CN107013517A - Method for reducing throttling loss of hydraulic system - Google Patents
Method for reducing throttling loss of hydraulic system Download PDFInfo
- Publication number
- CN107013517A CN107013517A CN201610057523.9A CN201610057523A CN107013517A CN 107013517 A CN107013517 A CN 107013517A CN 201610057523 A CN201610057523 A CN 201610057523A CN 107013517 A CN107013517 A CN 107013517A
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- Prior art keywords
- valve
- way throttle
- hydraulic
- throttle valve
- way
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- 238000000034 method Methods 0.000 title claims abstract description 22
- 238000006073 displacement reaction Methods 0.000 claims description 24
- 238000013016 damping Methods 0.000 claims description 16
- 239000012530 fluid Substances 0.000 claims description 7
- 230000001276 controlling effect Effects 0.000 abstract 1
- 230000001105 regulatory effect Effects 0.000 abstract 1
- 230000007363 regulatory process Effects 0.000 abstract 1
- 239000007788 liquid Substances 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000009514 concussion Effects 0.000 description 1
- 230000006866 deterioration Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 239000002699 waste material Substances 0.000 description 1
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
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/023—Excess flow valves, e.g. for locking cylinders in case of 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
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
- F15B11/17—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors using two or more pumps
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
The invention provides a method for reducing throttling loss of a hydraulic system. When the pressure difference between two ends of the one-way throttle valve I is higher or lower than the set value P of the servo slide valve II0When the pressure difference between two ends of the one-way throttle valve I is used for controlling the servo slide valve II and the variable hydraulic pump, the rotating speed of the quantitative hydraulic motor and the flow of the one-way throttle valve I are regulated, so that the pressure difference between two ends of the one-way throttle valve I is equal to P0The servo spool II is not actuated and enters a steady state. The reversing valve I is positioned at the left position, the pressure difference at the two ends of the one-way throttle valve II controls the servo slide valve I and the variable hydraulic pump II, and the rotating speed of the quantitative hydraulic motor II is adjusted, so that the flow passing through the one-way throttle valve II is constant. The invention can effectively reduce the throttling loss in the speed regulating process of the hydraulic system, greatly save energy and prolong the service life of oil.
Description
Technical field
The invention belongs to HYDRAULIC CONTROL SYSTEM field, more particularly to a kind of method for reducing hydraulic system restriction loss.
Background technology
The hydraulic system of equipment of Hot Strip Mill adjusts the speed of executive component using throttling method, to meet technological requirement.At present,
Hydraulic system be typically by hydraulic cylinder, 2 one-way throttle valves, 2 hydraulic control one-way valves, 2 reversal valves and pressure oil pipeline,
Return line is constituted.During throttle grverning, substantial amounts of pressure potential is changed into heat energy, not only causes the waste of the energy, and
And accelerate the deterioration process of fluid.
So that hydraulic cylinder piston rod stretches out as an example, the course of work of hydraulic system speed control loop is：The commutation of reversal valve I is in right position,
Pressure oil enters the control chamber of hydraulic control one-way valve II, hydraulic control one-way valve II is in pass-through state.The commutation of reversal valve II is in right position,
Pressure oil enters the plunger shaft of hydraulic cylinder, hydraulic cylinder through the check valve in reversal valve II, hydraulic control one-way valve I, one-way throttle valve II
Fluid in rod chamber enters the oil return box of reversal valve II through the choke valve in one-way throttle valve I, hydraulic control one-way valve II.One-way throttle
Valve I sets up the speed of hydraulic cylinder, and its difference pressuring loss is in 6~10MPa, and restriction loss is very big.
The content of the invention
The present invention provides a kind of method for reducing hydraulic system restriction loss, and its purpose is intended to save the energy, extends the fluid life-span.
Therefore, the technical solution that the present invention is taken is：
A kind of method for reducing hydraulic system restriction loss, it is characterised in that：
Set up hydraulic control system：
Hydraulic control system include hydraulic cylinder, one-way throttle valve I, one-way throttle valve II, servo guiding valve I, servo guiding valve II,
Hydraulic control one-way valve I, hydraulic control one-way valve II, volume adjustable hydraulic pump I, volume adjustable hydraulic pump II, constant displacement hydraulic motor I, quantitative hydraulic
Motor II, reversal valve I, reversal valve II, check valve I, check valve II, check valve III, check valve IV, damping hole I, resistance
Buddhist nun hole II, damping hole III, damping hole IV, pressure oil pipeline and return line；I group of volume adjustable hydraulic pump I and constant displacement hydraulic motor
Into a hydraulic transformer, volume adjustable hydraulic pump II constitutes a hydraulic transformer with constant displacement hydraulic motor II；
Hydraulic control process：
The commutation of reversal valve I is in right position, and pressure oil opens hydraulic control one-way valve II；
The commutation of reversal valve II is in right position, and pressure oil passes through reversal valve II, check valve III, hydraulic control one-way valve I, one-way throttle valve
Check valve in II enters hydraulic cylinder, promotes hydraulic cylinder piston rod to stretch out；
The fluid of hydraulic cylinder rod chamber pass through one-way throttle valve I in choke valve, hydraulic control one-way valve II, constant displacement hydraulic motor I,
Check valve IV, the oil return box of reversal valve II；
Set the operating pressure value P of servo guiding valve II0For some determination value in the range of 0.2~2MPa, calculated according to technological requirement
Go out the opening degree of one-way throttle valve I, as long as so keeping the pressure difference at the two ends of one-way throttle valve I constant, by one-way throttle valve I
Flow be exactly a steady state value so that ensure hydraulic cylinder according to technological requirement speed run；
When the pressure difference at the two ends of one-way throttle valve I exceedes the setting value P of servo guiding valve II0When, illustrate the stream by one-way throttle valve I
Amount is more than technological requirement more than the speed of desired value, i.e. hydraulic cylinder, and the action of servo guiding valve II increases the discharge capacity of volume adjustable hydraulic pump I,
The power increase that volume adjustable hydraulic pump I needs, so that the power output increase of constant displacement hydraulic motor I, I turn of constant displacement hydraulic motor
Speed declines, by the flow-reduction of one-way throttle valve I, and the pressure difference at the two ends of one-way throttle valve I is equal to P0, servo guiding valve II keeps
Standing state, enters a stable state；
When the pressure difference at the two ends of one-way throttle valve I is less than the setting value P of servo guiding valve II0When, illustrate the stream by one-way throttle valve I
Amount is less than technological requirement less than the speed of desired value, i.e. hydraulic cylinder, and the action of servo guiding valve II reduces the discharge capacity of volume adjustable hydraulic pump I,
The power reduction that volume adjustable hydraulic pump I needs, so that the power output of constant displacement hydraulic motor I reduces, I turn of constant displacement hydraulic motor
Speed rises, and by the flow increase of one-way throttle valve I, the pressure difference at the two ends of one-way throttle valve I is equal to P0, servo guiding valve II keeps
Standing state, enters a stable state；
When reversal valve I, the commutation of reversal valve II are in left position, the process that its hydraulic cylinder piston rod is retracted and the process class of above-mentioned stretching
Seemingly, in the process, the pressure difference control servo guiding valve I at the two ends of one-way throttle valve II, and then the discharge capacity of control volume adjustable hydraulic pump II,
The rotating speed of adjustment quantitative hydraulic motor II, so that it is constant by the flow of one-way throttle valve II, the speed of hydraulic cylinder is met work
Skill requirement.
Beneficial effects of the present invention are：
The present invention can effectively reduce the restriction loss in hydraulic system speed regulation process, so as to be greatly saved the energy, extend the fluid life-span,
Realize environment-friendly, resource-effective target.
Brief description of the drawings
Fig. 1 is that hydraulic control system hydraulic cylinder piston rod stretches out view.
In figure：Hydraulic cylinder 1, one-way throttle valve I 2, one-way throttle valve II 3, servo guiding valve I 4, hydraulic control one-way valve I 5, liquid
Control check valve II 6, servo guiding valve II 7, volume adjustable hydraulic pump I 8, constant displacement hydraulic motor I 9, check valve I 10, reversal valve I 11,
Reversal valve II 12, constant displacement hydraulic motor II 13, volume adjustable hydraulic pump II 14, check valve II 15, check valve III 16, check valve IV 17,
Damping hole I 18, damping hole II 19, damping hole III 20, damping hole IV 21.P is pressure oil pipeline, and T is return line.
Embodiment
Set up hydraulic control system：
Hydraulic control system includes hydraulic cylinder 1, one-way throttle valve I 2, one-way throttle valve II 3, servo guiding valve I 4, fluid-control one-way
Valve I 5, hydraulic control one-way valve II 6, servo guiding valve II 7, volume adjustable hydraulic pump I 8, constant displacement hydraulic motor I 9, check valve I 10, change
To valve I 11, reversal valve II 12, constant displacement hydraulic motor II 13, volume adjustable hydraulic pump II 14, check valve II 15, check valve III 16,
Check valve IV 17, damping hole I 18, damping hole II 19, damping hole III 20, damping hole IV 21, pressure oil pipeline P and oil return pipe
Road T.
Volume adjustable hydraulic pump I 8 constitutes a hydraulic transformer, volume adjustable hydraulic pump II 14 and quantitative hydraulic with constant displacement hydraulic motor I 9
Motor II 13 constitutes a hydraulic transformer.
The control process of hydraulic control system：
The commutation of reversal valve I 11 is in right position, and pressure oil opens hydraulic control one-way valve II 6.
The commutation of reversal valve II 12 is in right position, and pressure oil is by reversal valve II 12, check valve III 16, hydraulic control one-way valve I 5, list
Check valve into choke valve II 3 enters hydraulic cylinder 1, promotes the piston rod of hydraulic cylinder 1 to stretch out.
The fluid of the rod chamber of hydraulic cylinder 1 is by the choke valve in one-way throttle valve I 2, hydraulic control one-way valve II 6, constant displacement hydraulic motor
I 9, oil return box after check valve IV 17, reversal valve II 12.
Set the operating pressure value P of servo guiding valve II 70For some determination value in the range of 0.2~2MPa, according to technological requirement meter
The opening degree of one-way throttle valve I 2 is calculated, as long as so keeping the pressure difference at the two ends of one-way throttle valve I 2 constant, by one-way throttle
The flow of valve I 2 is exactly a steady state value, so as to ensure that hydraulic cylinder 1 is run according to the speed of technological requirement.
When the pressure difference at the two ends of one-way throttle valve I 2 exceedes the setting value P of servo guiding valve II 70When, illustrate to pass through one-way throttle valve I 2
Flow be more than desired value, the i.e. speed of hydraulic cylinder 1 be more than technological requirement, servo guiding valve II 7 action make volume adjustable hydraulic pump I 8
Discharge capacity increases, the power increase that volume adjustable hydraulic pump I 8 needs, so that the power output increase of constant displacement hydraulic motor I 9, quantitative
The rotating speed of hydraulic motor I 9 declines, by the flow-reduction of one-way throttle valve I 2, and the pressure difference at the two ends of one-way throttle valve I 2 is equal to P0,
Servo guiding valve II 7 keeps standing state, enters a stable state.
When the pressure difference at the two ends of one-way throttle valve I 2 is less than the setting value P of servo guiding valve II 70When, illustrate to pass through one-way throttle valve I 2
Flow be less than desired value, the i.e. speed of hydraulic cylinder 1 be less than technological requirement, servo guiding valve II 7 action make volume adjustable hydraulic pump I 8
Discharge capacity reduces, the power reduction that volume adjustable hydraulic pump I 8 needs, so that the power output of constant displacement hydraulic motor I 9 reduces, it is quantitative
The rotating speed of hydraulic motor I 9 rises, and by the flow increase of one-way throttle valve I 2, the pressure difference at the two ends of one-way throttle valve I 2 is equal to P0,
Servo guiding valve II 7 keeps standing state, enters a stable state.
When reversal valve I 11, the commutation of reversal valve II 12 are in left position, the process that its piston rod of hydraulic cylinder 1 is retracted and above-mentioned stretching
Process is similar.In the process, the pressure difference control servo guiding valve I 4 at the two ends of one-way throttle valve II 3, and then control volume adjustable hydraulic pump
II 14 discharge capacity, the rotating speed of adjustment quantitative hydraulic motor II 13, so that it is constant by the flow of one-way throttle valve II 3, make liquid
The speed of cylinder pressure 1 meets technological requirement.
Damping hole I 18, damping hole II 19 can make the action of servo guiding valve II 7 gentle, to avoid servo guiding valve II 7 frequent
Action, forms concussion state.And servo guiding valve II 7 should then leave dead band when manufacturing and designing.
Claims (1)
1. a kind of method for reducing hydraulic system restriction loss, it is characterised in that：
Set up hydraulic control system：
Hydraulic control system include hydraulic cylinder, one-way throttle valve I, one-way throttle valve II, servo guiding valve I, servo guiding valve II,
Hydraulic control one-way valve I, hydraulic control one-way valve II, volume adjustable hydraulic pump I, volume adjustable hydraulic pump II, constant displacement hydraulic motor I, quantitative hydraulic
Motor II, reversal valve I, reversal valve II, check valve I, check valve II, check valve III, check valve IV, damping hole I, resistance
Buddhist nun hole II, damping hole III, damping hole IV, pressure oil pipeline and return line；I group of volume adjustable hydraulic pump I and constant displacement hydraulic motor
Into a hydraulic transformer, volume adjustable hydraulic pump II constitutes a hydraulic transformer with constant displacement hydraulic motor II；
Hydraulic control process：
The commutation of reversal valve I is in right position, and pressure oil opens hydraulic control one-way valve II；
The commutation of reversal valve II is in right position, and pressure oil passes through reversal valve II, check valve III, hydraulic control one-way valve I, one-way throttle valve
Check valve in II enters hydraulic cylinder, promotes hydraulic cylinder piston rod to stretch out；
The fluid of hydraulic cylinder rod chamber pass through one-way throttle valve I in choke valve, hydraulic control one-way valve II, constant displacement hydraulic motor I,
Check valve IV, the oil return box of reversal valve II；
Set the operating pressure value P of servo guiding valve II0For some determination value in the range of 0.2~2MPa, calculated according to technological requirement
Go out the opening degree of one-way throttle valve I, as long as so keeping the pressure difference at the two ends of one-way throttle valve I constant, by one-way throttle valve I
Flow be exactly a steady state value so that ensure hydraulic cylinder according to technological requirement speed run；
When the pressure difference at the two ends of one-way throttle valve I exceedes the setting value P of servo guiding valve II0When, illustrate the stream by one-way throttle valve I
Amount is more than technological requirement more than the speed of desired value, i.e. hydraulic cylinder, and the action of servo guiding valve II increases the discharge capacity of volume adjustable hydraulic pump I,
The power increase that volume adjustable hydraulic pump I needs, so that the power output increase of constant displacement hydraulic motor I, I turn of constant displacement hydraulic motor
Speed declines, by the flow-reduction of one-way throttle valve I, and the pressure difference at the two ends of one-way throttle valve I is equal to P0, servo guiding valve II keeps
Standing state, enters a stable state；
When the pressure difference at the two ends of one-way throttle valve I is less than the setting value P of servo guiding valve II0When, illustrate the stream by one-way throttle valve I
Amount is less than technological requirement less than the speed of desired value, i.e. hydraulic cylinder, and the action of servo guiding valve II reduces the discharge capacity of volume adjustable hydraulic pump I,
The power reduction that volume adjustable hydraulic pump I needs, so that the power output of constant displacement hydraulic motor I reduces, I turn of constant displacement hydraulic motor
Speed rises, and by the flow increase of one-way throttle valve I, the pressure difference at the two ends of one-way throttle valve I is equal to P0, servo guiding valve II keeps
Standing state, enters a stable state；
When reversal valve I, the commutation of reversal valve II are in left position, the process that its hydraulic cylinder piston rod is retracted and the process class of above-mentioned stretching
Seemingly, in the process, the pressure difference control servo guiding valve I at the two ends of one-way throttle valve II, and then the discharge capacity of control volume adjustable hydraulic pump II,
The rotating speed of adjustment quantitative hydraulic motor II, so that it is constant by the flow of one-way throttle valve II, the speed of hydraulic cylinder is met work
Skill requirement.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201610057523.9A CN107013517A (en) | 2016-01-27 | 2016-01-27 | Method for reducing throttling loss of hydraulic system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201610057523.9A CN107013517A (en) | 2016-01-27 | 2016-01-27 | Method for reducing throttling loss of hydraulic system |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN107013517A true CN107013517A (en) | 2017-08-04 |
Family
ID=59438590
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201610057523.9A Pending CN107013517A (en) | 2016-01-27 | 2016-01-27 | Method for reducing throttling loss of hydraulic system |
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| Country | Link |
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| CN (1) | CN107013517A (en) |
Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3963378A (en) * | 1975-06-04 | 1976-06-15 | Caterpillar Tractor Co. | Part throttle control -- pump override |
| CN1190601C (en) * | 2002-10-29 | 2005-02-23 | 浙江大学 | Load sensing hydraulic system for controlling six-way multiple unit valve |
| CN103758810A (en) * | 2013-10-22 | 2014-04-30 | 陕西盛迈石油有限公司 | Open core type load sensory system |
| WO2014119569A1 (en) * | 2013-01-29 | 2014-08-07 | 日立建機株式会社 | Pressure oil energy recovery device for operating machine |
| CN204200727U (en) * | 2014-09-19 | 2015-03-11 | 鞍钢股份有限公司 | Hydraulic speed regulation loop system of axial plunger variable displacement motor |
| CN104863914A (en) * | 2015-04-13 | 2015-08-26 | 徐州徐工液压件有限公司 | Electrohydraulic joint control flow collecting valve |
| CN103321981B (en) * | 2013-07-01 | 2015-09-02 | 武汉船用机械有限责任公司 | Shark jaw oil cylinder working-pressure protective system |
-
2016
- 2016-01-27 CN CN201610057523.9A patent/CN107013517A/en active Pending
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3963378A (en) * | 1975-06-04 | 1976-06-15 | Caterpillar Tractor Co. | Part throttle control -- pump override |
| CN1190601C (en) * | 2002-10-29 | 2005-02-23 | 浙江大学 | Load sensing hydraulic system for controlling six-way multiple unit valve |
| WO2014119569A1 (en) * | 2013-01-29 | 2014-08-07 | 日立建機株式会社 | Pressure oil energy recovery device for operating machine |
| CN103321981B (en) * | 2013-07-01 | 2015-09-02 | 武汉船用机械有限责任公司 | Shark jaw oil cylinder working-pressure protective system |
| CN103758810A (en) * | 2013-10-22 | 2014-04-30 | 陕西盛迈石油有限公司 | Open core type load sensory system |
| CN204200727U (en) * | 2014-09-19 | 2015-03-11 | 鞍钢股份有限公司 | Hydraulic speed regulation loop system of axial plunger variable displacement motor |
| CN104863914A (en) * | 2015-04-13 | 2015-08-26 | 徐州徐工液压件有限公司 | Electrohydraulic joint control flow collecting valve |
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Application publication date: 20170804 |
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