pump port one a side arrives the 2nd pump port one b side by aperture 50 or aperture 51, increases the pressure of oil hydraulic pump 1 and the working oil between relief valve 20R and one-way valve 21R.In addition, the pressure of the 1st pump port one a side moves to the 2nd pump port one b side and reduces along with the working oil of the 1st pump port one a side.
If the pressure increase of oil hydraulic pump 1 and the working oil between relief valve 20R and one-way valve 21R and reach the setting pressure of relief valve 20R, then relief valve 20R becomes valve opening state, and its working oil arrives the second side of relief valve 20R.
If the pressure of the working oil of the 1st pump port one a side reduces and lower than the setting pressure of relief valve 20L, then relief valve 20L becomes valve closing state.Now, the pressure of the working oil of the 2nd pump port one b side is also lower than the setting pressure of relief valve 20R, and therefore relief valve 20R also becomes valve closing state.Its result, as represented with the thick dotted line of black in Figure 10, the pressure of the working oil in pipeline C1, C4, C7 and C12 and oil hydraulic pump 1 become with the pressure of the working oil between relief valve 20R and one-way valve 21R roughly presses identical pressure with the setting of relief valve 20L, 20R.
With this, when the rotation of oil hydraulic pump 1 is in halted state, the pressure during hydraulic pressure closed-loop system 100A makes the 1st pump port one a and the 2nd pump port one b separately becomes roughly presses equal pressure with the setting of relief valve 20L, 20R.This is to increase the degree of compression making oil hydraulic pump 1 start the working oil in two pump ports of the oil hydraulic pump 1 before rotation in advance.Strictly, be the degree of compression in order to increase the working oil in inhalation port in advance, but in fact before oil hydraulic pump 1 starts to rotate and which pump port uncertain can become inhalation port, therefore increase the degree of compression of the working oil in two pump ports in advance.
Its result, the Volume Changes (compression volume) of the working oil in oil hydraulic pump 1 is introduced in the rotation that hydraulic pressure closed-loop system 100A can be reduced by oil hydraulic pump 1, and improves the rising responsiveness that oil hydraulic pump 1 starts flow when rotating and pressure.
At this, with reference to Figure 13, the change of the rise time of the pressure that spues of the oil hydraulic pump 1 that the difference of the setting pressure due to relief valve 20L, 20R causes is described.In addition, the epimere of Figure 13 represents the time history of the pressure that spues of oil hydraulic pump 1, and the hypomere of Figure 13 represents the time history of the rotating speed of oil hydraulic pump 1.
And, the passing represented with solid line in Figure 13 epimere represents and is installed with as passing time P1 (> 0) [MPa] by the setting of relief valve 20L, 20R, and the passing represented with dotted line in Figure 13 epimere represents the passing setting of relief valve 20L, 20R be installed with when being 0 [MPa].
As represented in Figure 13 hypomere, if make oil hydraulic pump 1 start to rotate at moment t0, then the pressure that the spues setting of relief valve 20L, 20R be installed with as the oil hydraulic pump 1 time P1 [MPa] (being such as 2 [MPa]) gets started rising.And, from oil hydraulic pump 1 starts rotation till transit time t1 [ms] (being such as 8 ~ 10 [ms]), the pressure that spues of oil hydraulic pump 1 slowly rises, and after transit time t1 [ms], rises with the constant corresponding to the rotating speed of oil hydraulic pump 1.
On the other hand, although oil hydraulic pump 1 is in rotation status, the setting of relief valve 20L, 20R is installed with the oil hydraulic pump 1 when being 0 [MPa] spue be pressed in transit time t2 (> t1) [ms] till with less than 0 the state of [MPa] pass.In addition, in Figure 13 epimere, for convenience of explanation, the value of negative pressure is expressed as 0 [MPa].And, when starting rotation from oil hydraulic pump 1 when transit time t2 [ms], spuing of oil hydraulic pump 1 presses off rising of beginning, and slowly rises to transit time t3 (> t2) [ms] (being such as 28.5 [ms]).And after transit time t3 [ms], the pressure that spues of oil hydraulic pump 1 rises with the constant corresponding to the rotating speed of oil hydraulic pump 1.In addition, the rotating speed of oil hydraulic pump 1 is from the rotating speed N1 [rpm] starting the moment of transit time t4 (t2 < t4 < t3) [ms] (being such as 25 [ms]) rotation and reach regulation.
So, when the setting of relief valve 20L, 20R being installed with as P1 [MPa], oil hydraulic pump 1 when transit time t1 [ms], starts to suck normally after starting to rotate.Below, the required time till normal for beginning suction is called " spuing the pressure rise time ".In contrast, the setting of relief valve 20L, 20R be installed with when being 0 [MPa], oil hydraulic pump 1 till transit time t2 [ms], is in the suction defective mode with cavitation erosion after starting to rotate, and namely pump spues the state of decrease in efficiency.And oil hydraulic pump 1 can start normal suction in the moment of transit time t3.
By above structure, 2 port ones a, the 1b of the oil hydraulic pump 1 when hydraulic pressure closed-loop system 100A can be stopped the rotation by relief valve 20L, 20R hydraulic control pump 1 separately in pressure.Its result, hydraulic pressure closed-loop system 100A can on the basis of the effect of hydraulic pressure closed-loop system 100, or improves with the effect of hydraulic pressure closed-loop system 100 rising characteristic that oil hydraulic pump 1 starts flow when rotating and pressure independently.
Further, by the setting of relief valve 20L, 20R is installed with into the value P1 [MPa] higher than 0 [MPa], hydraulic pressure closed-loop system 100A can suppress or avoid oil hydraulic pump 1 start when rotating with cavitation erosion suction bad, thus shorten spue pressure the rise time.
Embodiment 3
Then, with reference to Figure 14, the hydraulic pressure closed-loop system 100B involved by the 3rd embodiment of the present invention is described.In addition, Figure 14 is the synoptic diagram of the structure example representing hydraulic pressure closed-loop system 100B.
Hydraulic pressure closed-loop system 100B replaces reciprocable valve 7 and possesses flushing valve 7A, different from hydraulic pressure closed-loop system 100A in this, but identical with hydraulic pressure closed-loop system 100A on other aspects.
Therefore, omit the explanation of identical point and describe difference in detail.In addition, for the constitutive requirements identical with hydraulic pressure closed-loop system 100A, use with in order to the reference symbol that reference symbol that hydraulic pressure closed-loop system 100A uses is identical is described.
Flushing valve 7A possesses: one-way valve 7A1, becomes valve opening state when the pressure of the working oil in pipeline C2 reaches regulation pressure; And one-way valve 7A2, become valve opening state when the pressure of the working oil in pipeline C1 reaches regulation pressure.
One-way valve 7A1 is configured on pipeline C7, becomes valve opening state, make the working oil of service tank T1 by pipeline C11 and pipeline C7 incoming line C1 when the pressure of the working oil in pipeline C2 reaches regulation pressure.In addition, become valve closing state when the pressure of the working oil of one-way valve 7A1 in pipeline C2 is pressed lower than regulation, block the flowing of the working oil between service tank T1 and pipeline C1.And, become valve opening state during the pressure of the pressure that one-way valve 7A1 can be configured to the working oil in pipeline C2 higher than the working oil in pipeline C1, during the pressure of the pressure that also can be configured to the working oil in pipeline C2 lower than the working oil in pipeline C1, also become valve opening state.Further, one-way valve 7A1 can be configured to, and becomes valve opening state during pressure higher than the working oil in pipeline C1 of the pressure of the working oil in pipeline C2, becomes valve closing state during pressure lower than the working oil in pipeline C1 of the pressure of the working oil in pipeline C2.
One-way valve 7A2 is configured on pipeline C8, becomes valve opening state, make the working oil of service tank T1 by pipeline C11 and pipeline C8 incoming line C2 when the pressure of the working oil in pipeline C1 reaches regulation pressure.In addition, become valve closing state when the pressure of the working oil of one-way valve 7A2 in pipeline C1 is pressed lower than regulation, block the flowing of the working oil between service tank T1 and pipeline C2.And, become valve opening state during the pressure of the pressure that one-way valve 7A2 can be configured to the working oil in pipeline C1 higher than the working oil in pipeline C2, during the pressure of the pressure that also can be configured to the working oil in pipeline C1 lower than the working oil in pipeline C2, also become valve opening state.Further, during the pressure of the pressure that one-way valve 7A2 can be configured to the working oil in pipeline C1 higher than the working oil in pipeline C2, become valve opening state, during pressure lower than the working oil in pipeline C2 of the pressure of the working oil in pipeline C1, become valve closing state.
So, when oil hydraulic pump 1 rotates, when the pressure of the working oil in pipeline C1 and pipeline C2 becomes the pressure lower than the working oil in service tank T1, when namely working oil is not enough, flushing valve 7A makes up this deficiency by the working oil of service tank T1.
By above structure, hydraulic pressure closed-loop system 100B in the same manner as hydraulic pressure closed-loop system 100A, 2 port ones a, the 1b of the oil hydraulic pump 1 when can be stopped the rotation by relief valve 20L, 20R hydraulic control pump 1 separately in pressure.Its result, hydraulic pressure closed-loop system 100B, in the same manner as hydraulic pressure closed loop circuit 100A, can improve the rising characteristic that oil hydraulic pump 1 starts flow when rotating and pressure.
And, hydraulic pressure closed-loop system 100B is in the same manner as hydraulic pressure closed-loop system 100A, by the setting of relief valve 20L, 20R being installed with into the value P1 [MPa] higher than 0 [MPa], the suction with cavitation erosion that can suppress or avoid oil hydraulic pump 1 to start when rotating is bad, thus shortens the pressure rise time that spues.
Above, the preferred embodiments of the present invention have been described in detail, but the invention is not restricted to the embodiments described, without departing from the scope of the present invention, can to above-described embodiment various distortion and displacement in addition.
Such as, in above-described embodiment, hydraulic pressure closed-loop system 100,100A, 100B are the structure driving oil hydraulic cylinder 3 with oil hydraulic pump 1, but also can be the structure driving oil hydraulic motor with oil hydraulic pump 1.
And, in above-described embodiment, hydraulic pressure closed-loop system 100,100A, 100B use as by the worktable of the large load capacity type hydraulic drive type Large Plane Grinder of control device in order to mobile, but can use as by the injection cylinder of the injection molding machine of control device or movable pressure plate in order to mobile, also can use as by the component parts of other construction planies of control device in order to mobile.
And, the application advocates the preference of No. 2011-243809, Japanese patent application based on application on November 7th, 2011 and the preference based on No. 2011-243810, Japanese patent application, and is applied in the application by reference to by the full content of these Japanese patent applications.
Symbol description
1-oil hydraulic pump, 1a-the 1st pump port, 1b-the 2nd pump port, 2-electric motor, 3-oil hydraulic cylinder, 3a-piston, 3b-the 1st port, 3c-the 2nd port, 3L-the 1st grease chamber, 3R-the 2nd grease chamber, 4L, 4R-safety valve, 7-reciprocable valve, 7a-first side port, 7b, 7c-secondary port, 9-output detections sensor, 9a-position transducer, 9b-turn-sensitive device, 9c1-the 1st discharge-amount sensor, 9c2-the 2nd discharge-amount sensor, 10-control gear, 11-electric motor control unit, 12-pump efficiency calculating part, 13-pump condition judgement portion, 15-input device, 16-display unit, 17-instantaneous speech power, 100-hydraulic pressure closed-loop system, T1-service tank.

Claims (3)

1. a hydraulic pressure closed-loop system, it can drive the oil hydraulic cylinder or oil hydraulic motor with the 1st port and the 2nd port, it is characterized in that possessing:
Oil hydraulic pump, has the 1st pump port be communicated with described 1st port flow by the 1st pipeline and the 2nd pump port be communicated with described 2nd port flow by the 2nd pipeline;
Electric motor, controls the rotation of described oil hydraulic pump;
Relief valve, is configured at described 1st pipeline and described 2nd pipeline respectively; And
One-way valve, is connected in parallel with described relief valve respectively, and stops working oil from described oil hydraulic pump to described oil hydraulic cylinder or described hydraulic motors.
2. hydraulic pressure closed-loop system according to claim 1, is characterized in that,
Described oil hydraulic pump is axial piston pump.
3. hydraulic pressure closed-loop system according to claim 1, is characterized in that,
Described hydraulic pressure closed-loop system possesses safety valve, and described safety valve is configured at respectively and links the pipeline that described 1st pipeline and working oil are filled with and the pipeline linking described 2nd pipeline and service tank,
The setting pressure of described relief valve is less than the setting pressure of described safety valve.
CN201510671507.4A 2011-11-07 2012-09-14 Closed hydraulic circuit system Pending CN105298782A (en)

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JP2011-243809 2011-11-07
JP2011243809A JP5628134B2 (en) 2011-11-07 2011-11-07 Hydraulic closed circuit system
JP2011-243810 2011-11-07
JP2011243810A JP5859279B2 (en) 2011-11-07 2011-11-07 Hydraulic closed circuit system
CN201280044650.5A CN103827509B (en) 2011-11-07 2012-09-14 Hydraulic pressure closed-loop system

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