CN107131162B - A kind of hydraulic control system for the double driving devices at a slow speed of large-sized grinder - Google Patents
A kind of hydraulic control system for the double driving devices at a slow speed of large-sized grinder Download PDFInfo
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- CN107131162B CN107131162B CN201710306555.2A CN201710306555A CN107131162B CN 107131162 B CN107131162 B CN 107131162B CN 201710306555 A CN201710306555 A CN 201710306555A CN 107131162 B CN107131162 B CN 107131162B
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
- F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
- F15B11/042—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the feed line, i.e. "meter in"
- F15B11/0423—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the feed line, i.e. "meter in" by controlling pump output or bypass, other than to maintain constant speed
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B02—CRUSHING, PULVERISING, OR DISINTEGRATING; PREPARATORY TREATMENT OF GRAIN FOR MILLING
- B02C—CRUSHING, PULVERISING, OR DISINTEGRATING IN GENERAL; MILLING GRAIN
- B02C25/00—Control arrangements specially adapted for crushing or disintegrating
-
- 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
- F15B11/161—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
- F15B11/165—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load for adjusting the pump output or bypass in response to demand
-
- 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
-
- 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
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D48/00—External control of clutches
- F16D48/02—Control by fluid pressure
-
- 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
- F15B2211/60—Circuit components or control therefor
- F15B2211/63—Electronic controllers
- F15B2211/6303—Electronic controllers using input signals
- F15B2211/6306—Electronic controllers using input signals representing a pressure
- F15B2211/6313—Electronic controllers using input signals representing a pressure the pressure being a load pressure
-
- 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
- F15B2211/6657—Open loop control, i.e. control without feedback
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
- F15B2211/75—Control of speed of the output member
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D48/00—External control of clutches
- F16D48/02—Control by fluid pressure
- F16D2048/0257—Hydraulic circuit layouts, i.e. details of hydraulic circuit elements or the arrangement thereof
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- Food Science & Technology (AREA)
- Chemical & Material Sciences (AREA)
- Analytical Chemistry (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
A kind of hydraulic control system for the double driving devices at a slow speed of large-sized grinder is related to a kind of hydraulic control system of driving device, including control loop, the control loop includes open circuit and closed circuit；The present invention drives the rotation of grinding machine, completion to drive this own job function at a slow speed by the way that closed circuit is arranged；Open circuit control brake, clutch are set, to realize grinding machine normal operating conditions and the at a slow speed interlocking between driving condition, it is ensured that large-sized grinder is capable of the purpose of safe operation when in inspecting state.
Description
【Technical field】
The present invention relates to a kind of hydraulic control systems of driving device, double at a slow speed for large-sized grinder more particularly, to one kind
The hydraulic control system of driving device.
【Background technology】
Grinding machine is a kind of milling equipment that application is very universal, and general there are two types of working conditions：Normal grinding working condition
And inspecting state, rotating speed is generally 14-30r/min when grinding machine is in grinding working condition, is driven by main motor；When grinding machine is in
Rotating speed requires very low, generally 0.1r/min or so when inspecting state, is driven by driving device at a slow speed, driving device conduct at a slow speed
Its effect of grinding machine important component is not allowed to substitute, installation and maintenance period grinding machine to the security requirement of slow driving device very
Height, all the time, slow driving device are all made of motor driving, referred to as electronic slow drive, with the increase of grinding machine specification, the installation of grinding machine
Power is also increasing, due to Gear Processing and carrying, will become development trend using the grinding machine of twin-engined drives, at this
Since load increases in the case of kind, in addition in order to reduce the limitation of the gear-driven unbalance loading of size and the design of retarder speed ratio,
It cannot have been met the requirements using single slow driving device, the configuration application of double slow driving devices will become mainstay scheme, from
Synchronism, the reliability of braking that space, two slow driving devices drive, and big pinion gear and main reducing gear carrying and speed
Than optimization etc. analysis, not only control that relatively difficult to achieve, cost is higher using double electronic slow driving devices, and safety, can
It is not high by property, therefore do not used by home and abroad user.
【Invention content】
In order to overcome the shortcomings of in background technology, the present invention discloses a kind of liquid for the double driving devices at a slow speed of large-sized grinder
Pressure control system drives the rotation of grinding machine, completion to drive this own job function at a slow speed by the way that closed circuit is arranged；Open type is arranged to return
Road control brake, clutch, to realize grinding machine normal operating conditions and the at a slow speed interlocking between driving condition, it is ensured that large-scale
Grinding machine is capable of the purpose of safe operation when in inspecting state.
In order to realize that the goal of the invention, the present invention adopt the following technical scheme that：
A kind of hydraulic control system for the double driving devices at a slow speed of large-sized grinder, including fuel tank 1, further include controlling back
Road, the control loop include open circuit and closed circuit；
The closed circuit includes transfer tube, slippage pump, proportion electro-magnet and stroking mechanism, safety valve A, safety valve B, mends
Oily check valve A, repairing check valve B, repairing check valve C, repairing check valve D, repairing check valve E, repairing check valve F, auxiliary are overflow
Flow valve, outlet filter, heat exchange valve, heat exchange overflow valve, cooler, return filter, oil absorption filter, pressure sensor A, pressure
Force snesor B, pressure sensor C, pressure sensor D, balanced valve A, balanced valve B, hydraulic motor A, hydraulic motor B, brake
A, the T mouths of brake B, retarder A and retarder B, the proportion electro-magnet and stroking mechanism, the A mouths of oil absorption filter, oil return
The B mouths of filter, the T mouths of hydraulic motor A, hydraulic motor B T mouths be connected respectively with fuel tank with the T of auxiliary overflow valve mouths, institute
The S mouths for stating slippage pump are connected with the B of oil absorption filter mouths, the A mouths of the transfer tube, the P mouths of safety valve A, repairing check valve A
B mouths, the A mouths of heat exchange valve, the A mouths of balanced valve A be connected with the A of balanced valve B mouths, the B mouths of the transfer tube, the P of safety valve B
Mouth, the B mouths of repairing check valve B, the B mouths of heat exchange valve, balanced valve A A1 mouths be connected with the A1 of balanced valve B mouths, the slippage pump
P mouths be connected with the A of outlet filter mouths, the B mouths of the outlet filter and the P of proportion electro-magnet and stroking mechanism mouths,
The A mouths of repairing check valve A, the A mouths of repairing check valve B, the A mouths of repairing check valve C, the A mouths of repairing check valve D, repairing are unidirectional
The A mouths of valve E, the A mouths of repairing check valve F, the T mouths of safety valve A, safety valve B T mouths be connected with the P of auxiliary overflow valve mouths, institute
The P mouths for stating heat exchange valve are connected with the P mouths of heat exchange overflow valve, and the T mouths of the heat exchange overflow valve are connected with the A of cooler mouths,
The B mouths of the cooler are connected with the A of return filter mouths, the B mouths of the repairing check valve C, the B mouths of hydraulic motor A, pressure
The oil inlet of force snesor A is connected with the B1 of balanced valve A mouths, the B mouths of the repairing check valve D, the B mouths of hydraulic motor B, pressure
The oil inlet of force snesor B is connected with the B1 of balanced valve B mouths, the B mouths of the repairing check valve E, the A mouths of hydraulic motor A, pressure
The oil inlet of force snesor C is connected with the B of balanced valve A mouths, the B mouths of the repairing check valve F, the A mouths of hydraulic motor B, pressure
The oil inlet of force snesor D is connected with the B of balanced valve B mouths；
The open circuit includes control pump, electromagnetic relief valve, Solenoid ball valve A, Solenoid ball valve B, Solenoid ball valve C, electromagnetism
Reversal valve A, solenoid directional control valve B, hydraulic control one-way valve A, hydraulic control one-way valve B, Double throttle check valve A, Double throttle check valve B, shunting
Motor A, diffluence motor B, clutch driving hydraulic cylinder A, clutch driving hydraulic cylinder B, clutch driving hydraulic cylinder C, clutch
Driving hydraulic cylinder D, travel switch A, travel switch B, travel switch C, travel switch D, pressure switch A, pressure switch B, clutch
Device A and clutch B；It is described control pump S mouths, the T mouths of Solenoid ball valve C, the T mouths of electromagnetic relief valve, solenoid directional control valve A T mouths,
The T mouths of solenoid directional control valve B, the T mouths of diffluence motor A, diffluence motor B T mouths be connected respectively with fuel tank, it is described control pump P
P mouths, the Solenoid ball valve A of mouth, the P mouths of solenoid directional control valve A, the P mouths of solenoid directional control valve B, the P mouths of Solenoid ball valve C, electromagnetic relief valve
P1 mouths be connected with the P3 of Solenoid ball valve A mouths, the A mouths of the solenoid directional control valve A are connected with the A1 of hydraulic control one-way valve A mouths,
The B mouths of the solenoid directional control valve A are connected with the A of hydraulic control one-way valve A mouths, the A mouths and hydraulic control one-way valve of the solenoid directional control valve B
The A1 mouths of B are connected, and the B mouths of the solenoid directional control valve B are connected with the A of hydraulic control one-way valve B mouths, the B of the hydraulic control one-way valve A
Mouth is connected with the A of Double throttle check valve A mouths, and the B1 mouths of the hydraulic control one-way valve A are connected with the A1 of Double throttle check valve A mouths, institute
The B mouths for stating hydraulic control one-way valve B are connected with the A of Double throttle check valve B mouths, the B1 mouths of the hydraulic control one-way valve B and double one-way throttles
The A1 mouths of valve B are connected, and the B mouths of the Double throttle check valve A are connected with the P of diffluence motor A mouths, the B1 of Double throttle check valve A
Mouth is connected with A mouthfuls of the rod chamber of A mouthfuls of the rod chamber of clutch driving hydraulic cylinder A, clutch driving hydraulic cylinder B, the shunting
The P1 mouths of motor A are connected with B1 mouthfuls of the rodless cavity of clutch driving hydraulic cylinder A, and the P2 mouths and clutch of diffluence motor A drive
B2 mouthfuls of the rodless cavity of hydraulic cylinder B is connected, and the B mouths of the Double throttle check valve B are connected with the P of diffluence motor B mouths, double unidirectional
The B1 mouths of throttle valve B are connected with A mouthfuls of the rod chamber of A mouthfuls of the rod chamber of clutch driving hydraulic cylinder C, clutch driving hydraulic cylinder D
Connect, the P1 mouths of the diffluence motor B are connected with B1 mouthfuls of the rodless cavity of clutch driving hydraulic cylinder C, the P2 mouths of diffluence motor B and
B2 mouthfuls of the rodless cavity of clutch driving hydraulic cylinder D is connected, the A mouths of the Solenoid ball valve C and P1 mouths, the electromagnetism of Solenoid ball valve B
The P3 mouths of ball valve B are connected, the P2 mouths of the Solenoid ball valve A, the P2 mouths of Solenoid ball valve B, the oil inlet of pressure switch A and braking
The oil inlet of device B is connected, the P4 mouths of the Solenoid ball valve A, the P4 mouths of Solenoid ball valve B, the oil inlet of pressure switch B and braking
The oil inlet of device A is connected, and the left and right two on clutch A straight-line trajectories is arranged in the travel switch A and travel switch B
The limit of left and right two that a extreme position, the travel switch C and travel switch D are arranged on clutch B straight-line trajectories
Position；
The hydraulic control system for the double driving devices at a slow speed of large-sized grinder, the drive of the transfer tube, control pump
Dynamic motor, the solenoid valve of proportion electro-magnet and stroking mechanism, pressure sensor A, pressure sensor B, pressure sensor C, pressure
Sensor D, electromagnetic relief valve, Solenoid ball valve A, Solenoid ball valve B, Solenoid ball valve C, solenoid directional control valve A, solenoid directional control valve B, stroke
Switch A, travel switch B, travel switch C, travel switch D, pressure switch A, pressure switch B turn together with for measuring grinding mill barrel
The photoelectric encoder of speed is respectively connected to controller.
Due to using technical solution as described above, the present invention to have the advantages that：
Hydraulic control system of the present invention for the double driving devices at a slow speed of large-sized grinder, including closed circuit
It is not only mutual indepedent but also interrelated with open circuit, it is used to drive the rotation of grinding machine, completion to drive at a slow speed by the way that closed circuit is arranged
Move this own job function；Open circuit is set for control brake, clutch, to realize grinding machine normal operating conditions with it is slow
Interlocking between fast driving condition, it is ensured that large-sized grinder is capable of the purpose of safe operation when in inspecting state；The present invention is set
Count it is reasonable, energy-saving significantly, using effect is good.
【Description of the drawings】
Fig. 1 is the structural diagram of the present invention；
In figure：1, fuel tank；2, transfer tube；3, slippage pump；4, proportion electro-magnet and stroking mechanism；5.1, safety valve A；5.2、
Safety valve B；6.1, repairing check valve A；6.2, repairing check valve B；6.3, repairing check valve C；6.4, repairing check valve D；6.5、
Repairing check valve E；6.6, repairing check valve F；7, auxiliary overflow valve；8, outlet filter；9, heat exchange valve；10, exchange heat overflow valve；
11, cooler；12, return filter；13, oil absorption filter；14.1, pressure sensor A；14.2, pressure sensor B；14.3、
Pressure sensor C；14.4, pressure sensor D；15.1, balanced valve A；15.2, balanced valve B；16.1, hydraulic motor A；16.2, liquid
Pressure motor B；17.1, brake A；17.2, brake B；18.1, retarder A；18.2, retarder B；19, control pump；20, electromagnetism
Overflow valve；21, Solenoid ball valve A；22, Solenoid ball valve B；23, Solenoid ball valve C；24.1, solenoid directional control valve A；24.2, electromagnetic switch
Valve B；25.1, hydraulic control one-way valve A；25.2, hydraulic control one-way valve B；26.1, Double throttle check valve A；26.2, Double throttle check valve B；
27.1, diffluence motor A；27.2, diffluence motor B；28.1, clutch driving hydraulic cylinder A；28.2, clutch driving hydraulic cylinder B；
28.3, clutch driving hydraulic cylinder C；28.4, clutch driving hydraulic cylinder D；29.1, travel switch A；29.2, travel switch B；
29.3, travel switch C；29.4, travel switch D；30.1, pressure switch A；30.2, pressure switch B；31.1, clutch A；
31.2, clutch B.
【Specific implementation mode】
The present invention can be explained in more detail by the following examples, the invention is not limited in the following examples,
The open purpose of the present invention is intended to all changes and improvements in the protection scope of the invention.
The hydraulic control system for the double driving devices at a slow speed of large-sized grinder in conjunction with described in attached drawing 1, including fuel tank 1, also
Including control loop, the control loop includes open circuit and closed circuit；The closed circuit includes transfer tube 2, repairing
Pump 3, proportion electro-magnet and stroking mechanism 4, safety valve A5.1, safety valve B5.2, repairing check valve A6.1, repairing check valve
B6.2, repairing check valve C6.3, repairing check valve D6.4, repairing check valve E6.5, repairing check valve F6.6, auxiliary overflow valve 7,
Outlet filter 8, heat exchange valve 9, heat exchange overflow valve 10, cooler 11, return filter 12, oil absorption filter 13, pressure sensing
Device A14.1, pressure sensor B14.2, pressure sensor C14.3, pressure sensor D14.4, balanced valve A15.1, balanced valve
B15.2, hydraulic motor A16.1, hydraulic motor B16.2, brake A17.1, brake B17.2, retarder A18.1 and retarder
B mouths, the hydraulic pressure of the T mouths of B18.2, the proportion electro-magnet and stroking mechanism 4, the A mouths of oil absorption filter 13, return filter 12
The T mouths of motor A16.1, the T mouths of hydraulic motor B16.2 are connected with fuel tank 1 respectively with the T of auxiliary overflow valve 7 mouths, the repairing
The S mouths of pump 3 are connected with the B of oil absorption filter 13 mouths, the A mouths of the transfer tube 2, P mouths, the repairing check valve of safety valve A5.1
The B mouths of A6.1, the A mouths of heat exchange valve 9, balanced valve A15.1 A mouths be connected with the A of balanced valve B15.2 mouths, the transfer tube 2
B mouthfuls, the P mouths of safety valve B5.2, the B mouths of repairing check valve B6.2, the B mouths of heat exchange valve 9, the A1 mouths of balanced valve A15.1 and balance
The A1 mouths of valve B15.2 are connected, and the P mouths of the slippage pump 3 are connected with the A of outlet filter 8 mouths, the outlet filter 8
B mouths and the P of proportion electro-magnet and stroking mechanism 4 mouths, the A mouths of repairing check valve A6.1, repairing check valve B6.2 A mouths, mend
The A of the A mouths of oily check valve C6.3, the A mouths of repairing check valve D6.4, the A mouths of repairing check valve E6.5, repairing check valve F6.6
Mouth, the T mouths of safety valve A5.1, safety valve B5.2 T mouths be connected with the P of auxiliary overflow valve 7 mouths, the P mouths of the heat exchange valve 9 and
The P mouths of heat exchange overflow valve 10 are connected, and the T mouths of the heat exchange overflow valve 10 are connected with the A of cooler 11 mouths, the cooler
11 B mouths are connected with the A of return filter 12 mouths, the B mouths of the repairing check valve C6.3, the B mouths of hydraulic motor A16.1,
The oil inlet of pressure sensor A14.1 is connected with the B1 of balanced valve A15.1 mouths, B mouths, the hydraulic pressure of the repairing check valve D6.4
The B mouths of motor B16.2, the oil inlet of pressure sensor B14.2 are connected with the B1 of balanced valve B15.2 mouths, and the repairing is unidirectional
The B mouths of valve E6.5, the A mouths of hydraulic motor A16.1, pressure sensor C14.3 oil inlet be connected with the B of balanced valve A15.1 mouths
Connect, the B mouths of the repairing check valve F6.6, the A mouths of hydraulic motor B16.2, pressure sensor D14.4 oil inlet and balanced valve
The B mouths of B15.2 are connected；The open circuit includes control pump 19, electromagnetic relief valve 20, Solenoid ball valve A21, Solenoid ball valve
B22, Solenoid ball valve C23, solenoid directional control valve A24.1, solenoid directional control valve B24.2, hydraulic control one-way valve A25.1, hydraulic control one-way valve
B25.2, Double throttle check valve A26.1, Double throttle check valve B26.2, diffluence motor A27.1, diffluence motor B27.2, clutch
Driving hydraulic cylinder A28.1, clutch driving hydraulic cylinder B28.2, clutch driving hydraulic cylinder C28.3, clutch driving hydraulic cylinder
D28.4, travel switch A29.1, travel switch B29.2, travel switch C29.3, travel switch D29.4, pressure switch A30.1,
Pressure switch B30.2, clutch A31.1 and clutch B31.2；The S mouths of the control pump 19, T mouths, the electricity of Solenoid ball valve C23
The T mouths of magnetic overflow valve 20, the T mouths of solenoid directional control valve A24.1, the T mouths of solenoid directional control valve B24.2, diffluence motor A27.1 T mouths,
The T mouths of diffluence motor B27.2 are also connected with fuel tank 1 respectively, it is described control pump 19 P mouths, solenoid directional control valve A24.1 P mouths,
The P1 mouths and electricity of the P mouths of solenoid directional control valve B24.2, the P mouths of Solenoid ball valve C23, the P mouths of electromagnetic relief valve 20, Solenoid ball valve A21
The P3 mouths of magnetic ball valve A21 are connected, and the A mouths of the solenoid directional control valve A24.1 are connected with the A1 of hydraulic control one-way valve A25.1 mouths,
The B mouths of the solenoid directional control valve A24.1 are connected with the A of hydraulic control one-way valve A25.1 mouths, the A mouths of the solenoid directional control valve B24.2
It is connected with the A1 of hydraulic control one-way valve B25.2 mouths, the B mouths of the solenoid directional control valve B24.2 and the A mouths of hydraulic control one-way valve B25.2
It is connected, the B mouths of the hydraulic control one-way valve A25.1 are connected with the A of Double throttle check valve A26.1 mouths, the hydraulic control one-way valve
The B1 mouths of A25.1 are connected with the A1 of Double throttle check valve A26.1 mouths, the B mouths of the hydraulic control one-way valve B25.2 and double one-way throttles
The A mouths of valve B26.2 are connected, and the B1 mouths of the hydraulic control one-way valve B25.2 are connected with the A1 of Double throttle check valve B26.2 mouths, described
The B mouths of Double throttle check valve A26.1 are connected with the P of diffluence motor A27.1 mouths, the B1 mouths of Double throttle check valve A26.1 with from
A mouthfuls of the rod chamber of clutch driving hydraulic cylinder A28.1, A mouthfuls of the rod chamber of clutch driving hydraulic cylinder B28.2 are connected, described point
The P1 mouths of stream motor A27.1 are connected with B1 mouthfuls of the rodless cavity of clutch driving hydraulic cylinder A28.1, the P2 of diffluence motor A27.1
Mouth is connected with B2 mouthfuls of the rodless cavity of clutch driving hydraulic cylinder B28.2, the B mouths of the Double throttle check valve B26.2 and shunting
The P mouths of motor B27.2 are connected, the rod chamber A of the B1 mouths and clutch driving hydraulic cylinder C28.3 of Double throttle check valve B26.2
Mouthful, A mouthful of the rod chamber of clutch driving hydraulic cylinder D28.4 be connected, P2 mouths and the clutch driving of the diffluence motor B27.2
B1 mouthfuls of the rodless cavity of hydraulic cylinder C28.3 is connected, the nothing of the P1 mouths and clutch driving hydraulic cylinder D28.4 of diffluence motor B27.2
B2 mouthfuls of rod cavity is connected, and the A mouths of the Solenoid ball valve C23 are connected with the P3 mouths of the P1 of Solenoid ball valve B22 mouths, Solenoid ball valve B22
Connect, the P2 mouths of the Solenoid ball valve A21, the P2 mouths of Solenoid ball valve B22, pressure switch A30.1 oil inlet and brake B17.2
Oil inlet be connected, the P4 mouths of the Solenoid ball valve A21, the P4 mouths of Solenoid ball valve B22, pressure switch B30.2 oil inlet
It is connected with the oil inlet of brake A17.1, the travel switch A29.1 and travel switch B29.2 are arranged in clutch A31.1
The extreme position of left and right two on straight-line trajectory, the travel switch C29.3 and travel switch D29.4 are arranged in clutch
The extreme position of left and right two on B31.2 straight-line trajectories；The transfer tube 2, the driving motor of control pump 19, ratio electromagnetism
The solenoid valve of iron and stroking mechanism 4, pressure sensor A14.1, pressure sensor B14.2, pressure sensor C14.3, pressure pass
Sensor D14.4, electromagnetic relief valve 20, Solenoid ball valve A21, Solenoid ball valve B22, Solenoid ball valve C23, solenoid directional control valve A24.1, electricity
Magnetic reversal valve B24.2, travel switch A29.1, travel switch B29.2, travel switch C29.3, travel switch D29.4, pressure are opened
Close A30.1, pressure switch B30.2 is respectively connected to controller together with the photoelectric encoder for measuring grinding mill barrel rotating speed.
Implement the hydraulic control system of the present invention for the double driving devices at a slow speed of large-sized grinder, has following special
Point：
" the invariable power adjusting " 1. of hydraulic system closed circuit
The realization of grinding machine driven at a slow speed is completed by the closed circuit in this system, and transfer tube 2 is with constant in closed circuit
Rotating speed rotates, and hydraulic motor A16.1, hydraulic motor B16.2 are controlled by changing the size and Orientation of discharge capacity of transfer tube 2
Rotating speed and direction of rotation；And " invariable power " regulative mode is used, the discharge capacity of transfer tube 2 is higher, and slow drive speed is faster；And system
Operating pressure is bigger, and slow driving device output torque is bigger；Under certain rotating speed, the discharge capacity of transfer tube 2 and the product of operating pressure
For the power of motor of transfer tube 2, so in the case where the power of motor of transfer tube 2 is certain, controller is returned by detecting enclosed
What pressure sensor A14.1, pressure sensor B14.2, pressure sensor C14.3 and pressure sensor D14.4 in road were fed back
Signal, can reduce the output flow of transfer tube 2 according to actual condition, that is, reduce rotating speed of the grinding machine slowly under drive state, for into
One step improves the driving capability of slow driving device, to improve the working range and applicable ability that hydraulic pressure drives slowly；
" the electric proportion adjustment " 2. of hydraulic system closed circuit
The variable regulative mode of transfer tube 2 is electric proportional control, and the flow of output and direction are directly proportional to control signal,
By inputing to the change of the size and Orientation of electric current on proportion electro-magnet and stroking mechanism 4, and in the work of 3 pressure oil of slippage pump
It can change the size and Orientation of 2 output flow of transfer tube with lower, and then make the flow of transfer tube 2 is proportional to change,
Make driven hydraulic motor A16.1, the speed of hydraulic motor B16.2 both directions and acceleration, deceleration can be smart
Really control；
Specific work process is as follows：When controller in 2 stroking mechanism of transfer tube proportion electro-magnet and stroking mechanism 4 just
When signal, the electromagnet b electrifications in proportion electro-magnet and stroking mechanism 4 control oil and variable piston are pushed to move right, transfer tube
2 A mouth pressure oil outputs pass through the A mouths that pressure oil is sent into hydraulic motor A16.1 by balanced valve A15.1, work as brake all the way
In when opening a sluice gate state, hydraulic motor A16.1 driving retarders A18.1 rotates A17.1；Same another way through balanced valve B15.2,
Pressure oil is sent into the A mouths of hydraulic motor B16.2, when brake B17.2, which is in, opens a sluice gate state, hydraulic motor B16.2 drivings
Retarder B18.2 rotations.When clutch A31.1, clutch B31.2 " close " simultaneously, retarder A18.1, retarder B18.2
It is common that grinding machine is driven to rotate in the forward direction；
It the hydraulic oil that is flowed out from the B mouths of hydraulic motor A16.1 through balanced valve A15.1 and is passed through from the B mouths of hydraulic motor B16.2
The hydraulic oil of balanced valve B15.2 outflows returns to the B mouths of transfer tube 2 jointly；
When controller is to 4 negative signal of proportion electro-magnet and stroking mechanism in 2 stroking mechanism of transfer tube, proportion electro-magnet
And 4 electromagnet a electrifications of stroking mechanism, it controls oil and variable piston is pushed to be moved to the left, the B mouths output of transfer tube 2, to drive liquid
Pressure motor A16.1, hydraulic motor B16.2 reversions, grinding machine also invert therewith, and oil circuit is similar when being rotated forward with grinding machine, and so it will not be repeated；
The hydraulic oil flowed out at this time from the A mouths of hydraulic motor A16.1 through balanced valve A15.1 is with the A mouths from hydraulic motor B16.2 through balance
The hydraulic oil of valve B15.2 outflows returns to the A mouths of transfer tube 2 jointly；
It should be further noted that:When clutch A31.1 " closing ", clutch B31.2 " disengagement ", grinding machine can only be by
Retarder A18.1 drivings；Otherwise when clutch B31.2 " closing ", clutch A31.1 " disengagement ", grinding machine can only be by retarder
B18.2 drives；This function can be such that grinding machine by two slow driving devices while can drives, and can also be driven by any of which one is slow
Device is operated alone, and facilitates two clutches " to tooth ", unbalance loading operating mode occurs in gear, this function is largely effective；
Big due to loading for large-sized mining grinding mill, rotary inertia is big, and hydraulic motor A16.1 is furnished with balanced valve in this system
A15.1, no matter hydraulic motor A16.1 is in main story or reversion, and oil inlet and the oil extraction of hydraulic motor A16.1 can pass through balanced valve
The I/O traffic of A15.1, hydraulic motor A16.1 can be balanced valve A15.1 and effectively carry out throttling control for brake, avoid
Under Exceed load operating mode, hydraulic motor A16.1, the danger damaged due to for shortage of oil, and grinding machine choosing turns also more may be used
It leans on, while hydraulic motor A16.1 output shafts are provided with brake A17.1, brake A17.1 can be protected under operating mode under overload
Hydraulic motor A16.1 is protected, and the requirement to safety arrestment when grinding machine maintenance can be met；
It is furnished with balanced valve B15.2 on the inlet and outlet of fuel channel of hydraulic motor B16.2, hydraulic motor B16.2 output shafts are provided with system
Dynamic device B17.2；Balanced valve B15.2 is identical as balanced valve A15.1, and brake B17.2 is identical as brake A17.1, therefore no longer superfluous
It states.
" the electro-hydraulic closed-loop control " 3. of hydraulic system closed circuit
Said from grinding process angle, when grinding machine is shut down it is small more than 4 when more than when, the material in grinding mill barrel may freeze
Knot, grinding machine should be at driving working condition slowly at this time, and be in equilibrium state as early as possible as far as possible；For this operating mode, this hydraulic pressure system
System can have an important control function by " electro-hydraulic closed-loop control " -- and " anti-material freezes "；Specifically：In grinding machine
The load of inner barrel rushes down fall before, the operating pressure of transfer tube 2 can rise always, if system pressure is got on certain angle
Come it is higher, then grind in material it is uneven, be judged as that material freezes；Slow drive must rotate and reverse at this time, make grinding machine towards load
Direction, which rotates, ensures that two lateral load of grinding machine is roughly equal i.e. in equilibrium state；
In hydraulic system closed circuit:The A mouths of hydraulic motor A16.1 are equipped with pressure for C14.3, B mouthfuls equipped with pressure sensor
The A mouths of sensors A 14.1, hydraulic motor B16.2 are equipped with pressure sensor B14.2 for D14.4, B mouthfuls equipped with pressure sensor, in addition
Photoelectric encoder for detecting grinding mill barrel rotating speed.Controller is effectively controlled by detecting the feedback signals of these electric elements
The positive and negative and size of the input signal of proportion electro-magnet and stroking mechanism 4, makes the side of 2 output flow of transfer tube in transfer tube 2 processed
To being automatically adjusted with size, to make grinding machine automatically realize main story, reversion, realize that the material freezed in mill loosens；Work as control
Device detects the pressure sensor C14.3 being connected with the A of hydraulic motor A16.1 mouths and is connected with the B of hydraulic motor A16.1 mouths
When the feedback signal of pressure sensor A14.1 is of substantially equal and controller detects and is connected with the A of hydraulic motor B16.2 mouths
Pressure sensor D14.4 and the pressure sensor B14.2 being connected with the B of hydraulic motor B16.2 mouths the basic phase of feedback signal
Material has basically reached equilibrium state in then being ground whens equal；
The closed circuit synthesis " electric proportion adjustment " of this hydraulic system, " invariable power adjusting ", " electro-hydraulic closed-loop control " are realized
The slow torque and automatic matching rotating speed for driving the slow driving device output in drift angle, hydraulic pressure that grinding machine rotates under operating mode, can not only improve
Automation, intelligent level and the security reliability that can undoubtedly greatly improve mill running of mill driving system；
4. the open circuit in hydraulic system is used to control brake A17.1, the hydraulic motor on hydraulic motor A16.1
The engagement and disengagement of brake B17.2 and clutch A31.1, clutch B31.2 on B16.2；
In Double-hydraulic at a slow speed driving device, it be furnished with brake A17.1, hydraulic pressure horse on the output shaft of hydraulic motor A16.1
It is furnished with brake B17.2 on up to the output shaft of B16.2；Control pump 19 can effectively control brake A17.1, brake B17.2, make
It obtains grinding machine and is stably held in non-equilibrium site, to keep operator more safe when replacing liner plate；And in brake
The oil passage of A17.1 is furnished with pressure switch B30.2, and the oil passage of brake B17.2 is furnished with pressure switch A30.1, works as controller
When detecting that pressure switch sends out signal, illustrate to be opened brake by pressure oil, allows hydraulic motor to rotate at this time, if not having
Detect that the signal that pressure switch is sent out, controller will not then be such that hydraulic motor rotates, according to logical action relationship shown in following table,
Can not only may be implemented brake A17.1, brake B17.2 single movement but also can realize brake A17.1, brake
B17.2 is acted simultaneously, so as to realize two driving device single action or linkage actions at a slow speed；
Two at a slow speed the clutch A31.1 of driving device, the opening and closing movement of clutch B31.2 also completed by open circuit,
According to logical action relationship shown in following table, clutch A31.1, the single movement of clutch B31.2 but also energy can not only may be implemented
Realize the linkage action of clutch A31.1, clutch B31.2；
Open circuit solenoid valve action logic table
The specific work process that can be seen that from above data is：When being intended to realize " brake A17.1 is opened a sluice gate ", electromagnet
SV1, SV7, SV8 are charged, remaining electromagnet is not charged, start the motor of control pump 19, control pump 19 directly from fuel tank oil suction, by
It is charged in electromagnet SV1, the P mouths of control pump 19 are not connected with the T of electromagnetic relief valve 20 mouths, to make system set up pressure；
Electromagnet SV7 electrifications, the P3 mouths of Solenoid ball valve A21 are connected with the P4 mouths of Solenoid ball valve A21 so that the P mouths of control pump 19 are through electricity
The P3 mouths of magnetic ball valve A21, the P4 mouths of Solenoid ball valve A21 are output to the oil inlet of brake A17.1, thus by brake A17.1
It opens.Electromagnet SV8 is used for the oil return line of control brake A17.1, when it is charged, the P3 mouths and electromagnetism of Solenoid ball valve B22
The P4 mouths of ball valve B22 are not communicated with, so as to keep the input pressure of brake A17.1 constant, to maintain brake A17.1's
Open a sluice gate state；
When pressure switch B30.2 (PS1 in the logical action table of the immediate boiling circuit) detections in brake A17.1 oil passage
When to pressure and acting, controller can be sent a signal to, can realize in logical action table " allows hydraulic motor A16.1 to revolve at this time
Turn " functional status.
Remaining logical action describes similar, and so it will not be repeated.
Part not in the detailed description of the invention is the prior art.
Claims (2)
1. a kind of hydraulic control system for the double driving devices at a slow speed of large-sized grinder, including fuel tank（1）, it is characterized in that：Also wrap
Control loop is included, the control loop includes open circuit and closed circuit；
The closed circuit includes transfer tube（2）, slippage pump（3）, proportion electro-magnet and stroking mechanism（4）, safety valve A（5.1）、
Safety valve B（5.2）, repairing check valve A（6.1）, repairing check valve B（6.2）, repairing check valve C（6.3）, repairing check valve D
（6.4）, repairing check valve E（6.5）, repairing check valve F（6.6）, auxiliary overflow valve（7）, outlet filter（8）, heat exchange valve
（9）, heat exchange overflow valve（10）, cooler（11）, return filter（12）, oil absorption filter（13）, pressure sensor A
（14.1）, pressure sensor B（14.2）, pressure sensor C（14.3）, pressure sensor D（14.4）, balanced valve A（15.1）, it is flat
Weigh valve B（15.2）, hydraulic motor A（16.1）, hydraulic motor B（16.2）, brake A（17.1）, brake B（17.2）, slow down
Device A（18.1）With retarder B（18.2）, the proportion electro-magnet and stroking mechanism（4）T mouths, oil absorption filter（13）A
Mouth, return filter（12）B mouths, hydraulic motor A（16.1）T mouths, hydraulic motor B（16.2）T mouths and auxiliary overflow valve
（7）T mouths respectively and fuel tank（1）It is connected, the slippage pump（3）S mouths and oil absorption filter（13）B mouths be connected, institute
State transfer tube（2）A mouths, safety valve A（5.1）P mouths, repairing check valve A（6.1）B mouths, heat exchange valve（9）A mouths, balance
Valve A（15.1）A mouths and balanced valve B（15.2）A mouths be connected, the transfer tube（2）B mouths, safety valve B（5.2）P
Mouth, repairing check valve B（6.2）B mouths, heat exchange valve（9）B mouths, balanced valve A（15.1）A1 mouths and balanced valve B（15.2）'s
A1 mouthfuls are connected, the slippage pump（3）P mouths and outlet filter（8）A mouths be connected, the outlet filter（8）B
Mouth and proportion electro-magnet and stroking mechanism（4）P mouths, repairing check valve A（6.1）A mouths, repairing check valve B（6.2）A mouths,
Repairing check valve C（6.3）A mouths, repairing check valve D（6.4）A mouths, repairing check valve E（6.5）A mouths, repairing check valve F
（6.6）A mouths, safety valve A（5.1）T mouths, safety valve B（5.2）T mouths and auxiliary overflow valve（7）P mouths be connected, it is described
Heat exchange valve（9）P mouths and heat exchange overflow valve（10）P mouths be connected, the heat exchange overflow valve（10）T mouths and cooler（11）
A mouths be connected, the cooler（11）B mouths and return filter（12）A mouths be connected, the repairing check valve C
（6.3）B mouths, hydraulic motor A（16.1）B mouths, pressure sensor A（14.1）Oil inlet and balanced valve A（15.1）B1
Mouth is connected, the repairing check valve D（6.4）B mouths, hydraulic motor B（16.2）B mouths, pressure sensor B（14.2）Into
Hydraulic fluid port and balanced valve B（15.2）B1 mouths be connected, the repairing check valve E（6.5）B mouths, hydraulic motor A（16.1）A
Mouth, pressure sensor C（14.3）Oil inlet and balanced valve A（15.1）B mouths be connected, the repairing check valve F（6.6）'s
B mouthfuls, hydraulic motor B（16.2）A mouths, pressure sensor D（14.4）Oil inlet and balanced valve B（15.2）B mouths be connected；
The open circuit includes that control pumps（19）, electromagnetic relief valve（20）, Solenoid ball valve A（21）, Solenoid ball valve B（22）, electricity
Magnetic ball valve C（23）, solenoid directional control valve A（24.1）, solenoid directional control valve B（24.2）, hydraulic control one-way valve A（25.1）, hydraulic control one-way valve B
（25.2）, Double throttle check valve A（26.1）, Double throttle check valve B（26.2）, diffluence motor A（27.1）, diffluence motor B
（27.2）, clutch driving hydraulic cylinder A（28.1）, clutch driving hydraulic cylinder B（28.2）, clutch driving hydraulic cylinder C
（28.3）, clutch driving hydraulic cylinder D（28.4）, travel switch A（29.1）, travel switch B（29.2）, travel switch C
（29.3）, travel switch D（29.4）, pressure switch A（30.1）, pressure switch B（30.2）, clutch A（31.1）With clutch B
（31.2）；The control pump（19）S mouths, Solenoid ball valve C（23）T mouths, electromagnetic relief valve（20）T mouths, solenoid directional control valve A
（24.1）T mouths, solenoid directional control valve B（24.2）T mouths, diffluence motor A（27.1）T mouths, diffluence motor B（27.2）T mouths
Respectively and fuel tank（1）It is connected, the control pump（19）P mouths, solenoid directional control valve A（24.1）P mouths, solenoid directional control valve B
（24.2）P mouths, Solenoid ball valve C（23）P mouths, electromagnetic relief valve（20）P mouths, Solenoid ball valve A（21）P1 mouths and electromagnetism
Ball valve A（21）P3 mouths be connected, the solenoid directional control valve A（24.1）A mouths and hydraulic control one-way valve A（25.1）A1 mouths be connected
It connects, the solenoid directional control valve A（24.1）B mouths and hydraulic control one-way valve A（25.1）A mouths be connected, the solenoid directional control valve B
（24.2）A mouths and hydraulic control one-way valve B（25.2）A1 mouths be connected, the solenoid directional control valve B（24.2）B mouths and hydraulic control list
To valve B（25.2）A mouths be connected, the hydraulic control one-way valve A（25.1）B mouths and Double throttle check valve A（26.1）A mouth phases
Even, the hydraulic control one-way valve A（25.1）B1 mouths and Double throttle check valve A（26.1）A1 mouths be connected, the hydraulic control one-way valve B
（25.2）B mouths and Double throttle check valve B（26.2）A mouths be connected, the hydraulic control one-way valve B（25.2）B1 mouths and double unidirectional
Throttle valve B（26.2）A1 mouths be connected, the Double throttle check valve A（26.1）B mouths and diffluence motor A（27.1）P mouth phases
Connection, Double throttle check valve A（26.1）B1 mouths and clutch driving hydraulic cylinder A（28.1）A mouthfuls of rod chamber, clutch driving
Hydraulic cylinder B（28.2）A mouthfuls of rod chamber be connected, the diffluence motor A（27.1）P1 mouths and clutch driving hydraulic cylinder A
（28.1）B1 mouthfuls of rodless cavity be connected, diffluence motor A（27.1）P2 mouths and clutch driving hydraulic cylinder B（28.2）Without bar
B2 mouthfuls of chamber is connected, the Double throttle check valve B（26.2）B mouths and diffluence motor B（27.2）P mouths be connected, it is double unidirectional
Throttle valve B（26.2）B1 mouths and clutch driving hydraulic cylinder C（28.3）A mouthfuls of rod chamber, clutch driving hydraulic cylinder D
（28.4）A mouthfuls of rod chamber be connected, the diffluence motor B（27.2）P2 mouths and clutch driving hydraulic cylinder C（28.3）'s
B1 mouthfuls of rodless cavity is connected, diffluence motor B（27.2）P1 mouths and clutch driving hydraulic cylinder D（28.4）B2 mouthfuls of phases of rodless cavity
Connection, the Solenoid ball valve C（23）A mouths and Solenoid ball valve B（22）P1 mouths, Solenoid ball valve B（22）P3 mouths be connected, institute
State Solenoid ball valve A（21）P2 mouths, Solenoid ball valve B（22）P2 mouths, pressure switch A（30.1）Oil inlet and brake B
（17.2）Oil inlet be connected, the Solenoid ball valve A（21）P4 mouths, Solenoid ball valve B（22）P4 mouths, pressure switch B
（30.2）Oil inlet and brake A（17.1）Oil inlet be connected, the travel switch A（29.1）With travel switch B
（29.2）It is arranged in clutch A（31.1）The extreme position of left and right two on straight-line trajectory, the travel switch C（29.3）
With travel switch D（29.4）It is arranged in clutch B（31.2）The extreme position of left and right two on straight-line trajectory.
2. the hydraulic control system according to claim 1 for the double driving devices at a slow speed of large-sized grinder, it is characterized in that：Institute
State transfer tube（2）, control pump（19）Driving motor, proportion electro-magnet and stroking mechanism（4）Solenoid valve, pressure sensor A
（14.1）, pressure sensor B（14.2）, pressure sensor C（14.3）, pressure sensor D（14.4）, electromagnetic relief valve（20）、
Solenoid ball valve A（21）, Solenoid ball valve B（22）, Solenoid ball valve C（23）, solenoid directional control valve A（24.1）, solenoid directional control valve B
（24.2）, travel switch A（29.1）, travel switch B（29.2）, travel switch C（29.3）, travel switch D（29.4）, pressure
Switch A（30.1）, pressure switch B（30.2）It is respectively connected to control together with for measuring the photoelectric encoder of grinding mill barrel rotating speed
Device.
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| CN108227756B (en) * | 2018-01-23 | 2020-12-11 | 南京科远智慧科技集团股份有限公司 | High-precision valve control method |
| CN108654789A (en) * | 2018-06-27 | 2018-10-16 | 江阴双马重工装备有限公司 | A kind of ladle prebreaker hydraulic control system |
| CN108654791A (en) * | 2018-06-27 | 2018-10-16 | 江阴双马重工装备有限公司 | A kind of ladle precrushing mechanism |
| CN108654790A (en) * | 2018-06-27 | 2018-10-16 | 江阴双马重工装备有限公司 | A kind of ladle prebreaker |
| CN108940560B (en) * | 2018-07-16 | 2024-04-02 | 江阴双马重工装备有限公司 | Remote control system of crusher for field unmanned operation |
| CN110758094B (en) * | 2019-10-30 | 2024-04-26 | 南通威而多专用汽车制造有限公司 | Hydraulic system for engineering machinery walking and working method thereof |
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| US7251935B2 (en) * | 2005-08-31 | 2007-08-07 | Caterpillar Inc | Independent metering valve control system and method |
| DE102007004494A1 (en) * | 2006-07-12 | 2008-01-17 | Continental Teves Ag & Co. Ohg | Electrohydraulic control system for actuating an actuator in a motor vehicle |
| CN101387307A (en) * | 2008-10-31 | 2009-03-18 | 镇江华晨华通路面机械有限公司（中外合资） | Engineering machinery front wheel walking system driven by single motor |
| US8607559B2 (en) * | 2009-12-29 | 2013-12-17 | Eaton Corporation | Fluid bypass system |
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| CN104832470A (en) * | 2014-09-22 | 2015-08-12 | 北汽福田汽车股份有限公司 | Hydraulic control system of hydraulic motor |
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