CN106438584B - A kind of variable pressure and flow type hydraulic servomechanism and method of work based on electric machine speed regulation - Google Patents
A kind of variable pressure and flow type hydraulic servomechanism and method of work based on electric machine speed regulation Download PDFInfo
- Publication number
- CN106438584B CN106438584B CN201610849277.0A CN201610849277A CN106438584B CN 106438584 B CN106438584 B CN 106438584B CN 201610849277 A CN201610849277 A CN 201610849277A CN 106438584 B CN106438584 B CN 106438584B
- Authority
- CN
- China
- Prior art keywords
- piston rod
- controller
- servo valve
- cylinder piston
- control
- 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.)
- Active
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
- F15B21/02—Servomotor systems with programme control derived from a store or timing device; Control devices therefor
-
- 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
- F15B2211/25—Pressure control functions
Abstract
The present invention relates to a kind of variable pressure and flow type hydraulic servomechanism and method of work based on electric machine speed regulation, the servo control mechanism includes controller, oily filter, position sensor, brushless direct current motor, constant displacement pump, charged piston, servo valve and oil cylinder；The controller receives position signal, controls servo valve start, while controls motor to drive constant displacement pump control cylinder piston motion.Servo control mechanism of the present invention and method of work, the external force according to suffered by oil cylinder, dynamic adjusting system pressure, when the servo control mechanism is worked, for a long time in operating on low voltage state, advantageously reduces leakage.Relatively low system pressure can directly reduce the power consumption of servo control mechanism.Formed using less expensive electronic component, the realization of the controller of embedded software, cost can be reduced.
Description
Technical field
The present invention relates to hydraulic servomechanism, more particularly to a kind of variable pressure and flow type hydraulic servo-machine based on electric machine speed regulation
Structure and method of work.
Background technology
Hydraulic servomechanism belongs to one kind of Positioning Servo System, is widely used in mechanical industry, aerospace etc.
, it is necessary to the wider occasion of high-power, big power output, big output torque, speed adjustable range in field.With power is big, electrodeless variable-speed,
Respond the advantages that fast.
It is several big that general hydraulic servomechanism includes hydraulic energy source, start (hydraulic cylinder or hydraulic motor), position detection etc.
Part, there is the problems such as complicated, volume is big, efficiency is low, easy leakage, stringent to requirements such as volume weight, efficiency
The application of occasion is extremely restricted.
Current hydraulic servomechanism is general to use except indivedual mechanisms for only needing simple start are using pump control cylinder scheme
Valve-controlled cylinder, to obtain more preferable controllability, its hydraulic energy source generally uses constant pressure variable displacement pump or constant displacement pump, constant pressure variable displacement pump
The shortcomings that be that of high cost, volume is larger, the service life is shorter, the shortcomings that constant displacement pump, is that pressure cannot be adjusted, and can only use overflow
The additional valve member such as valve, pressure regulator valve is realized, causes efficiency low；Simultaneously as system pressure is higher, hydraulic pressure oil seepage is be easy to cause,
Cause the pollution to environment, these shortcomings limit conventional hydraulic servomechanism stringent to space weight, efficiency requirements
The application of occasion.
Therefore there is an urgent need to effectively reduce the system energy consumption and overall volume, the method for weight of hydraulic servomechanism.
The content of the invention
In view of above-mentioned analysis, the present invention is intended to provide a kind of variable pressure and flow type hydraulic servomechanism based on electric machine speed regulation
And method of work, to solve problems of the prior art.
The purpose of the present invention is mainly achieved through the following technical solutions：
One side based on the embodiment of the present invention, an embodiment of the present invention provides a kind of change buckling based on electric machine speed regulation
Amount type hydraulic servomechanism, including controller, oily filter, position sensor, brushless direct current motor, constant displacement pump, charged piston, watch
Take valve and oil cylinder；
Wherein, controller is connected with position sensor and servo valve respectively, and position sensor is connected with cylinder piston rod, control
Motor-drive circuit is connected with brushless direct current motor in device processed, and motor is mechanically connected with constant displacement pump, and oily filter is installed on constant displacement pump
Delivery outlet, charged piston are connected with low pressure oil way, servo valve and oil cylinder composition valve-controlled cylinder system.
In based on an alternative embodiment of the invention, in valve-controlled cylinder system, delivery outlet of the pressure oil through the servo valve
Into oil cylinder, cylinder piston rod is promoted to make straight-line displacement.
In based on an alternative embodiment of the invention, position sensor is connected with the cylinder piston rod, obtains oil cylinder
The position signal of piston rod, is transferred to the controller.
In based on an alternative embodiment of the invention, overflow valve is further included, the overflow valve is used to work as system pressure liter
Excess traffic is back to low pressure oil way when up to exceeding design load, specifically include end cap, O-ring, valve body, cone valve, spring, spiral shell
It is stifled.
Other side based on the embodiment of the present invention, an embodiment of the present invention provides a kind of variable pressure and flow of electric machine speed regulation
The method of work of type hydraulic servomechanism, comprises the following steps：
S1, carry out system initialization to servo control mechanism；
The oil cylinder that the target location command signal and position sensor that S2, controller provide the external world received obtain is lived
The difference of the current position signal of stopper rod is converted to servo valve control electric current, control servo valve work；Controller is according to by mistake at the same time
Difference signal, controls motor speed, further the quantitative pump output flow change of control, so as to adjust system pressure；Drive cylinder is lived
Stopper rod；
S3, input new target position signal to controller, and the controller is according to new target position signal and position
The difference of the position signal of sensor cylinder piston rod, controls servo valve and motor drive cylinder piston rod again；
S4, circulation perform above-mentioned steps S2 to S3, move back and forth cylinder piston rod.
In based on an alternative embodiment of the invention, step S2 further comprises：
S21, controller drive oil according to the position of cylinder piston rod and the difference control servo valve and motor of target location
Cylinder piston rod accelerates target location described in movement velocity fast approaching；
S22, controller further control servo valve and motor according to the position of cylinder piston rod and the difference of target location
Drive cylinder piston rod slows down until stablizing in the target location.
In based on an alternative embodiment of the invention, step S3 further comprises：
S31, controller drive according to the position of cylinder piston rod and the difference control servo valve and motor of new target location
Dynamic cylinder piston rod accelerates target location new described in movement velocity fast approaching；
S32, controller according to the difference of the position of cylinder piston rod and new target location further control servo valve with
Motor drive cylinder piston rod slows down until stablizing in the new target location.
In based on an alternative embodiment of the invention, step S21 further comprises：
S211, the servo valve control current control servo valve start of controller output, output flow increase, high pressure oil
Oil cylinder is flowed into from the delivery outlet of servo valve, promotes cylinder piston rod movement；
According to embedded control strategy, driving motor improves rotating speed for S212, the controller, and quantitative pump output flow adds
Greatly, system pressure is improved, makes the cylinder piston rod position fast approaching target location.
In based on an alternative embodiment of the invention, step S22 further comprises：
S221, the servo valve control servo valve start of controller output, output flow diminish, until be zero, oil cylinder
Output speed reduce, until stablize in target location；
The control strategy control motor that S222, the controller embed reduces rotating speed, and quantitative pump output flow declines, system
Pressure declines therewith, until cylinder piston rod can be maintained static；
The control strategy control motor speed that S223, the controller embed maintains certain numerical value, exports constant displacement pump
Flow is equal to leakage current amount in servo valve.
In based on an alternative embodiment of the invention, further include：
When the controller drives the motor to be rotated with maximum speed, the quantitative pump output flow reaches maximum
It is worth, the excess traffic outside oil cylinder start needs, makes system pressure rise to over design load, and overflow valve is opened, excess traffic
Low pressure oil way is back to by overflow valve, system pressure falls after rise, maintains design load.
The present invention has the beneficial effect that：
1. reduce leakage:The external force according to suffered by oil cylinder, dynamic adjusting system pressure, when the servo control mechanism is worked, for a long time
In operating on low voltage state, leakage is advantageously reduced.
2. reduce power consumption:Relatively low system pressure can directly reduce the power consumption of servo control mechanism.
3. reduce cost:The function of needing the hydraulic component of costliness to realize in conventional servo mechanism, using less expensive
Electronic component composition, the controller of embedded software are realized, can reduce cost.
Other features and advantages of the present invention will illustrate in the following description, also, partial become from specification
Obtain it is clear that or being understood by implementing the present invention.The purpose of the present invention and other advantages can be by the explanations write
Specifically noted structure is realized and obtained in book, claims and attached drawing.
Brief description of the drawings
Attached drawing is only used for showing the purpose of specific embodiment, and is not considered as limitation of the present invention, in whole attached drawing
In, identical reference symbol represents identical component.Fig. 1 is a kind of variable pressure and flow type hydraulic servomechanism servo of electric machine speed regulation
The structure diagram of mechanism；
Fig. 2 is overflow valve composition schematic diagram；
Fig. 3 is a kind of flow chart of work methods of the variable pressure and flow type hydraulic servomechanism servo control mechanism of electric machine speed regulation.
Reference numeral：
101- controllers, 102- oily filters, 103- position sensors, 104- brushless direct current motors, 105- constant displacement pumps, 106-
Overflow valve, 107- charged pistons, 108- servo valves, 109- oil cylinders；
201- end caps, 202-O types circle, 203- spools, 204-O types circle, 205- valve bodies, 206- cone valves, 207- springs, 208-
Screw plug.
Embodiment
The preferred embodiment of the present invention is specifically described below in conjunction with the accompanying drawings, wherein, attached drawing forms the application part, and
It is used to explain the principle of the present invention together with embodiments of the present invention.
A specific embodiment according to the present invention, discloses a kind of variable pressure and flow type hydraulic servo based on electric machine speed regulation
Mechanism, including controller, oily filter, position sensor, brushless direct current motor, constant displacement pump, overflow valve, charged piston, servo valve
And oil cylinder；
Wherein, controller is connected with position sensor and servo valve respectively, and position sensor is connected with cylinder piston rod, control
Motor-drive circuit is connected with brushless direct current motor in device processed, and motor is mechanically connected with constant displacement pump, and oily filter is installed on constant displacement pump
Delivery outlet, overflow valve are connected installed in oil duct close to constant displacement pump delivery outlet position, charged piston with low pressure oil way, servo valve and oil
Cylinder constitutes a valve-controlled cylinder system, and in valve-controlled cylinder system, pressure oil enters the oil cylinder through servo valve valve pocket opening, oil
Pressure promotes the oil cylinder piston to make straight-line displacement.
Specifically, wherein servo valve is 3-position 4-way type servo valve, and oil cylinder is bi-directional symmetrical oil cylinder, and A, B of servo valve are defeated
Outlet is connected with oil cylinder both ends respectively.
Overflow valve, as shown in Fig. 2, including end cap, O-ring, valve body, cone valve, spring, screw plug, by rotating screw plug, is adjusted
The decrement of spring, sets preset aerial drainage pressure.The design maximum vent flow of overflow valve is slightly below constant displacement pump maximum output stream
Amount.When system pressure is excessive, overflow valve is opened, and high pressure oil is leaked to low pressure oil way；Otherwise shut-off.Specifically, when A cavity pressures are big
When rating system pressure Ps, overflow valve is opened, and hydraulic oil leaks to B chambers, and after system pressure is decreased below Ps, overflow valve closes
It is disconnected.
Constant displacement pump allowable stress is more than 1.5 times of design rating system pressure, it is ensured that raise suddenly in system pressure and
When overflow valve is not yet turned on, the structure of constant displacement pump breakage will not occur because of impact.
Wherein, oily filter is installed on constant displacement pump delivery outlet, for avoiding fifth wheel from entering high-pressure oil passage；
Wherein, charged piston is connected with low pressure oil way, by spring pre-pressing force, low pressure oil way is produced certain pressure
Power, meets constant displacement pump oil suction requirement；
The rated operating pressure Ps of servo valveNEqual to rating system pressure.Meanwhile must to obtain servo valve reliable for this programme
Operating pressure Ps1Parameter, as system minimum pressure design load.
Servo valve constitutes a valve-controlled cylinder system with oil cylinder, and specifically, wherein servo valve is 3-position 4-way type servo valve,
Oil cylinder is bi-directional symmetrical oil cylinder, and A, B delivery outlet of servo valve are connected with oil cylinder both ends respectively, and servo control mechanism feeds back for position closed loop
System, work step are as follows：
S1, carry out system initialization to servo control mechanism.
The oil cylinder that the target location command signal and position sensor that S2, controller provide the external world received obtain is lived
The difference of the current position signal of stopper rod is converted to servo valve control electric current, control servo valve work；Controller is according to by mistake at the same time
Difference signal, controls motor speed, further the quantitative pump output flow change of control, so as to adjust system pressure；Drive cylinder is lived
Stopper rod.
Further, the oil that the target location command signal and position sensor that controller provides the external world received obtain
The difference of the current position signal of cylinder piston rod is first amplified before conversion.
Specifically, using classical PID algorithm, calculate motor control pwm signal duty cycle, motor-drive circuit according to
Pwm signal duty cycle driving motor is rotated to be rotated by certain rotating speed；Motor speed changes the quantitative pump output flow change of control,
So as to adjust system pressure；Specifically, the change of motor speed, makes quantitative pump output flow change, so that system pressure liter
High or reduction, hydraulic energy source is provided for valve-controlled cylinder.
S21, controller drive according to the position of cylinder piston rod and the difference control servo valve of target location with control motor
Dynamic cylinder piston rod accelerates movement velocity fast approaching target location.
Start using servo valve as main control cylinder, when error is larger between target position signal and current position signal,
Generally when allowing more than twice of site error more than system, it is meant that resistance suffered by oil cylinder is larger or outgoing position is away from target position
Put farther out, the control strategy computing that controller embeds exports big control parameter, and controller driving motor improves rotating speed, constant displacement pump
Output flow increases, and improves system pressure and accelerates cylinder movement speed at the same time to improve oil cylinder power output.
When controller driving motor is rotated with maximum speed, quantitative pump output flow reaches maximum, is carried for valve-controlled cylinder
For the high-pressure and hydraulic energy, oil cylinder start need outside excess traffic, system pressure can be made to rise to over design load, overflow valve
Open, excess traffic is back to low pressure oil way by overflow valve, and system pressure falls after rise, maintains design load, controller output
Servo valve control current control servo valve start, output flow is maximum, under servo valve control current control, servo valve work,
High pressure oil flows into oil cylinder from the delivery outlet of servo valve, promotes piston rod movement in oil cylinder；Make the outgoing position fast approaching of oil cylinder
Target location；With the movement of piston rod, the output signal intensity of position sensor, control is transmitted to as current position signal
Device；Meanwhile piston rod is also the start part of servo control mechanism, outside power output.
S22, controller further control servo valve and control according to the position of cylinder piston rod and the difference of target location
Motor drive cylinder piston rod slows down until stablizing in target location.
When current position signal is close to target location, error diminishes between two kinds of signals, the servo valve control of controller output
Electric current processed diminishes, until being zero, servo valve output flow diminishes, until being zero, the output speed of oil cylinder reduces, until stablizing
Target location, in the process, the rotating speed also controlled reduction therewith of motor, quantitative pump output flow decline, and system pressure is therewith
Decline, until oil cylinder can be maintained static；Hereafter, motor speed maintains certain numerical value, is equal to quantitative pump output flow and watches
Leakage current amount in valve is taken, system pressure maintains at this time, and oil cylinder power output is equal to outer load, and mechanism can maintain stable state.
For example, target location, at the top of oil cylinder, cylinder piston rod current location is needed in oil cylinder bottom, then cylinder piston rod
It is moved at the top of oil cylinder.
S3, input new target position signal to controller, and controller is according to target location command signal and position sensing
The difference of the position signal of device cylinder piston rod, controls servo valve, control motor drive cylinder piston rod again；
S31, controller drive according to the position of cylinder piston rod and the difference control servo valve of target location with control motor
Dynamic cylinder piston rod accelerates the new target location of movement velocity fast approaching.
Start using servo valve as main control cylinder, when error is larger between target position signal and current position signal,
Generally when allowing more than twice of site error more than system, it is meant that resistance suffered by oil cylinder is larger or outgoing position is away from target position
Put farther out, the control strategy computing that controller embeds exports big control parameter, and controller driving motor improves rotating speed, constant displacement pump
Output flow increases, and improves system pressure and accelerates cylinder movement speed at the same time to improve oil cylinder power output.
When controller driving motor is rotated with maximum speed, quantitative pump output flow reaches maximum, is carried for valve-controlled cylinder
For the high-pressure and hydraulic energy, oil cylinder start need outside excess traffic, system pressure can be made to rise to over design load, overflow valve
Open, excess traffic is back to low pressure oil way by overflow valve, and system pressure falls after rise, maintains design load, controller output
Servo valve control current control servo valve start, output flow is maximum, under servo valve control current control, servo valve work,
High pressure oil flows into oil cylinder from the delivery outlet of servo valve, promotes piston rod movement in oil cylinder；Make the outgoing position fast approaching of oil cylinder
New target location；With the movement of piston rod, the output signal intensity of position sensor, is transmitted to as current position signal
Controller；Meanwhile piston rod is also the start part of servo control mechanism, outside power output.
S32, controller further control servo valve and control according to the position of cylinder piston rod and the difference of target location
Motor drive cylinder piston rod slows down until stablizing in new target location.
When current position signal is close to new target location, error diminishes between two kinds of signals, the servo of controller output
Valve control electric current diminishes, until being zero, servo valve output flow diminishes, until being zero, the output speed of oil cylinder reduces, until steady
New target location is scheduled on, in the process, the rotating speed also controlled reduction therewith of motor, quantitative pump output flow declines, system
Pressure declines therewith, until oil cylinder can be maintained static；Hereafter, motor speed maintains certain numerical value, makes constant displacement pump output stream
Amount is equal to leakage current amount in servo valve, and system pressure maintains at this time, and oil cylinder power output is equal to outer load, and mechanism can maintain to stablize shape
State.
For example, cylinder piston rod current location is at the top of oil cylinder, new target location is in oil cylinder bottom, then cylinder piston rod
Need to be moved to oil cylinder bottom.
S4, circulation perform above-mentioned steps S2 to S3, move back and forth oil cylinder hydraulic bar.
Beneficial effect：
1) leakage is reduced:The external force according to suffered by oil cylinder, dynamic adjusting system pressure, when the servo control mechanism is worked, for a long time
In operating on low voltage state, leakage is advantageously reduced.
2) power consumption is reduced:Relatively low system pressure can directly reduce the power consumption of servo control mechanism.
3) cost is reduced:The function of needing the hydraulic component of costliness to realize in conventional servo mechanism, using less expensive
Electronic component composition, the controller of embedded software are realized, can reduce cost
In conclusion an embodiment of the present invention provides a kind of variable pressure and flow type hydraulic servomechanism based on electric machine speed regulation.
The foregoing is only a preferred embodiment of the present invention, but protection scope of the present invention be not limited thereto,
Any one skilled in the art the invention discloses technical scope in, the change or replacement that can readily occur in,
It should be covered by the protection scope of the present invention.
Claims (9)
1. a kind of variable pressure and flow type hydraulic servomechanism based on electric machine speed regulation, including controller, oily filter, position sensor, nothing
Brush dc motor, constant displacement pump, charged piston, servo valve and oil cylinder；
Wherein, controller is connected with position sensor and servo valve respectively, and position sensor is connected with cylinder piston rod, controller
Middle motor-drive circuit is connected with brushless direct current motor, and motor is mechanically connected with constant displacement pump, and oily filter is exported installed in constant displacement pump
Mouthful, charged piston is connected with low pressure oil way, servo valve and oil cylinder composition valve-controlled cylinder system；
The position sensor is connected with the cylinder piston rod, obtains the position signal of cylinder piston rod, is transferred to the control
Device processed；
The cylinder piston rod that the target location command signal and position sensor that controller provides the external world received obtain
The difference of current position signal is converted to servo valve control electric current, control servo valve work；Controller is according to error signal at the same time,
Motor speed is controlled, further the quantitative pump output flow change of control, so as to adjust system pressure；Drive cylinder piston rod.
A kind of 2. variable pressure and flow type hydraulic servomechanism based on electric machine speed regulation as claimed in claim 1, it is characterised in that institute
State in valve-controlled cylinder system, delivery outlet of the pressure oil through the servo valve enters oil cylinder, promotes cylinder piston rod to make straight-line displacement.
3. a kind of variable pressure and flow type hydraulic servomechanism based on electric machine speed regulation as claimed in claim 1, it is characterised in that also
Including overflow valve, the overflow valve is used to make excess traffic be back to low pressure oil when system pressure rises to over design load
Road, specifically includes end cap, O-ring, valve body, cone valve, spring, screw plug.
It is 4. a kind of such as the work of variable pressure and flow type hydraulic servomechanism of the claim 1-3 any one of them based on electric machine speed regulation
Method, it is characterised in that comprise the following steps：
S1, carry out system initialization to servo control mechanism；
The cylinder piston rod that the target location command signal and position sensor that S2, controller provide the external world received obtain
The difference of current position signal be converted to servo valve control electric current, control servo valve work；Controller is believed according to error at the same time
Number, motor speed is controlled, further the quantitative pump output flow change of control, so as to adjust system pressure；Drive cylinder piston rod；
S3, input new target position signal to controller, and the controller is according to new target position signal and position sensing
The difference of the position signal of device cylinder piston rod, controls servo valve and motor drive cylinder piston rod again；
S4, circulation perform above-mentioned steps S2 to S3, move back and forth cylinder piston rod.
5. the method for work of the variable pressure and flow type hydraulic servomechanism based on electric machine speed regulation as claimed in claim 4, its feature
It is, the step S2 further comprises：
S21, controller are lived according to the position of cylinder piston rod and the difference control servo valve and motor drive cylinder of target location
Stopper rod accelerates target location described in movement velocity fast approaching；
S22, controller further control servo valve and motor to drive according to the position of cylinder piston rod and the difference of target location
Cylinder piston rod slows down until stablizing in the target location.
6. the method for work of the variable pressure and flow type hydraulic servomechanism based on electric machine speed regulation as claimed in claim 4, its feature
It is, the step S3 further comprises：
S31, controller drive oil according to the position of cylinder piston rod and the difference control servo valve and motor of new target location
Cylinder piston rod accelerates target location new described in movement velocity fast approaching；
S32, controller further control servo valve and motor according to the difference of the position and new target location of cylinder piston rod
Drive cylinder piston rod slows down until stablizing in the new target location.
7. the method for work of the variable pressure and flow type hydraulic servomechanism based on electric machine speed regulation as claimed in claim 5, its feature
It is, the step S21 further comprises：
S211, the servo valve control current control servo valve start of controller output, output flow increase, and high pressure oil is from watching
The delivery outlet for taking valve flows into oil cylinder, promotes cylinder piston rod movement；
According to embedded control strategy, driving motor improves rotating speed for S212, the controller, and quantitative pump output flow is increased, carried
High system pressure, makes the cylinder piston rod position fast approaching target location.
8. the method for work of the variable pressure and flow type hydraulic servomechanism based on electric machine speed regulation as claimed in claim 5, its feature
It is, the step S22 further comprises：
S221, the servo valve control servo valve start of controller output, output flow diminishes, until be zero, oil cylinder it is defeated
Go out speed reduction, until stablizing in target location；
The control strategy control motor that S222, the controller embed reduces rotating speed, and quantitative pump output flow declines, system pressure
Decline therewith, until cylinder piston rod can be maintained static；
The control strategy control motor speed that S223, the controller embed maintains certain numerical value, makes quantitative pump output flow
Equal to leakage current amount in servo valve.
9. the method for work of the variable pressure and flow type hydraulic servomechanism based on electric machine speed regulation as claimed in claim 4, its feature
It is to further include：
When the controller drives the motor to be rotated with maximum speed, the quantitative pump output flow reaches maximum, oil
Excess traffic outside cylinder start needs, makes system pressure rise to over design load, and overflow valve is opened, and excess traffic, which passes through, to overflow
Stream valve is back to low pressure oil way, and system pressure falls after rise, maintains design load.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201610849277.0A CN106438584B (en) | 2016-09-23 | 2016-09-23 | A kind of variable pressure and flow type hydraulic servomechanism and method of work based on electric machine speed regulation |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201610849277.0A CN106438584B (en) | 2016-09-23 | 2016-09-23 | A kind of variable pressure and flow type hydraulic servomechanism and method of work based on electric machine speed regulation |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN106438584A CN106438584A (en) | 2017-02-22 |
| CN106438584B true CN106438584B (en) | 2018-04-20 |
Family
ID=58169385
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201610849277.0A Active CN106438584B (en) | 2016-09-23 | 2016-09-23 | A kind of variable pressure and flow type hydraulic servomechanism and method of work based on electric machine speed regulation |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN106438584B (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111501869B (en) * | 2020-05-20 | 2022-07-29 | 三一重机有限公司 | Electric control hydraulic servo control system and method and electric excavator |
| CN116255493B (en) * | 2023-05-15 | 2023-08-01 | 苏州海卓伺服驱动技术有限公司 | Servo valve adjusting and controlling method and system |
| CN117212292B (en) * | 2023-09-19 | 2024-04-09 | 佛山市康思达液压机械有限公司 | Hydraulic press oil cylinder positioning control method, device, equipment and storage medium |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5785144A (en) * | 1994-05-24 | 1998-07-28 | Mercedes-Benz Ag | Power steering system/servo control |
| CN201027714Y (en) * | 2007-04-20 | 2008-02-27 | 绍兴市肯特机械电子有限公司 | Hydraulic equipment controlled by servo motor |
| CN105351278A (en) * | 2015-12-10 | 2016-02-24 | 上海新跃仪表厂 | Novel compound electro-hydraulic servo control system |
| CN105346532A (en) * | 2015-10-26 | 2016-02-24 | 浙江万安科技股份有限公司 | Hydraulic servo boosting system |
-
2016
- 2016-09-23 CN CN201610849277.0A patent/CN106438584B/en active Active
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5785144A (en) * | 1994-05-24 | 1998-07-28 | Mercedes-Benz Ag | Power steering system/servo control |
| CN201027714Y (en) * | 2007-04-20 | 2008-02-27 | 绍兴市肯特机械电子有限公司 | Hydraulic equipment controlled by servo motor |
| CN105346532A (en) * | 2015-10-26 | 2016-02-24 | 浙江万安科技股份有限公司 | Hydraulic servo boosting system |
| CN105351278A (en) * | 2015-12-10 | 2016-02-24 | 上海新跃仪表厂 | Novel compound electro-hydraulic servo control system |
Also Published As
| Publication number | Publication date |
|---|---|
| CN106438584A (en) | 2017-02-22 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN100424361C (en) | Closed electrohydraulic controlling system | |
| CN106438584B (en) | A kind of variable pressure and flow type hydraulic servomechanism and method of work based on electric machine speed regulation | |
| CN201769389U (en) | Hydraulic press | |
| CN107630847A (en) | Electric ratio pressure continuously regulates and controls hydraulic motor/pump | |
| CN101865190A (en) | Position and flow double-close-loop direct-drive volume control electro-hydraulic servo system | |
| CN107061393B (en) | Closed model pump control hydraulic system | |
| CN110397634B (en) | Low-energy-consumption high-dynamic pump valve combined position servo system and control method thereof | |
| CN108533546B (en) | Hydraulic excavator power system adopting double-pump direct drive and differential fast forward automatic switching | |
| CN103573618B (en) | A kind of car variable-displacement power steering pump | |
| CN203516006U (en) | Passive clearance adjusting system of reciprocating compressor | |
| CN102829009A (en) | Hydraulic artificial muscle hydraulic drive and control system | |
| KR101776327B1 (en) | Continuous Control Variable Displacement Oil Pump Unit | |
| CN102943500A (en) | Energy-saving control method of hydraulic negative flow of excavator | |
| CN206874582U (en) | Closed model pump control hydraulic system | |
| CN204382705U (en) | Servo hydraulic press hybrid power two-way pump Ore-controlling Role | |
| CN105278559A (en) | Variable speed hydraulic power supply compound compensation control system and method | |
| CN107763202A (en) | A kind of electric-liquid type buncher speed compares optimal control system | |
| CN102494128B (en) | Pump control CVT electrohydraulic control system | |
| CN205918570U (en) | Axial plunger pump device of high accuracy electric proportional control | |
| CN104234988A (en) | Explosion-proof electronically-controlled closed pump and method for maintaining high utilization rate of engine power constantly thereby | |
| CN109441895B (en) | Servo electrohydraulic driver | |
| CN202746131U (en) | Swash plate type variable displacement piston pump | |
| CN202984634U (en) | Servo control system for die-casting machine | |
| CN105644619A (en) | Intelligent hydraulic power steering system and control method thereof | |
| CN205381305U (en) | Intelligence power -assisted steering system |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |