CN104067032B - Hydraulic pressure closed loop system - Google Patents
Hydraulic pressure closed loop system Download PDFInfo
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- CN104067032B CN104067032B CN201280067659.8A CN201280067659A CN104067032B CN 104067032 B CN104067032 B CN 104067032B CN 201280067659 A CN201280067659 A CN 201280067659A CN 104067032 B CN104067032 B CN 104067032B
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- pressure
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B7/00—Systems in which the movement produced is definitely related to the output of a volumetric pump; Telemotors
- F15B7/005—With rotary or crank input
- F15B7/006—Rotary pump input
-
- 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
- F15B2211/20538—Type of pump constant capacity
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/205—Systems with pumps
- F15B2211/2053—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
- F15B2211/205—Systems with pumps
- F15B2211/20576—Systems with pumps with multiple pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/27—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
- F15B2211/30—Directional control
- F15B2211/305—Directional control characterised by the type of valves
- F15B2211/3052—Shuttle 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
- F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
- F15B2211/50536—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using unloading valves controlling the supply pressure by diverting fluid to the return line
-
- 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
- F15B2211/60—Circuit components or control therefor
- F15B2211/63—Electronic controllers
- F15B2211/6303—Electronic controllers using input signals
- F15B2211/6336—Electronic controllers using input signals representing a state of the output member, e.g. position, speed or acceleration
-
- 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
-
- 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
- F15B2211/765—Control of position or angle of the output member
- F15B2211/7656—Control of position or angle of the output member with continuous position control
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/38—Control of exclusively fluid gearing
- F16H61/40—Control of exclusively fluid gearing hydrostatic
- F16H61/4078—Fluid exchange between hydrostatic circuits and external sources or consumers
- F16H61/4139—Replenishing or scavenging pumps, e.g. auxiliary charge pumps
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fluid-Pressure Circuits (AREA)
- Control Of Fluid Gearings (AREA)
Abstract
The present invention provides a kind of hydraulic pressure closed loop system.The hydraulic pressure closed loop system (100) of the present invention can drive hydraulic cylinder (3), described hydraulic pressure closed loop system to possess: hydraulic pump (1)；Electro-motor (2), controls the rotation of hydraulic pump (1)；Reversal valve (7), secondary port (7b) connects with the first pipeline (C1), and secondary port (7c) connects with the second pipeline (C2)；Supply pump (5), discharge port connects with the primary side port (7a) of reversal valve (7)；And overflow valve (8), it is set to set pressure by supply pump (5) produced supply pressure.First pipeline (C1) and the second pipeline (C2) are set to supply pressure by reversal valve (7) by supply pump (5).Overflow valve (8) can change setting pressure.
Description
Technical field
The present invention relates to a kind of working oil that can utilize high flow capacity drives the hydraulic pressure of hydraulic cylinder or hydraulic motor to close
Loop systems, particularly relates to a kind of hydraulic pressure closed loop system possessing the powered hydraulic pump by motor.
Background technology
Conventionally, there is known be equipped on fluid motor-driven HST (the Hydro Static of engineering machinery
Transmission) system, this HST system possesses the hydraulic pump directly linked with engine as driving source
(such as, referenced patent document 1).
And, it is known to being equipped on the dipper cylinder driving hydraulic pressure closed loop of hydraulic actuated excavator, this hydraulic pressure closed loop has
The standby hydraulic pump directly linked with engine is as driving source (such as, referenced patent document 2).
Conventional art document
Patent documentation
Patent documentation 1: Japanese Unexamined Patent Publication 2008-32198 publication
Patent documentation 2: Japanese Laid-Open Patent Publication 61-127967 publication
Summary of the invention
The technical task that invention is to be solved
But, HST system or hydraulic pressure closed loop described in patent documentation 1 and patent documentation 2 all will be with engines
The hydraulic pump directly linked is used as driving source, is therefore unsuitable for that requirement hydraulic pump is small and being driven of correct rotation
The micro-locality in dynamic portion controls.
In view of the above problems, it is an object of the invention to provide a kind of working oil of high flow capacity that can pass through to quilt
Drive division is driven, and by the working oil of low discharge, driven part can be carried out micro-locality control
Hydraulic pressure closed loop system.
For solving the means of technical task
To achieve these goals, embodiments of the invention relate to a kind of hydraulic pressure closed loop system, and it can drive
Having the first port and the hydraulic cylinder of the second port or hydraulic motor, wherein, described hydraulic pressure closed loop system has
Standby: hydraulic pump, be there is the first pump port connected with described first port flow by the first pipeline and pass through
The second pump port that second pipeline connects with described second port flow；Electro-motor, controls described hydraulic pump
Rotation；Reversal valve, it has 1 primary side port and 2 secondary port, this secondary port
One connects with described first pipeline fluid, and another of this secondary port connects with described second pipeline fluid
Logical；Supply pump, discharge port connects with the primary side port flow of described reversal valve；And overflow valve, by institute
State supply pump produced supply pressure to be set to set pressure, described supply pump by described reversal valve by described first
Pipeline and described second pipeline are set to described supply pressure.
Invention effect
According to said structure, the present invention can provide a kind of working oil of high flow capacity that can pass through to driven part
It is driven, and by the working oil of low discharge, driven part can be carried out the hydraulic pressure of micro-locality control
Closed loop system.
Accompanying drawing explanation
Fig. 1 is the synoptic diagram of the structure example representing the hydraulic pressure closed loop system involved by embodiments of the invention.
Fig. 2 is the figure representing main line pressure less than the state of hydraulic pressure closed loop system during supply pressure.
The shape of hydraulic pressure closed loop system when Fig. 3 is to represent the working oil driving hydraulic cylinder utilizing hydraulic pump to be spued
The figure of state.
Detailed description of the invention
Hereinafter, with reference to accompanying drawing, embodiments of the invention are illustrated.
Fig. 1 is the summary of the structure example representing the hydraulic pressure closed loop system 100 involved by embodiments of the invention
Figure.
Hydraulic pressure closed loop system 100 is driven liquid by electro-motor 2 by the hydraulic pump 1 of Spin Control for utilizing
The system of cylinder pressure 3.Hydraulic cylinder 3 is such as driving high load capability hydraulic drive type Large Plane Grinder
Workbench.
In the present embodiment, hydraulic pressure closed loop system 100 mainly by hydraulic pump 1, electro-motor 2, hydraulic cylinder 3,
Relief valve 4L, 4R, supply pump 5, electro-motor 6, reversal valve 7, overflow valve 8, sensor 9 and control
Device 10 is constituted.
Hydraulic pump 1 is the device driving hydraulic cylinder 3, for example, fixed capacity type bidirectional hydraulic pump.It addition,
Hydraulic pump 1 is alternatively variable displacement pump.
Electro-motor 2 is the device of the rotation controlling hydraulic pump 1, for example, AC servo motor.
Hydraulic cylinder 3 is to have the first grease chamber 3L and the hydraulic pressure of the second grease chamber 3R being spaced by piston 3a
Actuating device.First grease chamber 3L is by the first pump port of the first port 3b and pipeline C1 with hydraulic pump 1
1a is in fluid communication, and the second grease chamber 3R is by the second pump end of the second port 3c and pipeline C2 with hydraulic pump 1
Mouth 1b fluid communication.In the present embodiment, hydraulic cylinder 3 is possess the both sides extension along piston 3a 2
The double piston-rod cylinder of piston rod, 1 in 2 piston rods ties with surface grinding machine workbench (not shown)
Close.Live it addition, hydraulic cylinder 3 can also be the list possessing unilateral 1 piston rod extended along piston 3a
Stopper rod cylinder, it is also possible to be the direct piston-rodless structure being combined with piston 3a of surface grinding machine workbench.
Relief valve 4L is to service tank T1 when the pressure in pipeline C1 becomes more than authorized pressure
The valve of the working oil in releasing pipeline C1.Further, relief valve 4R is to become for the pressure in pipeline C2
For the valve of the working oil in service tank T1 releasing pipeline C2 time more than authorized pressure.Will below it addition,
Pipeline C1 and pipeline C2 is referred to as " main line ", by the pressure in the pressure in pipeline C1 and pipeline C2
It is referred to as " main line pressure "
Relief valve 4L is configured at the pipe being connected by the pipeline C3 being in fluid communication with service tank T1 and pipeline C1
On the C4 of road, relief valve 4R is configured on the pipeline C5 being connected by pipeline C3 and pipeline C2.
Supply pump 5 is hydraulic pump, and this hydraulic pump discharge working oil is so that pipeline C1 and the respective pressure of pipeline C2
Power becomes more than the supply pressure of regulation, for example, fixed capacity type one-way hydraulic pump.It addition, supply pump 5 is also
It can be variable displacement pump.Further, supply pump 5 often rotates 1 time discharge-amount be less than hydraulic pump 1 often rotate
The discharge-amount of 1 time.The working oil that supply pump 5 is spued is the working oil for auxiliary.
Electro-motor 6 is the device of the rotation controlling supply pump 5, for example, AC servo motor.Electronic horse
Reach 6 persistently to rotate with the rotating speed of regulation, so that supply pump 5 persistently spues working oil with regulation flow velocity.Separately
Outward, electro-motor 6 is in order to change the discharge-amount of supply pump 5, so that the discharge of supply pump 5 presses to regulation
Supply pressure, it is also possible to rotate changing while rotating speed.
Reversal valve 7 be control piper C1 or pipeline C2 and service tank T1 and supply pump 5 each between
The valve of the flowing of working oil, has 1 primary side port 7a and 2 secondary port 7b, 7c.
Primary side port 7a connects via the discharge port flow of pipeline C6 with supply pump 5, secondary port
A port 7b be in fluid communication via pipeline C7 and pipeline C1, another port 7c of secondary port
It is in fluid communication via pipeline C8 and pipeline C2.
Specifically, when the pressure in pipeline C1 is less than the supply pressure of regulation, reversal valve 7 passes through secondary
In the working oil incoming line C1 that supply pump 5 is spued by side ports 7b.Further, when in pipeline C2
When pressure is pressed less than the supply of regulation, reversal valve 7 will supply what pump 5 was spued by secondary port 7c
In working oil incoming line C2.
Overflow valve 8 is valve as described below: when the pressure of primary side port 8a becomes the setting pressure of regulation
Time above, make primary side port 8a and secondary port 8b fluid communication so that primary side port 8a
Working oil flows out to secondary port 8b.
Primary side port 8a is in fluid communication via pipeline C9 and pipeline C6, and secondary port 8b is via pipeline
C10 and service tank T1 is in fluid communication.
In the present embodiment, overflow valve 8 is electromagnetic proportion relief valve, according to from the control controlling device 10 supply
The size of electric current processed changes to set presses.It addition, the supply pressure setting pressure with supplying pump 5 of overflow valve 8 is right
Should.
Sensor 9 is the sensor of the operating state of detection hydraulic cylinder 3, for example, detects the position of piston 3a
The position sensor moved.The value of detection is exported to controlling device 10 by sensor 9.
Controlling device 10 be to be used for controlling the device of hydraulic pressure closed loop system 100, for example, possess CPU,
The computer of RAM, ROM, input/output interface etc..
Further, control device 10 according to the input of user, determine the required movement of surface grinding machine workbench away from
Required displacement from (distance of current location to target location), i.e. piston 3a.Further, control
Device 10 determines the direction of rotation of hydraulic pump 1 according to the required displacement of determined piston 3a and turns
Speed, and the control letter corresponding with the direction of rotation of the hydraulic pump 1 determined and rotating speed to electro-motor 2 output
Number.Specifically, control device 10 and get over the rotating speed of ambassador's hydraulic pump 1 with the required displacement of piston 3a
The biggest mode determines the rotating speed of hydraulic pump 1.Further, device 10 is controlled with along with the required shifting of piston 3a
Dynamic distance diminishes i.e. along with the mode making the rotating speed of hydraulic pump 1 diminish near target location determines hydraulic pump 1
Rotating speed.
Further, control the device 10 output according to sensor 9, monitor the position of piston 3a, i.e. flat stone mill
The position of bed workbench, and judge that surface grinding machine workbench has arrived target location the most.
When being judged to that surface grinding machine workbench arrives target location, control device 10 to electro-motor 2
Output is for making the control signal rotating stopping of hydraulic pump 1.
Then, with reference to Fig. 2, the state of the hydraulic pressure closed loop system 100 when main line pressure is pressed less than supply
Illustrate.It addition, in Fig. 2, heavy line represents the supply pressure state higher than main line pressure.Further,
In order to make accompanying drawing become apparent from Fig. 2, omit sensor 9 and control the diagram of device 10.
In the present embodiment, even if when hydraulic pump 1 and electro-motor 2 stop, electro-motor 6 is also with regulation
Rotating speed persistently rotate, make supply pump 5 with regulation rotating speed persistently rotate.Its result, supply pump 5 is with rule
Fixed flow velocity persistently spues working oil.
The working oil if supply pump 5 persistently spues, causes the pressure in pipeline C6 and pipeline C9 to reach supply
The pressure i.e. setting pressure of overflow valve 8, then overflow valve 8 makes the work in pipeline C6 and pipeline C9 by pipeline C10
Make oil to flow out to service tank T1.Pressure in its result, pipeline C6 and pipeline C9 maintains supply pressure.
Now, if the pressure in pipeline C1 is less than supply pressure, then as shown in arrow AR1, reversal valve 7 leads to
Cross secondary port 7b and pipeline C7 and working oil is supplied to pipeline C1.The flowing of this working oil is at pipeline
Pressure in C1 reaches to disappear during supply pressure.
Equally, if the pressure in pipeline C2 is less than supply pressure, then as shown in arrow AR2, reversal valve 7 leads to
Cross secondary port 7c and pipeline C8 and working oil is supplied to pipeline C2.The flowing of this working oil is at pipeline
Pressure in C2 reaches to disappear during supply pressure.
So, in hydraulic pressure closed loop system 100, the pressure in pipeline C1 and pipeline C2 becomes supply pressure all the time
Above.This means to increase in advance hydraulic pump 1 start main line pressure before rotating (following, be set to
" initially pressure "), and increase the degree of compression of working oil in main line in advance.
Its result, the main line that hydraulic pressure closed loop system 100 can be caused by the rotation of hydraulic pump 1 by reduction
The change in volume (compression volume) of interior working oil improves hydraulic control rigidity, gets rid of response lag, and
And the control resolution of working oil discharge volume based on the pump anglec of rotation can be improved.Such as high load capability
Hydraulic drive type Large Plane Grinder is such, and the capacity of the working oil in hydraulic cylinder 3 and main line is the biggest, and
The compression volume reaching work load pressure is the biggest, and its effect is the most notable.By this effect, hydraulic pressure closed loop system
100 drivings that can be carried out piston 3a (surface grinding machine workbench) by the working oil of high flow capacity, and energy
The micro-locality enough carrying out piston 3a (surface grinding machine workbench) controls.
Can also be according to weight (such as, the surface grinding machine workbench of driven object it addition, control device 10
And the gross weight of machined object placed on it.) change supply pressure.
Specifically, the driven object that control device 10 is detected according to weight sensor (not shown)
Weight, changes the size that overflow valve 8 output controls electric current, and changes the setting pressure of overflow valve 8, i.e.
Supply pressure.
More specifically, the weight of driven object is the biggest, and the setting pressure of overflow valve 8 i.e. supplies buckling and must get over
Greatly.This is for the degree of compression by increasing the working oil in main line, eliminates the weight because of driven object
The biggest and become the change in volume of the working oil in main line the biggest, that caused by the rotation of hydraulic pump 1
The impact of (compression volume).
Thus, hydraulic pressure closed loop system 100 can make the micro-locality control of piston 3a (surface grinding machine workbench)
The lifting stability of characteristics of system, and unrelated with varying in weight of driven object.
Further, when hydraulic pressure closed loop system 100 is holding state, controls device 10 and can also reduce overflow valve 8
Setting pressure, make supply pump 5 no-load operation.
Specifically, control device 10 and judge hydraulic pressure closed loop system 100 whether according to the input of operator
For holding state, when being judged to holding state, change the size that overflow valve 8 output is controlled electric current,
It is low that the setting pressure making overflow valve 8 i.e. supplies pressure drop.
Thus, hydraulic pressure closed loop system 100 is prevented from energy when hydraulic pressure closed loop system 100 is for holding state
Waste.
When then, hydraulic cylinder 3 being driven with reference to the Fig. 3 working oil to utilizing hydraulic pump 1 to be spued
The state of hydraulic pressure closed loop system 100 illustrates.It addition, in Fig. 3, thick dashed line represents that hydraulic pump 1 is from
One pump port 1a is in result pipeline C1, C4, C7 of the first grease chamber 3L discharge working oil of hydraulic cylinder 3
Pressure rise state.Further, heavy line represents the supply pressure state higher than the pressure in pipeline C2.
Further, in Fig. 3, in order to make accompanying drawing clearer, omit sensor 9 and control the diagram of device 10.
As it is shown on figure 3, in hydraulic pressure closed loop system 100, according to the input of operator, by electronic horse
Reaching 2 makes hydraulic pump 1 rotate, and drives hydraulic cylinder 3, so that piston 3a (surface grinding machine workbench) is to arrow
Head direction shown in AR3 is moved.
Now, working oil is supplied to pipeline C1 and the first grease chamber 3L, pipeline C1 and first by hydraulic pump 1
The degree of compression of the working oil in grease chamber 3L increases.Work in its result, pipeline C1 and the first grease chamber 3L
The pressure of oil increases.
On the other hand, by hydraulic pump 1 from pipeline C2 and the second grease chamber 3R sucking-off working oil, pipeline C2
And the degree of compression of the working oil that second in grease chamber 3R reduces.In its result, pipeline C2 and the second grease chamber 3R
Working oil pressure reduce.
If the pressure of the working oil in pipeline C2 and the second grease chamber 3R reduces and presses less than supply, then such as arrow
Shown in AR4, reversal valve 7 supplies working oil by secondary port 7c and pipeline C8 to pipeline C2.This
Time, as shown in arrow AR41, supply pump 5 supplies working oil by pipeline C6 to reversal valve 7.This work
The flowing of oil pressure in pipeline C2 and the second grease chamber 3R reaches to disappear during supply pressure.
It is alternatively it addition, rotate above supply pressure during hydraulic pump 1 with the rotating speed of regulation and drives hydraulic pump 1
Different values is pressed in supply before, such as, be alternatively the value pressed less than the supply before driving hydraulic pump 1.This
The application target being because supply pressure is different.Specifically, this is because drive the supply before hydraulic pump 1
Pressure, for improving hydraulic control rigidity and realizing the stabilisation of the volume elasticity of working oil, makes hydraulic pump 1 on the contrary
Supply pressure during rotation is used for replenishing working oil not enough in main line and preventing the generation of air pocket etc..And
And, by supply pressure when making hydraulic pump 1 rotate is set to lower value, it is possible to reduce and make supply pump 5 revolve
The load of the electro-motor 6 turned.It addition, now, device 10 is controlled such as according to the rotating speed of hydraulic pump 1
Change the size that overflow valve 8 output is controlled electric current.Specifically, control device 10 and make overflow valve 8
Set pressure i.e. supply pressure along with hydraulic pump 1 rotating speed increase and reduce.
So, little by the rotation of hydraulic pump 1 when the pressure of a pipeline in pipeline C1 and pipeline C2
When supply pressure, hydraulic pressure closed loop system 100 supplements working oil by reversal valve 7.That is, as pipeline C1 and
When the volume of the working oil of a pipeline in pipeline C2 reduces, hydraulic pressure closed loop system 100 is in order to supplement it
Volume change (compression volume) supplies working oil by reversal valve 7.
By above structure, hydraulic pressure closed loop system 100 can realize piston 3a by the working oil of high flow capacity
The position control of (surface grinding machine), and piston 3a (flat stone mill can be realized by the working oil of low discharge
Bed) micro-locality control.
Above, the preferred embodiments of the present invention are described in detail, but the present invention has been not restricted to above-mentioned
Embodiment, without departing from the scope of the present invention, it is possible to above-described embodiment various deformation and displacement in addition.
Such as, in above-described embodiment, hydraulic pressure closed loop system 100 is for utilize hydraulic pump 1 to drive hydraulic cylinder 3
Structure, but alternatively utilize hydraulic pump 1 to drive the structure of hydraulic motor.
Further, in above-described embodiment, hydraulic pressure closed loop system 100 is used for moving high load capability hydraulic drive type
The workbench of Large Plane Grinder, but can also be used for injection cylinder or the moving die plate of mobile injection moulding machine, also
Can be used for moving the component parts of other lathes.
Further, the application advocates based on Japanese patent application 2012-23491 filed in 6 days February in 2012
Number priority, the full content of this Japanese publication is by with reference to being applied in the application.
Symbol description
1-hydraulic pump, 1a-the first pump port, 1b-the second pump port, 2-electro-motor, 3-hydraulic cylinder,
3a-piston, 3b-the first port, 3c-the second port, 3L-the first grease chamber, 3R-the second grease chamber, 4L, 4R-
Relief valve, 5-supplies pump, 6-electro-motor, 7-reversal valve, 7a-primary side port, 7b, 7c-secondary side
Port, 8-overflow valve, 8a-primary side port, 8b-secondary port, 9-sensor, 10-controls dress
Put, 100-hydraulic pressure closed loop system, T1-tank, C1～C10-pipeline.
Claims (2)
1. a hydraulic pressure closed loop system, its can drive have the first port and the hydraulic cylinder of the second port or
Hydraulic motor, it is characterised in that described hydraulic pressure closed loop system possesses:
Hydraulic pump, is had the first pump port connected with described first port flow by the first pipeline and passes through
The second pump port that second pipeline connects with described second port flow；
First electro-motor, controls the rotation of described hydraulic pump；
Reversal valve, it has 1 primary side port and 2 secondary port, of this secondary port
Connecting with described first pipeline fluid, another of this secondary port connects with described second pipeline fluid；
Supply pump, discharge port connects with the primary side port flow of described reversal valve, and by the second electronic horse
Reach driving；
Overflow valve, is set to set pressure by supplying pressure produced by described supply pump, and can change this setting
Pressure；And
Control device, change the setting pressure of described overflow valve,
Described supply pump is before driving described hydraulic pump, by described reversal valve by described first pipeline and institute
State the second pipeline and be set to described supply pressure,
Described control device reduces described setting and presses, so that more than the rotary speed that described hydraulic pump is with regulation
Described supply when rotary speed rotates is forced down in driving the supply pressure before described hydraulic pump.
2. a hydraulic pressure closed loop system, it can drive has the first port and the hydraulic cylinder of the second port or liquid
Pressure motor, it is characterised in that described hydraulic pressure closed loop system possesses:
Hydraulic pump, is had the first pump port connected with described first port flow by the first pipeline and passes through
The second pump port that second pipeline connects with described second port flow；
First electro-motor, controls the rotation of described hydraulic pump；
Reversal valve, it has 1 primary side port and 2 secondary port, of this secondary port
Connecting with described first pipeline fluid, another of this secondary port connects with described second pipeline fluid；
Supply pump, discharge port connects with the primary side port flow of described reversal valve, and by the second electronic horse
Reach driving；
Overflow valve, is set to set pressure by supplying pressure produced by described supply pump, and can change this setting
Pressure；And
Control device, change the setting pressure of described overflow valve,
Described supply pump is before driving described hydraulic pump, by described reversal valve by described first pipeline and institute
State the second pipeline and be set to described supply pressure,
Described control device is that the weight by described hydraulic cylinder or the driven object of described fluid motor-driven is the biggest
More increase the described control device setting pressure.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2012023491A JP6009770B2 (en) | 2012-02-06 | 2012-02-06 | Hydraulic closed circuit system |
| JP2012-023491 | 2012-02-06 | ||
| PCT/JP2012/078541 WO2013118356A1 (en) | 2012-02-06 | 2012-11-02 | Hydraulic closed circuit system |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN104067032A CN104067032A (en) | 2014-09-24 |
| CN104067032B true CN104067032B (en) | 2016-10-12 |
Family
ID=48947143
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201280067659.8A Expired - Fee Related CN104067032B (en) | 2012-02-06 | 2012-11-02 | Hydraulic pressure closed loop system |
Country Status (4)
| Country | Link |
|---|---|
| JP (1) | JP6009770B2 (en) |
| KR (1) | KR20140108278A (en) |
| CN (1) | CN104067032B (en) |
| WO (1) | WO2013118356A1 (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP6896484B2 (en) * | 2017-03-31 | 2021-06-30 | 住友重機械工業株式会社 | Position control device, hydraulic drive device |
| CN107965572B (en) * | 2017-11-06 | 2020-06-26 | 北京理工大学 | An electro-hydraulic control system for automatic transmission |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN87102639A (en) * | 1986-06-11 | 1987-12-23 | 株式会社岛津制作所 | Hydraulic system |
| CN1237233A (en) * | 1996-09-13 | 1999-12-01 | 维克斯公司 | Electrohydraulic system and apparatus with bidirectional electric-motor hydraulic-pump unit |
| US6360537B1 (en) * | 1999-07-23 | 2002-03-26 | Sauer-Danfoss Inc. | System for controlling a hydraulic vehicle drive |
| CN1502834A (en) * | 2002-11-26 | 2004-06-09 | 伊顿公司 | Hydraulically actuated by-pass valve |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3744244A (en) * | 1971-07-30 | 1973-07-10 | Automation Equipment Inc | Hydrostatic drive |
| FR2301741A1 (en) * | 1975-02-20 | 1976-09-17 | Renault | DI |
| US3999387A (en) * | 1975-09-25 | 1976-12-28 | Knopf Frank A | Closed loop control system for hydrostatic transmission |
| US3972189A (en) * | 1975-11-17 | 1976-08-03 | Eaton Corporation | Control for hydrostatic transmissions |
| JPS5618155A (en) * | 1979-07-19 | 1981-02-20 | Yanmar Agricult Equip Co Ltd | Self-traveling tractor |
| JPS6418665U (en) * | 1987-07-24 | 1989-01-30 | ||
| JPS6435169A (en) * | 1987-07-31 | 1989-02-06 | Honda Motor Co Ltd | Hydraulic control device for vehicle continuously variable transmission |
| EP0395657B1 (en) * | 1987-10-13 | 1991-08-14 | ZF FRIEDRICHSHAFEN Aktiengesellschaft | Hydrostatic-mechanical drive system |
| JPH03229065A (en) * | 1990-01-31 | 1991-10-11 | Shimadzu Corp | Hydraulic machine type transmission |
| US7430860B2 (en) * | 2004-09-28 | 2008-10-07 | Parker-Hannifin Corporation | Hydrostatic transmission circuit |
| JP4742732B2 (en) * | 2005-08-04 | 2011-08-10 | トヨタ自動車株式会社 | Vehicle transmission |
| JP5368943B2 (en) * | 2009-11-10 | 2013-12-18 | 川崎重工業株式会社 | Hydraulic control device |
| JP5343037B2 (en) * | 2010-05-17 | 2013-11-13 | 株式会社 神崎高級工機製作所 | Swash plate type hydraulic machine and hydrostatic transmission |
-
2012
- 2012-02-06 JP JP2012023491A patent/JP6009770B2/en not_active Expired - Fee Related
- 2012-11-02 WO PCT/JP2012/078541 patent/WO2013118356A1/en active Application Filing
- 2012-11-02 KR KR1020147019533A patent/KR20140108278A/en not_active Ceased
- 2012-11-02 CN CN201280067659.8A patent/CN104067032B/en not_active Expired - Fee Related
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN87102639A (en) * | 1986-06-11 | 1987-12-23 | 株式会社岛津制作所 | Hydraulic system |
| CN1237233A (en) * | 1996-09-13 | 1999-12-01 | 维克斯公司 | Electrohydraulic system and apparatus with bidirectional electric-motor hydraulic-pump unit |
| US6360537B1 (en) * | 1999-07-23 | 2002-03-26 | Sauer-Danfoss Inc. | System for controlling a hydraulic vehicle drive |
| CN1502834A (en) * | 2002-11-26 | 2004-06-09 | 伊顿公司 | Hydraulically actuated by-pass valve |
Also Published As
| Publication number | Publication date |
|---|---|
| JP6009770B2 (en) | 2016-10-19 |
| WO2013118356A1 (en) | 2013-08-15 |
| CN104067032A (en) | 2014-09-24 |
| KR20140108278A (en) | 2014-09-05 |
| JP2013160318A (en) | 2013-08-19 |
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