CN110219836A - A kind of mine hoist safety switching brake perseverance deceleration hydraulic system and braking method - Google Patents
A kind of mine hoist safety switching brake perseverance deceleration hydraulic system and braking method Download PDFInfo
- Publication number
- CN110219836A CN110219836A CN201910495369.7A CN201910495369A CN110219836A CN 110219836 A CN110219836 A CN 110219836A CN 201910495369 A CN201910495369 A CN 201910495369A CN 110219836 A CN110219836 A CN 110219836A
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- directional control
- control valve
- solenoid directional
- valve
- mouth
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- 238000000034 method Methods 0.000 title claims abstract description 13
- 239000002828 fuel tank Substances 0.000 claims abstract description 17
- 239000003921 oil Substances 0.000 claims description 102
- 239000012530 fluid Substances 0.000 claims description 8
- 238000001802 infusion Methods 0.000 claims description 7
- 230000008676 import Effects 0.000 claims description 6
- 238000012544 monitoring process Methods 0.000 claims description 5
- 239000007788 liquid Substances 0.000 claims description 4
- 239000003638 chemical reducing agent Substances 0.000 claims description 3
- 239000010720 hydraulic oil Substances 0.000 claims description 3
- 238000010992 reflux Methods 0.000 claims description 2
- 238000009825 accumulation Methods 0.000 claims 2
- 230000005611 electricity Effects 0.000 description 5
- 230000006837 decompression Effects 0.000 description 2
- 239000003245 coal Substances 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 230000007812 deficiency Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
Classifications
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B66—HOISTING; LIFTING; HAULING
- B66D—CAPSTANS; WINCHES; TACKLES, e.g. PULLEY BLOCKS; HOISTS
- B66D5/00—Braking or detent devices characterised by application to lifting or hoisting gear, e.g. for controlling the lowering of loads
- B66D5/02—Crane, lift hoist, or winch brakes operating on drums, barrels, or ropes
- B66D5/24—Operating devices
- B66D5/26—Operating devices pneumatic or hydraulic
-
- 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
- F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
- F15B1/02—Installations or systems with accumulators
-
- 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
- F15B13/025—Pressure reducing 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
- 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
- F15B13/06—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with two or more servomotors
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B66—HOISTING; LIFTING; HAULING
- B66D—CAPSTANS; WINCHES; TACKLES, e.g. PULLEY BLOCKS; HOISTS
- B66D5/00—Braking or detent devices characterised by application to lifting or hoisting gear, e.g. for controlling the lowering of loads
- B66D5/02—Crane, lift hoist, or winch brakes operating on drums, barrels, or ropes
- B66D5/12—Crane, lift hoist, or winch brakes operating on drums, barrels, or ropes with axial effect
- B66D5/14—Crane, lift hoist, or winch brakes operating on drums, barrels, or ropes with axial effect embodying discs
-
- 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
- F15B2013/002—Modular valves, i.e. consisting of an assembly of interchangeable components
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/205—Systems with pumps
- F15B2211/20507—Type of prime mover
- F15B2211/20515—Electric motor
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/205—Systems with pumps
- F15B2211/2053—Type of pump
- F15B2211/20546—Type of pump variable 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
- F15B2211/25—Pressure control functions
-
- 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
- F15B2211/315—Directional control characterised by the connections of the valve or valves in the circuit
- F15B2211/31523—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source and an output member
- F15B2211/31541—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source and an output member having a single pressure source and multiple output members
-
- 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
-
- 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
- F15B2211/634—Electronic controllers using input signals representing a state of a valve
-
- 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
- F15B2211/665—Methods of control using electronic components
- F15B2211/6653—Pressure control
-
- 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
- F15B2211/665—Methods of control using electronic components
- F15B2211/6658—Control using different modes, e.g. four-quadrant-operation, working mode and transportation mode
Abstract
The invention discloses a kind of mine hoist safety switching brake perseverance deceleration hydraulic system and braking method, system includes including fuel tank, motor, variable pump, electromagnetic proportion relief valve, check valve, accumulator, electromagnetic relief valve, pressure reducing valve, damper brake group, several solenoid directional control valves and solenoid-operated proportional reversal valve；It avoids accumulator in the impact caused by lifting system of braking process rapid pressure by the different commutations of solenoid-operated proportional reversal valve, reduces the oil pressure of damper brake group linearly slowly, keep hoisting container to stablize and slow down；When constant deceleration failure, it is immediately switched to two stage braking, guarantee that lifting system is depressurized to the two stage braking oil pressure value of setting first with stable speed using the first pressure reducing valve of setting and the second pressure reducing valve, elevator is set to be in half braking state, being depressured again after postponing a period of time is that zero realization is braked completely.This mode of braking can prevent two stage braking after constant deceleration brake disabler from causing to impact to lifting system, guarantee the reliability of braking.
Description
Technical field
The present invention relates to a kind of safe switching brake perseverance deceleration hydraulic stations suitable for Hoist Emergency Braking, and in particular to
A kind of mine hoist safety switching brake perseverance deceleration hydraulic system and braking method, belong to mine hoist technical field.
Background technique
In coal mine production system, mine hoisting system is the important component for guaranteeing mine normal operation, and is braked
The reliability of system directly affects the safe handling of mine hoist equipment.
Currently, the braking system that elevator uses is mostly fluid pressure type disc type brake, braking is divided into service braking and safety
Braking.Service braking simply by adjust proportional pressure control valve to piezoelectric voltage so that adjust the oil pressure of disk brake, come real
The start and stop of existing elevator；It is to pass through monitoring that safety arrestment, which is divided into constant deceleration brake, level-one braking and two stage braking, constant deceleration brake,
Hoist Speed closed loop feedback adjusts the oil pressure of disc type brake to adjust proportional reversing valve or proportional servo valve commutation, allows
The slow locking brake disc of brake shoe, maintains deceleration in one stable range；Level-one braking is exactly two groups of disc type brakes
The oil pressure of device is all adjusted to zero, directly carrys out locking brake disc with maximum braking moment；Two stage braking is first disk brake
Oil pressure adjusting be reduced to a two stage braking pressure value, its oil pressure value is then reduced to zero again, is made by two-stage oil pressure
It is dynamic.
But most two stage braking oil pressure value is given when installing hydraulic station, after perseverance slows down failure,
No matter the oil pressure in damper brake has much, and two stage braking can all stablize oil pressure in a setting value, will lead to permanent deceleration in this way
It is switched to during two stage braking after failure, since accumulator fluid infusion acts on, oil pressure is possible to rise, and can give lifting system band
To impact, increase the danger for the rope that breaks, to bring safety accident.
Summary of the invention
In order to overcome various deficiencies of the existing technology, the present invention provides a kind of mine hoist safety switching brake perseverance deceleration
Hydraulic system and braking method prevent two stage braking after constant deceleration brake disabler from causing to impact to lifting system, guarantee system
Dynamic reliability.
To solve the above-mentioned problems, a kind of mine hoist safety switching brake perseverance deceleration hydraulic system of the present invention, including fuel tank,
The import of motor, variable pump, accumulator, electromagnetic switch valve group, braking valve group and reducer unit, variable pump passes through strainer and fuel tank
It is connected, the outlet of variable pump is connected by strainer with the P of solenoid directional control valve G1 mouth, and the T mouth of solenoid directional control valve G1 passes through the respectively
One check valve is connected with the first accumulator, is connected by second one-way valve with the second accumulator and the B with solenoid directional control valve G6
Mouth is connected；The P mouth of solenoid directional control valve G6, solenoid directional control valve G66 P mouth with the first brake valve oil inlet phase in braking valve group
Connect, the P mouth of solenoid directional control valve G7, the P mouth of solenoid directional control valve G77 are connected with the second brake valve oil inlet in braking valve group；
The A mouth of solenoid directional control valve G6, the P mouth of the A mouth of solenoid directional control valve G66 and solenoid directional control valve G2, the P mouth of solenoid directional control valve G22, electricity
The P mouth of magnetic reversal valve G3, the P mouth of solenoid directional control valve G33 are connected with the P of solenoid directional control valve G4 mouth；The A mouth of solenoid directional control valve G2,
It is connected after the A mouth of solenoid directional control valve G22 is in parallel with the first pressure reducing valve；The A mouth of the A mouth of solenoid directional control valve G3, solenoid directional control valve G33
It is connected after parallel connection with the second pressure reducing valve；On the oil circuit being connected between the P mouth of solenoid directional control valve G4 and the P of solenoid directional control valve G33 mouth
Third pressure reducing valve in parallel；For the setting value of first pressure reducing valve less than the setting value of the second pressure reducing valve, the setting value of the second pressure reducing valve is small
In the setting value of third pressure reducing valve.
Further, the T mouth of solenoid directional control valve G4 is connected with the P of solenoid directional control valve G44 mouth, the T mouth of solenoid directional control valve G44
It is connected with the B mouth of solenoid-operated proportional reversal valve G5, the P mouth of solenoid-operated proportional reversal valve G5 is connected in parallel on the second accumulator and second one-way valve
On connected oil circuit, the T mouth of solenoid-operated proportional reversal valve G5 is connected by electromagnetic relief valve with fuel tank.
Further, the first accumulator passes through B mouth, the solenoid directional control valve of first throttle valve Yu solenoid directional control valve G2 respectively
The B mouth of G22 is connected, and is connected by second throttle with the B mouth of the B of solenoid directional control valve G3 mouth, solenoid directional control valve G33.
Further, solenoid-operated proportional in parallel on the oil circuit being connected between the outlet of variable pump and the P of solenoid directional control valve G1 mouth
The oil outlet of the oil inlet of overflow valve, electromagnetic proportion relief valve is connected by radiator with fuel tank.
Solenoid directional control valve G1, solenoid directional control valve G2, solenoid directional control valve G22, solenoid directional control valve G3, solenoid directional control valve G33, electricity
Magnetic reversal valve G4, solenoid directional control valve G44, solenoid directional control valve G6, solenoid directional control valve G66, solenoid directional control valve G7, solenoid directional control valve
G77 is equipped with valve position monitoring sensor.
The T mouth of solenoid directional control valve G1, the import of the first accumulator, the second accumulator, A mouth, the damper brake of solenoid directional control valve G
Group oil inlet is equipped with oil pressure sensor.
A kind of mine hoist safety switching brake perseverance deceleration hydraulic system braking method, which comprises the steps of:
A), when braking under normal operating conditions, proportional pressure control valve is gradually reduced to zero from operating voltage to piezoelectric voltage, oil pressure
It is gradually reduced to residual voltage from operating oil pressure, damper brake group is gradually closed a floodgate, and full braking state is reached, and elevator stops working；
B), when safety failure occurs for elevator, control motor 2 stops working, and solenoid directional control valve G1 power loss is in right position,
And different location realizes mine hoist safety braking in well according to different hoisting containers, it is specific as follows:
When hoisting container is located at well head, solenoid directional control valve G7 in parallel and solenoid directional control valve G77 immediately power loss commutate to
Right position, the rapid oil return box of the hydraulic oil of damper brake group, oil pressure are reduced to rapidly zero, reach full braking state by level-one braking, real
Now stop immediately；
When hoisting container is located in well, solenoid directional control valve G6 in parallel and solenoid directional control valve G66 immediately power loss commutate to
Right position, and solenoid directional control valve G7 and solenoid directional control valve G77 in parallel is failure to actuate and maintains left position state, solenoid directional control valve G2, electromagnetism
Reversal valve G22, solenoid directional control valve G3, solenoid directional control valve G33, which are failure to actuate, maintains left position state, and the oil pressure of damper brake group is immediately from work
The oil pressure of third pressure reducing valve setting is reduced to as oil pressure；
Meanwhile solenoid directional control valve G4 and solenoid directional control valve G44 power loss are in right position, solenoid-operated proportional reversal valve G5 is constantly left
Right commutation, when solenoid-operated proportional reversal valve G5 is in right position, the second accumulator carries out fluid infusion to damper brake group, makes up deceleration value
Excessive, when solenoid-operated proportional reversal valve G5 is in left position, by electromagnetic relief valve reflux fuel tank, increase subtracts the oil liquid of damper brake group
Velocity amplitude keeps hoisting container deceleration to maintain a stable model so that making the oil pressure of damper brake group linearly slowly reduces
In enclosing, until oil pressure is reduced to zero, it is in complete on-position；
C), piezoelectric voltage is given to realize constant deceleration brake by adjusting solenoid-operated proportional reversal valve G5, when deceleration is excessive or mistake
Small when constant deceleration brake being caused to fail, be immediately switched to two stage braking: solenoid directional control valve G4, solenoid directional control valve G44 obtain electric be in
Left position blocks system to carry out constant deceleration brake, while solenoid directional control valve G2, solenoid directional control valve G22 power loss or solenoid directional control valve
G3, solenoid directional control valve G33 power loss are in right position, and the oil pressure of damper brake group is made to be reduced to the setting value or the second decompression of the first pressure reducing valve
The setting value of valve, while the first accumulator passes through first throttle valve or second throttle to damper brake group fluid infusion, stablizes system
In a two stage braking oil pressure value, elevator is in half braking state, after delay 5 seconds, solenoid directional control valve G7 and solenoid directional control valve
G77 power loss is in right position, so that the oil pressure of damper brake group is reduced to zero, elevator is braked completely.
Specifically, two stage braking is realized by following two ways in above-mentioned c) step:
The first, when damper brake group oil pressure value be lower than the second pressure reducing valve setting value, higher than the setting of the first pressure reducing valve
When value, solenoid directional control valve G2, solenoid directional control valve G22 power loss execute low oil pressure two stage braking；
Second, when the oil pressure value of damper brake group is higher than the setting value of the second pressure reducing valve, solenoid directional control valve G3, electromagnetic switch
Valve G33 power loss executes high oil pressure two stage braking.
The present invention avoids accumulator in braking process rapid pressure to promotion by the different commutations of solenoid-operated proportional reversal valve
It is impacted caused by system, reduces the oil pressure of damper brake group linearly slowly, kept hoisting container to stablize and slow down；When constant deceleration loses
When effect, it is immediately switched to two stage braking, guarantees lifting system first with steady using the first pressure reducing valve of setting and the second pressure reducing valve
Fixed speed is depressurized to the two stage braking oil pressure value of setting, and elevator is made to be in half braking state, drops again after postponing a period of time
Pressure is that zero realization is braked completely.The two stage braking mode that this hydraulic system is realized, more compared to previous mode of braking
Securely and reliably, down speeding procedure is more steady, avoids the oil pressure decline unexpected ftercompction of too fast or accumulator caused by lifting system
Impact, moreover it is possible to two stage braking oil pressure selectively be braked after the failure of constant pressure braking function.
Detailed description of the invention
Fig. 1 is hydraulic system principle figure in the present invention；
In figure: 1, fuel tank；2, motor；3, variable pump；4, electromagnetic proportion relief valve；5.1, the first check valve；5.2, second
Check valve；6.1, the first accumulator；6.2, the second accumulator；7, electromagnetic relief valve；8.1, the first pressure reducing valve；8.2, the second decompression
Valve；8.3, third pressure reducing valve；9.1 first throttle valve；9.2, second throttle；10, valve position monitoring sensor；11, oil pressure senses
Device；12, damper brake group；Solenoid directional control valve G1, solenoid directional control valve G2, solenoid directional control valve G22, solenoid directional control valve G3, electromagnetic switch
Valve G33, solenoid directional control valve G4, solenoid directional control valve G44, solenoid-operated proportional reversal valve G5, solenoid directional control valve G6, solenoid directional control valve G66,
Solenoid directional control valve G7, solenoid directional control valve G77.
Specific embodiment
The present invention is described in detail in the following with reference to the drawings and specific embodiments.
As shown in Figure 1, a kind of mine hoist safety switching brake perseverance deceleration hydraulic system, including fuel tank 1, motor 2, variable pump
3, the import of accumulator, electromagnetic switch valve group, braking valve group and reducer unit, variable pump 3 is connected by strainer with fuel tank 1, is become
The outlet of amount pump 3 is connected by strainer with the P of solenoid directional control valve G1 mouth, the P mouth of the outlet and solenoid directional control valve G1 of variable pump 3
Between on the oil circuit that is connected in parallel electromagnetic proportion relief valve 4 oil inlet, the oil outlet of electromagnetic proportion relief valve 4 by radiator with
Fuel tank phase；
The T mouth of solenoid directional control valve G1 is connected with the first accumulator 6.1 by the first check valve 5.1 respectively, is single by second
It is connected to valve 5.2 with the second accumulator 6.2 and is connected with the B of solenoid directional control valve G6 mouth；P mouth, the electromagnetism of solenoid directional control valve G6
The P mouth of reversal valve G66 is connected with the first brake valve oil inlet in braking valve group 12, and P mouth, the electromagnetism of solenoid directional control valve G7 changes
It is connected to the P mouth of valve G77 with the second brake valve oil inlet in braking valve group 12, T mouth, the electromagnetic switch of solenoid directional control valve G6
The T mouth oil return of the T mouth of valve G66, the T mouth of solenoid directional control valve G7, solenoid directional control valve G77 is to fuel tank；The A of solenoid directional control valve G6
Mouthful, the A mouth of solenoid directional control valve G66 and the P mouth of solenoid directional control valve G2, the P mouth of solenoid directional control valve G22, solenoid directional control valve G3 P
Mouthful, the P mouth of solenoid directional control valve G33 is connected with the P of solenoid directional control valve G4 mouth；A mouth, the solenoid directional control valve G22 of solenoid directional control valve G2
A mouth it is in parallel after be connected with the first pressure reducing valve 8.1；The A mouth of solenoid directional control valve G3, solenoid directional control valve G33 A mouth it is in parallel after with the
Two pressure reducing valves 8.2 are connected；Third in parallel on the oil circuit being connected between the P mouth of solenoid directional control valve G4 and the P of solenoid directional control valve G33 mouth
Pressure reducing valve 8.3；Setting value of the setting value of first pressure reducing valve 8.1 less than the second pressure reducing valve 8.2, the setting of the second pressure reducing valve 8.2
Value is less than the setting value of third pressure reducing valve 8.3；
The T mouth of solenoid directional control valve G4 is connected with the P of solenoid directional control valve G44 mouth, the T mouth and electromagnetism ratio of solenoid directional control valve G44
The B mouth of example reversal valve G5 is connected, and the P mouth of solenoid-operated proportional reversal valve G5 is connected in parallel on what the second accumulator 6.2 was connected with check valve 5.2
On oil circuit, the T mouth of solenoid-operated proportional reversal valve G5 is connected by electromagnetic relief valve 7 with fuel tank.
The aperture of solenoid-operated proportional reversal valve G5 is reconciled by reconciling the voltage of solenoid-operated proportional reversal valve G5, to realize system
The adjusting of dynamic speed；By the difference commutation of solenoid-operated proportional reversal valve G5, prevent from being depressured too fast or unexpected boosting to promotion system
It is impacted caused by system, avoids the generation of safety accident.
First accumulator 6.1 passes through the B mouth of first throttle valve 9.1 and solenoid directional control valve G2, solenoid directional control valve G22 respectively
B mouthfuls are connected, and are connected by second throttle 9.2 with the B mouth of the B of solenoid directional control valve G3 mouth, solenoid directional control valve G33.
First accumulator 6.1 is respectively by two groups of solenoid directional control valves to braking 12 fluid infusion of valve group, thus in two stage braking mistake
Second level pressurized oil braking can be selected respectively in journey.
Solenoid directional control valve G1, solenoid directional control valve G2, solenoid directional control valve G22, solenoid directional control valve G3, solenoid directional control valve G33, electricity
Magnetic reversal valve G4, solenoid directional control valve G44, solenoid directional control valve G6, solenoid directional control valve G66, solenoid directional control valve G7, solenoid directional control valve
G77 is equipped with valve position monitoring sensor 10.
The T mouth of solenoid directional control valve G1, the import of the first accumulator 6.1, the second accumulator 6.2, the A of solenoid directional control valve G6
Mouth, 12 oil inlet of damper brake group are equipped with oil pressure sensor 11.
Before normal work, motor 2 starts, solenoid directional control valve G6 power loss, is in right position, solenoid directional control valve G1, electromagnetic switch
Valve G2, solenoid directional control valve G22, solenoid directional control valve G3, solenoid directional control valve G33, solenoid directional control valve G4, solenoid directional control valve G44, electromagnetism
Reversal valve G66, solenoid directional control valve G7, solenoid directional control valve G77 it is electric, be in left position, solenoid-operated proportional reversal valve G5 is in middle position
It is failure to actuate；The pressure oil that variable pump 3 pumps out is adjusted through proportional pressure control valve 4 passes through the first check valve 5.1 and second one-way valve respectively
5.2 is oil-filled to the first accumulator 6.1, the second accumulator 6.2, until the size that oil pressure sensor 11 is set is reached, proportional overflow
Valve 4 opens to the maximum, oil-filled to finish, and system can enter normal work.
When normal work, solenoid directional control valve G1, solenoid directional control valve G2, solenoid directional control valve G22, solenoid directional control valve G3, electromagnetism
Reversal valve G33, solenoid directional control valve G4, solenoid directional control valve G44, solenoid directional control valve G6, solenoid directional control valve G66, solenoid directional control valve G7,
Solenoid directional control valve G77 it is electric, be in left position, solenoid-operated proportional reversal valve G5 is in middle position and is failure to actuate；Proportional pressure control valve 4 gives electricity
Voltage is gradually adjusted to operating voltage, and damper brake group 12 is slowly opened a sluice gate, and oil pressure is gradually increased to operating oil pressure, and system enters normal work
Make.
A kind of mine hoist safety switching brake perseverance deceleration hydraulic system braking method, includes the following steps:
A), when braking under normal operating conditions, proportional pressure control valve 4 is gradually reduced to zero from operating voltage to piezoelectric voltage, oil
Pressure is gradually reduced to residual voltage from operating oil pressure, and damper brake group 12 is gradually closed a floodgate, and full braking state is reached, and elevator stops working；
B), when safety failure occurs for elevator, control motor 2 stops working, and solenoid directional control valve G1 power loss is in right position,
And different location realizes mine hoist safety braking in well according to different hoisting containers, it is specific as follows:
When hoisting container is located at well head, solenoid directional control valve G7 in parallel and solenoid directional control valve G77 immediately power loss commutate to
Right position, the rapid oil return box of the hydraulic oil of damper brake group 12, oil pressure are reduced to rapidly zero, reach full braking state by level-one braking,
Realization is stopped immediately；
When hoisting container is located in well, solenoid directional control valve G6 in parallel and solenoid directional control valve G66 immediately power loss commutate to
Right position, and solenoid directional control valve G7 and solenoid directional control valve G77 in parallel is failure to actuate and maintains left position state, solenoid directional control valve G2, electromagnetism
Reversal valve G22, solenoid directional control valve G3, solenoid directional control valve G33, which are failure to actuate, maintains left position state, the oil pressure of damper brake group 12 immediately from
Operating oil pressure is reduced to the oil pressure of the setting of third pressure reducing valve 8.3；
Meanwhile solenoid directional control valve G4 and solenoid directional control valve G44 power loss are in right position, solenoid-operated proportional reversal valve G5 is constantly left
Right commutation, when solenoid-operated proportional reversal valve G5 is in right position, the second accumulator 6.2 carries out fluid infusion to damper brake group 12, makes up and subtracts
Velocity amplitude is excessive, and when solenoid-operated proportional reversal valve G5 is in left position, the oil liquid of damper brake group 12 passes through 7 withdrawing oil of electromagnetic relief valve
Case increases deceleration value, so that making the oil pressure of damper brake group 12 linearly slowly reduces, hoisting container deceleration is kept to maintain one
In a stable range, until oil pressure is reduced to zero, it is in complete on-position；
C), piezoelectric voltage is given to realize constant deceleration brake by adjusting solenoid-operated proportional reversal valve G5, when deceleration is excessive or mistake
Small when constant deceleration brake being caused to fail, be immediately switched to two stage braking: solenoid directional control valve G4, solenoid directional control valve G44 obtain electric be in
Left position blocks system to carry out constant deceleration brake, while solenoid directional control valve G2, solenoid directional control valve G22 power loss or solenoid directional control valve
G3, solenoid directional control valve G33 power loss are in right position, and the oil pressure of damper brake group 12 is made to be reduced to the setting value or of the first pressure reducing valve 8.1
The setting value of two pressure reducing valves 8.2, while the first accumulator 6.1 passes through first throttle valve 9.1 or second throttle 9.2 to damper brake
12 fluid infusion of group stablize system in a two stage braking oil pressure value, and elevator is in half braking state, and after delay 5 seconds, electromagnetism is changed
It is in right position to valve G7 and solenoid directional control valve G77 power loss, so that the oil pressure of damper brake group 12 is reduced to zero, elevator is braked completely.
Specifically, two stage braking is realized by following two ways in above-mentioned c) step:
The first, when damper brake group 12 oil pressure value be lower than the second pressure reducing valve 8.2 setting value, be higher than the first pressure reducing valve
When 8.1 setting value, solenoid directional control valve G2, solenoid directional control valve G22 power loss execute low oil pressure two stage braking；
Second, when the oil pressure value of damper brake group 12 is higher than the setting value of the second pressure reducing valve 8.2, solenoid directional control valve G3, electricity
Magnetic reversal valve G33 power loss, executes high oil pressure two stage braking.
Claims (8)
1. a kind of mine hoist safety switching brake perseverance deceleration hydraulic system, including fuel tank (1), motor (2), variable pump (3), accumulation of energy
Device, electromagnetic switch valve group and braking valve group, which is characterized in that further include reducer unit, the import of variable pump (3) by strainer with
Fuel tank (1) is connected, and the outlet of variable pump (3) is connected by strainer with the P mouth of solenoid directional control valve (G1), solenoid directional control valve (G1)
T mouthfuls are connected, by second one-way valve (5.2) and the second accumulation of energy with the first accumulator (6.1) respectively by the first check valve (5.1)
Device (6.2) is connected and is connected with the B mouth of solenoid directional control valve (G6)；P mouth, the solenoid directional control valve (G66) of solenoid directional control valve (G6)
P mouth with braking valve group (12) in the first brake valve oil inlet be connected, P mouth, the solenoid directional control valve of solenoid directional control valve (G7)
(G77) P mouth is connected with the second brake valve oil inlet in braking valve group (12)；A mouth, the electromagnetism of solenoid directional control valve (G6) change
To A mouth and the P mouth of solenoid directional control valve (G2) of valve (G66), the P mouth of solenoid directional control valve (G22), solenoid directional control valve (G3) P mouth,
The P mouth of solenoid directional control valve (G33) is connected with the P mouth of solenoid directional control valve (G4)；A mouth, the solenoid directional control valve of solenoid directional control valve (G2)
(G22) it is connected after A mouth is in parallel with the first pressure reducing valve (8.1)；The A of the A mouth of solenoid directional control valve (G3), solenoid directional control valve (G33)
It is connected after mouth is in parallel with the second pressure reducing valve (8.2)；Connect between the P mouth of solenoid directional control valve (G4) and the P mouth of solenoid directional control valve (G33)
Third pressure reducing valve (8.3) in parallel on logical oil circuit；Setting value the setting less than the second pressure reducing valve (8.2) of first pressure reducing valve (8.1)
Definite value, the setting value of the second pressure reducing valve (8.2) are less than the setting value of third pressure reducing valve (8.3).
2. mine hoist safety switching brake perseverance deceleration hydraulic system as described in claim 1, which is characterized in that solenoid directional control valve
(G4) T mouth is connected with the P mouth of solenoid directional control valve (G44), the T mouth and solenoid-operated proportional reversal valve (G5) of solenoid directional control valve (G44)
B mouth be connected, the P mouth of solenoid-operated proportional reversal valve (G5) is connected in parallel on what the second accumulator (6.2) was connected with second one-way valve (5.2)
On oil circuit, the T mouth of solenoid-operated proportional reversal valve (G5) is connected by electromagnetic relief valve 7 with fuel tank.
3. mine hoist safety switching brake perseverance deceleration hydraulic system as claimed in claim 2, which is characterized in that accumulator
(6.1) it is connected respectively by first throttle valve (9.1) with the B mouth of the B mouth of solenoid directional control valve (G2), solenoid directional control valve (G22), is led to
Second throttle (9.2) is crossed to be connected with the B mouth of the B mouth of solenoid directional control valve (G3), solenoid directional control valve (G33).
4. mine hoist safety switching brake perseverance deceleration hydraulic system as claimed in claim 3, which is characterized in that variable pump 3
The oil inlet of parallel connection electromagnetic proportion relief valve 4, solenoid-operated proportional on the oil circuit being connected between outlet and the P mouth of solenoid directional control valve (G1)
The oil outlet of overflow valve 4 is connected by radiator with fuel tank.
5. the mine hoist safety switching brake perseverance deceleration hydraulic system as described in Claims 1-4 any claim, feature
It is, solenoid directional control valve (G1), solenoid directional control valve (G2), solenoid directional control valve (G22), solenoid directional control valve (G3), solenoid directional control valve
(G33), solenoid directional control valve (G4), solenoid directional control valve (G44), solenoid directional control valve (G6), solenoid directional control valve (G66), electromagnetic switch
Valve (G7), solenoid directional control valve (G77) are equipped with valve position monitoring sensor (10).
6. mine hoist safety switching brake perseverance deceleration hydraulic system as claimed in claim 5, which is characterized in that solenoid directional control valve
(G1) T mouth, the import of the first accumulator (6.1), the second accumulator (6.2), the A mouth of solenoid directional control valve (G6), damper brake group
(12) oil inlet is equipped with oil pressure sensor (11).
7. a kind of mine hoist safety switching brake perseverance deceleration hydraulic system braking method, which comprises the steps of:
A), when braking under normal operating conditions, proportional pressure control valve (4) is gradually reduced to zero from operating voltage to piezoelectric voltage, oil pressure
It is gradually reduced to residual voltage from operating oil pressure, damper brake group (12) is gradually closed a floodgate, and reaches full braking state, elevator stops working；
B), when safety failure occurs for elevator, control motor (2) stops working, and solenoid directional control valve (G1) power loss is in right position,
And different location realizes mine hoist safety braking in well according to different hoisting containers, it is specific as follows:
When hoisting container is located at well head, solenoid directional control valve in parallel (G7) and solenoid directional control valve (G77) immediately power loss commutate to
Right position, the rapid oil return box of hydraulic oil of damper brake group (12), oil pressure are reduced to rapidly zero, reach full application of brake shape by level-one braking
State, realization are stopped immediately；
When hoisting container is located in well, solenoid directional control valve in parallel (G6) and solenoid directional control valve (G66) immediately power loss commutate to
Right position, and solenoid directional control valve (G7) and solenoid directional control valve (G77) in parallel is failure to actuate and maintains left position state, solenoid directional control valve
(G2), solenoid directional control valve (G22), solenoid directional control valve (G3), solenoid directional control valve (G33) are failure to actuate and maintain left position state, damper brake
The oil pressure of group (12) is reduced to the oil pressure that third pressure reducing valve (8.3) are set from operating oil pressure immediately；
Meanwhile solenoid directional control valve (G4) and solenoid directional control valve (G44) power loss are in right position, solenoid-operated proportional reversal valve (G5) is continuous
Left and right commutation, when solenoid-operated proportional reversal valve (G5) is in right position, the second accumulator (6.2) is mended to damper brake group (12)
Liquid, makes up that deceleration value is excessive, and when solenoid-operated proportional reversal valve (G5) is in left position, the oil liquid of damper brake group (12) passes through electromagnetism
Overflow valve (7) reflux fuel tank, increases deceleration value, so that making the oil pressure of damper brake group (12) linearly slowly reduces, keeps being promoted
Container deceleration maintains in a stable range, until oil pressure is reduced to zero, is in complete on-position；
C), piezoelectric voltage is given to realize constant deceleration brake by adjusting solenoid-operated proportional reversal valve (G5), when deceleration is excessive or too small
When constant deceleration brake being caused to fail, be immediately switched to two stage braking: solenoid directional control valve (G4), solenoid directional control valve (G44) obtain electric place
In left position, system is blocked to carry out constant deceleration brake, while solenoid directional control valve (G2), solenoid directional control valve (G22) power loss or electromagnetism
Reversal valve (G3), solenoid directional control valve (G33) power loss are in right position, and the oil pressure of damper brake group (12) is made to be reduced to the first pressure reducing valve
(8.1) setting value of setting value or the second pressure reducing valve (8.2), while the first accumulator (6.1) passes through first throttle valve (9.1)
Or second throttle (9.2) stablizes system in a two stage braking oil pressure value, elevator is in damper brake group (12) fluid infusion
Half braking state, after delay 5 seconds, solenoid directional control valve (G7) and solenoid directional control valve (G77) power loss are in right position, make damper brake group
(12) oil pressure is reduced to zero, and elevator is braked completely.
8. mine hoist safety switching brake perseverance deceleration hydraulic system braking method according to claim 7, which is characterized in that
Two stage braking is realized by following two ways in above-mentioned c) step:
The first, when damper brake group (12) oil pressure value be lower than the second pressure reducing valve (8.2) setting value, be higher than the first pressure reducing valve
(8.1) when setting value, solenoid directional control valve (G2), solenoid directional control valve (G22) power loss execute low oil pressure two stage braking；
Second, when the oil pressure value of damper brake group (12) be higher than the second pressure reducing valve (8.2) setting value, solenoid directional control valve (G3),
Solenoid directional control valve (G33) power loss, executes high oil pressure two stage braking.
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910495369.7A CN110219836B (en) | 2019-06-10 | 2019-06-10 | Safety switching braking constant-speed-reduction hydraulic system and braking method for elevator |
| PCT/CN2019/105023 WO2020248406A1 (en) | 2019-06-10 | 2019-09-10 | Constant decelerating hydraulic system for safe shifting braking of hoister and braking method |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910495369.7A CN110219836B (en) | 2019-06-10 | 2019-06-10 | Safety switching braking constant-speed-reduction hydraulic system and braking method for elevator |
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| Publication Number | Publication Date |
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| CN110219836A true CN110219836A (en) | 2019-09-10 |
| CN110219836B CN110219836B (en) | 2023-12-26 |
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| CN201910495369.7A Active CN110219836B (en) | 2019-06-10 | 2019-06-10 | Safety switching braking constant-speed-reduction hydraulic system and braking method for elevator |
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| CN (1) | CN110219836B (en) |
| WO (1) | WO2020248406A1 (en) |
Cited By (1)
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| CN111285281A (en) * | 2020-02-27 | 2020-06-16 | 中国矿业大学 | Method for controlling brake sticking action consistency of multiple sets of brakes of mine hoist |
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| CN112879366B (en) * | 2020-12-31 | 2022-02-15 | 华中科技大学 | Multifunctional full-sea-depth electric control integrated valve set |
| CN112833058B (en) * | 2021-01-21 | 2023-03-31 | 长沙中联重科环境产业有限公司 | Load-sensitive hydraulic system and hedge trimming equipment |
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| Publication number | Publication date |
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| WO2020248406A1 (en) | 2020-12-17 |
| CN110219836B (en) | 2023-12-26 |
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