CN108843630B - Position and pressure continuously adjustable driving roller depressing hydraulic control system - Google Patents
Position and pressure continuously adjustable driving roller depressing hydraulic control system Download PDFInfo
- Publication number
- CN108843630B CN108843630B CN201810810943.9A CN201810810943A CN108843630B CN 108843630 B CN108843630 B CN 108843630B CN 201810810943 A CN201810810943 A CN 201810810943A CN 108843630 B CN108843630 B CN 108843630B
- Authority
- CN
- China
- Prior art keywords
- valve
- oil port
- pressure
- way
- control
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Active
Links
- 230000000881 depressing effect Effects 0.000 title claims abstract description 11
- 238000003825 pressing Methods 0.000 claims abstract description 22
- 238000005266 casting Methods 0.000 claims abstract description 20
- 238000009749 continuous casting Methods 0.000 claims abstract description 13
- 238000004519 manufacturing process Methods 0.000 claims abstract description 12
- 238000006073 displacement reaction Methods 0.000 claims abstract description 10
- 239000012530 fluid Substances 0.000 claims description 10
- 230000001105 regulatory effect Effects 0.000 claims description 9
- 230000001276 controlling effect Effects 0.000 claims description 6
- 230000009471 action Effects 0.000 claims description 4
- 230000009699 differential effect Effects 0.000 claims description 3
- 238000002955 isolation Methods 0.000 claims description 3
- 230000009467 reduction Effects 0.000 abstract description 11
- 238000004134 energy conservation Methods 0.000 abstract description 2
- 238000005096 rolling process Methods 0.000 description 5
- 238000005098 hot rolling Methods 0.000 description 3
- 229910000831 Steel Inorganic materials 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 238000005516 engineering process Methods 0.000 description 2
- 238000007731 hot pressing Methods 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 238000007789 sealing Methods 0.000 description 2
- 239000010959 steel Substances 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 238000009530 blood pressure measurement Methods 0.000 description 1
- 238000010924 continuous production Methods 0.000 description 1
- 238000011217 control strategy Methods 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 239000000126 substance Substances 0.000 description 1
- 239000013589 supplement Substances 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- 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
- F15B11/024—Systems essentially incorporating special features for controlling the speed or actuating force of an output member by means of differential connection of the servomotor lines, e.g. regenerative circuits
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B22—CASTING; POWDER METALLURGY
- B22D—CASTING OF METALS; CASTING OF OTHER SUBSTANCES BY THE SAME PROCESSES OR DEVICES
- B22D11/00—Continuous casting of metals, i.e. casting in indefinite lengths
- B22D11/12—Accessories for subsequent treating or working cast stock in situ
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B22—CASTING; POWDER METALLURGY
- B22D—CASTING OF METALS; CASTING OF OTHER SUBSTANCES BY THE SAME PROCESSES OR DEVICES
- B22D11/00—Continuous casting of metals, i.e. casting in indefinite lengths
- B22D11/16—Controlling or regulating processes or operations
-
- 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
- F15B11/08—Servomotor systems without provision for follow-up action; Circuits therefor with only one servomotor
-
- 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
- F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
-
- 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
- F15B21/08—Servomotor systems incorporating electrically operated control means
Abstract
The invention aims to provide a driving roller depressing hydraulic control system with continuously adjustable position and pressure, which comprises a hydraulic cylinder provided with a displacement sensor, wherein a pressure transmitter is arranged in a plug cavity and a rod cavity of the hydraulic cylinder and is respectively connected with a common control loop and a light depressing control loop. The common control loop consists of a pressure selection electromagnetic reversing valve, a differential electromagnetic valve, a logic valve and the like, and achieves the functions of lifting and rapid pressing of the driving roller and the like. The soft depression control loop consists of an electromagnetic valve, a shuttle valve, a three-way pressure reducing valve, an electromagnetic proportional overflow valve, a quick valve, a hydraulic control one-way valve and the like, and achieves the soft depression control function of continuously adjusting the position or pressure of the driving roller. The common control loop and the soft reduction control loop are mutually and automatically isolated when each work, and can be automatically switched to the common control loop under the failure or fault state of the soft reduction control loop, so that the production continuity of the continuous casting machine is not affected. The driving roller has the advantages of performing conventional reduction and soft reduction on casting blanks, along with high production efficiency, energy conservation, high automation degree and reliable operation.
Description
Technical Field
The invention belongs to the technical field of hydraulic control of continuous casting steel, and relates to a hydraulic control system of a driving roller.
Background
In the field of continuous casting steel, with the differentiated demands of the market on casting blank specifications, the casting blank specifications are thicker and thicker, the center of the casting blank is loosened and segregated more and more seriously, the internal quality of the casting blank is greatly influenced, and the soft reduction technology is widely applied to the continuous casting technology as the most effective method for eliminating the defects. Meanwhile, in order to pursue high efficiency of production and high quality performance of a casting blank, a continuous casting machine is required to cast a casting blank of a conventional specification and also to produce an extra-thick casting blank of high quality and high added value, so that a driving roller of the continuous casting machine is required to have functions of performing conventional reduction and light reduction on the casting blank.
Disclosure of Invention
The invention aims to provide a driving roller pressing hydraulic control system with continuously adjustable position and pressure, which has the beneficial effects that the driving roller has the functions of performing conventional pressing and light pressing on a casting blank, and has the advantages of high production efficiency, energy saving, high automation degree and reliable operation.
The technical scheme adopted by the invention is that the hydraulic cylinder comprises a hydraulic cylinder provided with a displacement sensor, wherein a plug cavity and a rod cavity of the hydraulic cylinder are respectively connected with a common control loop and a soft-pressing control loop; the common control loop consists of a ball valve A, a ball valve B, an electromagnetic directional valve, a differential electromagnetic directional valve, a logic valve A, a logic valve B, a throttle valve, an overflow valve A and a pressure measuring joint M; the pressure pipeline P1 is connected with an oil port P of the electromagnetic directional valve through a ball valve A, and the pressure pipeline P2 is connected with an oil port T of the electromagnetic directional valve through a ball valve B; the oil port A of the electromagnetic reversing valve is provided with a pressure measuring joint M and is connected with the oil port P of the differential electromagnetic reversing valve, and the oil port T of the differential electromagnetic reversing valve is connected with the oil port A of the one-way valve A and is connected with an oil return pipeline T through the one-way valve A; the oil port A of the differential electromagnetic directional valve is connected with the oil port A of the logic valve B, and the oil port B of the logic valve B is connected with a plug cavity of the hydraulic cylinder through a rubber pipe B; the oil port B of the differential electromagnetic directional valve is connected with the oil port A of the logic valve A, and the oil port B of the logic valve A is connected with a rod cavity of the hydraulic cylinder through a throttle valve and a rubber pipe A; a pressure measuring joint M is arranged between the throttle valve and the rubber pipe A and is connected with an oil port P of the overflow valve A; a pressure measuring joint M is arranged between the oil port B of the logic valve B and the rubber pipe B and is connected with the oil port T of the overflow valve A;
the soft depression control loop consists of a ball valve C, a one-way valve A, a one-way valve B, a one-way valve C, a one-way valve D, an electromagnetic reversing valve, a shuttle valve, a three-way overflow valve, a hydraulic control one-way valve A, a hydraulic control one-way valve B, a hydraulic control one-way valve C, a quick valve, an overflow valve B, an electromagnetic proportional overflow valve, a speed regulating valve, a pressure transmitter A, a pressure transmitter B and a pressure measuring joint M; the pressure pipeline P3 is connected with an oil port P of the electromagnetic reversing valve through a ball valve C, an oil port T of the electromagnetic reversing valve is connected with an oil port A of the one-way valve A and is connected with an oil return pipeline T through the one-way valve A, the oil port A of the electromagnetic reversing valve is respectively connected with an oil port A of the shuttle valve and an oil port A of the one-way valve C, and the oil port B of the electromagnetic reversing valve is respectively connected with an oil port B of the shuttle valve and an oil port P of the three-way pressure reducing valve; the oil port B of the one-way valve C is connected with the oil port P of the quick valve and is provided with a pressure measuring joint M; an oil port A of the three-way pressure reducing valve is connected with an oil port A of the hydraulic control one-way valve A, an oil port T of the three-way pressure reducing valve is connected with an oil port A of the one-way valve A and is connected with an oil return pipeline T through the one-way valve A, and an oil port L of the three-way pressure reducing valve is connected with an oil port P of the electromagnetic proportional overflow valve; an oil port P of the electromagnetic proportional overflow valve is connected with an oil port B of the electromagnetic reversing valve through a speed regulating valve, and an oil port T of the electromagnetic proportional overflow valve is connected with an oil port A of the one-way valve B and is connected with an oil discharge pipeline L through the one-way valve B; an oil port B of the hydraulic control one-way valve A is connected with an oil port P of the quick valve, a control oil port X of the hydraulic control one-way valve A is connected with an oil port B of the electromagnetic reversing valve, and an oil drain port Y of the hydraulic control one-way valve A is connected with an oil port A of the one-way valve B and is connected with an oil drain pipeline L through the one-way valve B; the oil port T of the quick valve is connected with the oil port A of the check valve A and is connected with the oil return pipeline T through the check valve A, the oil port A of the quick valve is connected with the oil port A of the hydraulic control check valve B, and the oil port B of the quick valve is connected with the oil port A of the hydraulic control check valve C; the hydraulic control one-way valve B is connected with a rod cavity of the hydraulic cylinder through a rubber pipe A, a pressure transmitter A is arranged at the oil port B of the hydraulic control one-way valve B, the oil port B of the hydraulic control one-way valve B is connected with the oil port B of the one-way valve D and is connected with the oil return pipeline T through the one-way valve A through the oil port A of the one-way valve D, and the oil drain port Y of the hydraulic control one-way valve B is connected with the oil drain pipeline L through the one-way valve B; the hydraulic control one-way valve C is characterized in that an oil port B of the hydraulic control one-way valve C is connected with a plug cavity of the hydraulic cylinder through a rubber pipe B, a pressure transmitter B is arranged at the oil port B of the hydraulic control one-way valve C, the oil port B of the hydraulic control one-way valve C is connected with an oil port P of an overflow valve B and is connected with an oil return pipeline T through an oil port T of the overflow valve A by the one-way valve A, and an oil drain port Y of the hydraulic control one-way valve C is connected with the oil drain pipeline L through the one-way valve B; the hydraulic fluid port X of the shuttle valve is provided with a pressure measuring joint M and is respectively connected with the control hydraulic fluid port X of the logic valve A, the control hydraulic fluid port X of the logic valve B, the control hydraulic fluid port X of the hydraulic control one-way valve B and the control hydraulic fluid port X of the hydraulic control one-way valve C.
Further, the electromagnetic directional valve is used for realizing the pressure selection function of the soft-pressing control loop; the electromagnet b of the electromagnetic directional valve is electrified, the pressure of the pressure pipeline P3 enters the quick valve through the electromagnetic directional valve and the one-way valve C, and the real-time position of the hydraulic cylinder is controlled by the quick valve according to the feedback of the displacement sensor, so that the closed-loop control function of the hydraulic cylinder is realized; when continuous casting production process is required to implement continuous pressure adjustable control on casting blanks, an electromagnet a of an electromagnetic reversing valve is powered on, the pressure of a pressure pipeline P3 enters a quick valve through the electromagnetic reversing valve, a three-way pressure reducing valve and a hydraulic control one-way valve A, the pressing pressure of a hydraulic cylinder is controlled by the quick valve, and the continuous pressure adjustable control function of the hydraulic cylinder is realized by setting the pressure of an electromagnetic proportional overflow valve according to feedback of pressure transmitters A and B.
Further, the soft-press control loop realizes two kinds of pressure control; one is the pressure of a soft depression system acted on an oil port P of the quick valve by an oil port A of the electromagnetic directional valve through a one-way valve C, the pressure is directly from a pressure pipeline P3, and the other is the pressure acted on the oil port P of the quick valve by an oil port B of the electromagnetic directional valve through a three-way pressure reducing valve and a hydraulic control one-way valve A, and the pressure is controlled in a remote continuous adjustable way; the electromagnetic proportional overflow valve is used for realizing remote control, and the pressure of the electromagnetic proportional overflow valve is electrically set, namely, the oil return pressure applied to an oil drain port L of the three-way pressure reducing valve is controlled to realize a pressure continuous adjustable control function; the speed regulating valve is used for providing stable flow to improve the control precision and stability of the electromagnetic proportional relief valve; the one-way valve C and the hydraulic control one-way valve A realize mutual isolation of respective pressure control loops; the three-way pressure reducing valve can realize the rapid pressure relief function when the hydraulic cylinder is overloaded through the oil return port T, and protect casting blanks and equipment from being damaged.
Further, the differential electromagnetic directional valve has a position locking function, and can maintain a pre-failure state even in a failure state, for controlling retraction of the hydraulic cylinder, lifting of the driving roller; when the electromagnet B of the differential electromagnetic reversing valve is powered on, the oil port A of the differential electromagnetic reversing valve is communicated with the oil port B of the differential electromagnetic reversing valve, and oil discharged from the plug cavity enters the rod cavity of the hydraulic cylinder through the differential electromagnetic reversing valve due to the differential function of the hydraulic cylinder, so that the hydraulic cylinder is quickly pressed down; due to the differential effect of the hydraulic cylinder, the pressure of the rod cavity of the hydraulic cylinder can be increased, and the overflow valve A is used for protecting a rod cavity loop of the hydraulic cylinder to avoid equipment damage; the differential electromagnetic reversing valve is adopted to control the rapid pressing function of the hydraulic cylinders, so that the pressure oil source oil supply capacity of the hydraulic station can be greatly reduced, and particularly, when a plurality of hydraulic cylinders work simultaneously, the power configuration of the hydraulic station can be greatly reduced.
Further, the function of the shuttle valve is to ensure that when the control loop is under action under light pressure, the logic valve A and the logic valve B of the common control loop are completely closed through the control oil port X of the shuttle valve, and simultaneously, the hydraulic control one-way valve B and the hydraulic control one-way valve C are opened; when the soft-reduction control loop is in a failure state, the hydraulic control one-way valve B and the hydraulic control one-way valve C are automatically closed, the logic valve A and the logic valve B are automatically opened, and the loops of the soft-reduction control loop are isolated, so that the common control loop can reliably work.
The common control loop is characterized in that the electromagnetic directional valve is used for switching various pressures from the hydraulic station, so that lifting of the driving roller hydraulic cylinder and depressing control of the two pressures can be realized, and the control of the dummy bar and the depressing control of the casting blank can be respectively realized. Through the differential loop, the rapid pressing function can be realized when the driving rollers act simultaneously, and the power configuration of the hydraulic station can be reduced. The depression speed of the driving roller is adjusted by a throttle valve. The soft press control loop is used for controlling the driving roller to realize a soft press position or a pressure control mode. The position closed-loop control of the hydraulic cylinder is realized by detecting the numerical value of a displacement sensor on the hydraulic cylinder and electrically and automatically controlling the quick valve; the electromagnetic proportional pressure reducing valve is electrically and automatically controlled to realize the pressure closed-loop control of the hydraulic cylinder by detecting the numerical values of the pressure transmitters of the rod cavity and the plug cavity of the hydraulic cylinder. The position and pressure control modes are selected by the electromagnetic directional valve, and the two modes are isolated from each other and are not influenced by each other. The common control loop and the soft-press control loop are not interfered with each other. When the soft-touch control loop works, the common control loop is automatically isolated from the soft-touch control loop through a logic valve; when the common loop works, the soft-pressing control loop is automatically isolated from the common control loop through the electromagnetic valve and the hydraulic control one-way valve; furthermore, if the soft reduction control loop fails or fails, the control of the hydraulic cylinder can be automatically switched to the common control loop, the driving roller is automatically switched to the conventional reduction control of the casting blank, the production continuity of the continuous casting machine is not affected, and the working reliability of the continuous casting machine is improved.
Drawings
Fig. 1 is a schematic diagram of a drive roller depressing hydraulic control system.
Detailed Description
The present invention will be described in detail with reference to the following embodiments.
The invention is shown in fig. 1, and comprises a hydraulic cylinder 17 provided with a displacement sensor 18, wherein a plug cavity and a rod cavity of the hydraulic cylinder 17 are respectively connected with a common control loop 19 and a soft-press control loop 20. The common control circuit 19 consists of ball valves a101 and B102, a solenoid directional valve 3, a differential solenoid directional valve 4, a logic valve a501 and B502, a throttle valve 6, an overflow valve a1201 and a pressure measuring joint M. The pressure pipeline P1 is connected with an oil port P of the electromagnetic directional valve 3 through a ball valve A101, and the pressure pipeline P2 is connected with an oil port T of the electromagnetic directional valve 3 through a ball valve B102; the oil port A of the electromagnetic directional valve 3 is provided with a pressure measuring joint M and is connected with the oil port P of the differential electromagnetic directional valve 4, and the oil port T of the differential electromagnetic directional valve 4 is connected with the oil port A of the one-way valve A201 and is connected with an oil return pipeline T through the one-way valve A201; the oil port A of the differential electromagnetic directional valve 4 is connected with the oil port A of the logic valve B502, and the oil port B of the logic valve B502 is connected with a plug cavity of the hydraulic cylinder 17 through a rubber pipe B1502; the oil port B of the differential electromagnetic directional valve 4 is connected with the oil port A of the logic valve A501, and the oil port B of the logic valve A501 is connected with the rod cavity of the hydraulic cylinder 17 through the throttle valve 6 and the rubber pipe A1501. A pressure measuring joint M is arranged between the throttle valve 6 and the rubber pipe A1501 and is connected with an oil port P of the overflow valve A1201; a pressure measuring joint M is arranged between the oil port B of the logic valve B502 and the rubber pipe B1502 and is connected with the oil port T of the overflow valve A1201. The soft-press control loop 20 consists of a ball valve C103, a check valve A201, a check valve B202, a check valve C203, a check valve D204, an electromagnetic directional valve 7, a shuttle valve 8, a three-way overflow valve 9, a hydraulic control check valve 1001, a hydraulic control check valve B1002, a hydraulic control check valve C1003, a quick valve 11, an overflow valve B1202, an electromagnetic proportional overflow valve 13, a speed regulating valve 14, a pressure transmitter A1501, a pressure transmitter B1502 and a pressure measuring joint M. The pressure pipeline P3 is connected with an oil port P of the electromagnetic directional valve 7 through a ball valve C103, an oil port T of the electromagnetic directional valve 7 is connected with an oil port A of the one-way valve A201 and is connected with an oil return pipeline T through the one-way valve A201, the oil port A of the electromagnetic directional valve 7 is respectively connected with an oil port A of the shuttle valve 8 and an oil port A of the one-way valve C203, and an oil port B of the electromagnetic directional valve 7 is respectively connected with an oil port B of the shuttle valve 8 and an oil port P of the three-way pressure reducing valve 9; the oil port B of the check valve C203 is connected with the oil port P of the quick valve 11 and is provided with a pressure measuring joint M; an oil port A of the three-way pressure reducing valve 9 is connected with an oil port A of the hydraulic control one-way valve A1001, an oil port T of the three-way pressure reducing valve 9 is connected with an oil port A of the one-way valve A201 and is connected with an oil return pipeline T through the one-way valve A201, and an oil port L of the three-way pressure reducing valve 9 is connected with an oil port P of the electromagnetic proportional overflow valve 13; an oil port P of the electromagnetic proportional overflow valve 13 is connected with an oil port B of the electromagnetic reversing valve 7 through a speed regulating valve 14, and an oil port T of the electromagnetic proportional overflow valve 13 is connected with an oil port A of a one-way valve B202 and is connected with an oil drain pipeline L through the one-way valve B202; the oil port B of the hydraulic control one-way valve A1001 is connected with the oil port P of the quick valve 11, the control oil port X of the hydraulic control one-way valve A1001 is connected with the oil port B of the electromagnetic directional valve 7, and the oil drain port Y of the hydraulic control one-way valve A1001 is connected with the oil port A of the one-way valve B202 and is connected with the oil drain pipeline L through the one-way valve B202; the oil port T of the quick valve 11 is connected with the oil port A of the check valve A201 and is connected with the oil return pipeline T through the check valve A201, the oil port A of the quick valve 11 is connected with the oil port A of the hydraulic control check valve B1002, and the oil port B of the quick valve 11 is connected with the oil port A of the hydraulic control check valve C1003; the hydraulic control one-way valve B1002 is connected with the rod cavity of the hydraulic cylinder 17 through a rubber pipe A1501, the hydraulic transmitter A1601 is arranged at the hydraulic control one-way valve B1002, the hydraulic control one-way valve B1002 is connected with the hydraulic control one-way valve D204 through the hydraulic control one-way valve D204, the hydraulic control one-way valve A201 is connected with the oil return pipeline T through the one-way valve A201, and the hydraulic control one-way valve B1002 is connected with the hydraulic control one-way valve B202 through the one-way valve B202; the hydraulic port B of the hydraulic control check valve C1003 is connected with a plug cavity of the hydraulic cylinder 17 through a rubber pipe B1502, the hydraulic port B of the hydraulic control check valve C1003 is provided with a pressure transmitter B1602, the hydraulic port B of the hydraulic control check valve C1003 is connected with the hydraulic port P of the overflow valve B1202 and is connected with the oil return pipeline T through the check valve A201 by connecting the hydraulic port T of the overflow valve 12 with the hydraulic port A of the check valve A201, and the oil drain port Y of the hydraulic control check valve C1003 is connected with the hydraulic port A of the check valve B202 and is connected with the oil drain pipeline L through the check valve B202; the oil port X of the shuttle valve 8 is provided with a pressure measuring joint M and is respectively connected with the control oil port X of the logic valve A501, the control oil port X of the logic valve B502, the control oil port X of the hydraulic control one-way valve B1002 and the control oil port X of the hydraulic control one-way valve C1003;
the pressure pipeline P1, the pressure pipeline P2 and the pressure pipeline P3 are three pressures set according to a continuous casting production process, wherein P1 is the pressure of a dummy bar, P2 is the pressure of a hot-pressing blank, and P3 is the system pressure for implementing light pressing. The soft-touch control circuit 20 can achieve two types of pressure control. One of them is the pressure of the soft depression system acting on the port P of the quick valve 11 from the port a of the electromagnetic directional valve 7 via the check valve C203, and this pressure is the pressure directly from the pressure line P3. The other is the pressure of the oil port B of the electromagnetic directional valve 7 acting on the oil port P of the quick valve 11 through the three-way pressure reducing valve 9 and the hydraulic control one-way valve A1001, and the pressure can be controlled in a remote continuous adjustable way; the electromagnetic proportional relief valve 13 is used for realizing remote control, and the pressure of the electromagnetic proportional relief valve 13 is electrically set, namely, the oil return pressure applied to the oil drain port L of the three-way pressure reducing valve 9 is controlled to realize a pressure continuous adjustable control function; the speed regulating valve 14 is used for providing stable flow to improve the control precision and stability of the electromagnetic proportional overflow valve 13; the one-way valve C203 and the hydraulic control one-way valve A1001 realize the mutual isolation of the respective pressure control loops; the three-way pressure reducing valve 9 can realize the rapid pressure relief function when the hydraulic cylinder 17 is overloaded through the oil return port T, and protect casting blanks and equipment from being damaged.
The electromagnetic directional valve 3 has a position locking function, and can maintain a state before failure even in a failure state, and is mainly used for selecting the dummy bar pressure P1 and the hot blank pressing pressure P2. The differential electromagnetic directional valve 4 has a position locking function, can maintain a state before failure even in a failure state, and is mainly used for controlling the retraction of the hydraulic cylinder 17, namely the lifting of the driving roller; when the electromagnet B of the differential electromagnetic reversing valve 4 is powered on, the oil port A of the differential electromagnetic reversing valve 4 is communicated with the oil port B, and oil discharged from the plug cavity enters a rod cavity of the hydraulic cylinder through the differential electromagnetic reversing valve 4 due to the differential function of the hydraulic cylinder 17, so that the hydraulic cylinder 17 is quickly pressed down; due to the differential effect of the hydraulic cylinder 17, the pressure in the rod chamber of the hydraulic cylinder 17 will increase and the relief valve a1201 is used to protect the rod chamber circuit of the hydraulic cylinder 17 from damage. The adoption of the differential electromagnetic directional valve 4 to control the rapid pressing function of the hydraulic cylinders 17 can greatly reduce the pressure oil source oil supply capacity of the hydraulic station, and particularly, when a plurality of hydraulic cylinders 17 work simultaneously, the power configuration of the hydraulic station can be greatly reduced.
The throttle 6 is used for speed control of the hydraulic cylinder 7. Logic valve a501 and logic valve B502 are used for on-off control of the piston chamber and rod chamber circuits of hydraulic cylinder 17, respectively. When the control oil ports X of the logic valve A501 and the logic valve B502 are communicated with oil, the on-off state of the logic valve A501 and the logic valve B502 depends on the oil ports A and B of the logic valve A501 and the logic valve B502; when the oil ports A and B of the logic valve A501 and the logic valve B502 have pressure effect, the logic valve A501 and the logic valve B502 are opened under the pressure effect; when the oil ports a and B of the logic valve a501 and the logic valve B502 have no pressure, the logic valve a501 and the logic valve B502 are closed under the action of the springs. When the control ports X of the logic valves a501 and B502 are filled with the pressure oil, the control ports X of the logic valves a501 and B502 have a larger area than the pilot areas of the ports of the logic valves a501 and B502, so that the logic valves a501 and B502 respond to the circuit closing by the control ports X. The automatic switching function of the corresponding loop can be realized through the logic valve A501 and the logic valve B502.
The electromagnetic directional valve 7 is used for realizing the pressure selection function of the soft-press control loop. The electromagnet b of the electromagnetic directional valve 7 is electrified, the pressure of the pressure pipeline P3 enters the quick valve 11 through the electromagnetic directional valve 7 and the one-way valve C203, and the real-time position of the hydraulic cylinder 17 is controlled by the quick valve 11 according to the feedback of the displacement sensor 18, so that the closed-loop control function of the hydraulic cylinder 17 is realized; when continuous casting production process is required to carry out continuous pressure adjustable control on casting blanks, an electromagnet a of the electromagnetic directional valve 7 is powered on, the pressure of a pressure pipeline P3 enters the quick valve 11 through the electromagnetic directional valve 7, the three-way pressure reducing valve 9 and the hydraulic control one-way valve A1001, the pressing pressure of the hydraulic cylinder 17 is controlled by the quick valve 11, and the continuous pressure adjustable control function of the hydraulic cylinder 17 is realized by setting the pressure of the electromagnetic proportional overflow valve 13 according to feedback of the pressure transmitter A1601 and the pressure transmitter B1602. The function of the shuttle valve 8 is to ensure that when the control loop 20 is under the action of light pressure, the logic valve A501 and the logic valve B502 of the common control loop 19 are completely closed through the control oil port X of the shuttle valve 8, and simultaneously, the hydraulic control one-way valve B1002 and the hydraulic control one-way valve C1003 are opened; when the soft-reduction control loop 20 is in a failure state, the hydraulic control one-way valve B1002 and the hydraulic control one-way valve C1003 realize automatic closing, the logic valve A501 and the logic valve B502 realize automatic opening, and the loops of the soft-reduction control loop 20 are isolated, so that the common control loop 19 can work reliably.
The quick valve 11 consists of four logic on-off valves with the same functions, and electromagnets are a1, b1, c1 and d1 respectively, so that the quick on-off function of an oil way can be realized. The check valve D204 is used for controlling the oil supplement of the rod cavity of the hydraulic cylinder 9 and preventing the rod cavity of the hydraulic cylinder 17 from sucking empty and damaging the sealing of the hydraulic cylinder 17. The overflow valve B1202 is used for overpressure protection of the plug cavity of the hydraulic cylinder 9, prevents the excessive pressure of the plug cavity of the hydraulic cylinder 17 from damaging the sealing of the hydraulic cylinder 17, and simultaneously can prevent equipment damage caused by external load. The pressure transmitter A1601 is used for detecting the pressure of the rod cavity of the hydraulic cylinder 17, and forms a pressure closed-loop control function with the quick valve 11, and the pressure sensor B1602 is used for detecting the pressure of the plug cavity of the hydraulic cylinder 17, and forms a pressure closed-loop control function with the quick valve 11. And a displacement sensor 18 for detecting the position of the loading cylinder 17. The pressure taps M are used for pressure measurement of the corresponding circuit.
The working principle and the implementation method of the invention are as follows:
(1) Producing a conventional casting blank:
powering off all solenoid valves in the control loop under light pressure; the electromagnet b of the electromagnetic directional valve 3 in the common control loop is electrified, and the electromagnet a of the differential electromagnetic directional valve 4 is electrified; the hydraulic cylinder 17 retracts under the pressure of the dummy bar under P1, and the lifting function of the driving roller is realized.
Powering off all solenoid valves in the control loop under light pressure; the electromagnet b of the electromagnetic directional valve 3 in the common control loop is powered on, and the electromagnet b of the differential electromagnetic directional valve 4 is powered on; the hydraulic cylinder 17 presses down with the dummy bar pressure P1 to realize the function of driving the roll to press the dummy bar.
Powering off all solenoid valves in the control loop under light pressure; the electromagnet a of the electromagnetic directional valve 3 in the common control loop is powered on, and the electromagnet b of the differential electromagnetic directional valve 4 is powered on; the hydraulic cylinder 17 is pressed down by the hot-pressing blank pressure P2 to realize the function of driving the rolling hot blank.
(2) The soft press function needs to be implemented:
powering off all solenoid valves in the control loop under light pressure; the electromagnet b of the electromagnetic directional valve 3 in the common control loop is electrified, and the electromagnet a of the differential electromagnetic directional valve 4 is electrified; the hydraulic cylinder 17 retracts under the pressure of the dummy bar under P1, and the lifting function of the driving roller is realized.
Powering off all solenoid valves in the control loop under light pressure; the electromagnet b of the electromagnetic directional valve 3 in the common control loop is powered on, and the electromagnet b of the differential electromagnetic directional valve 4 is powered on; the hydraulic cylinder 17 presses down with the dummy bar pressure P1 to realize the function of driving the roll to press the dummy bar.
(1) Realizing position closed-loop control
The electromagnet B of the electromagnetic directional valve 7 in the control loop is electrified under light pressure, at the moment, the logic valve A501 and the logic valve B502 in the common control loop are automatically closed, the hydraulic control one-way valve B1002 and the hydraulic control one-way valve C1003 are automatically opened, and the quick valve 11 can realize closed-loop automatic control on the position of the hydraulic cylinder 17 by detecting the feedback value of the displacement sensor 18. At this time, the electromagnet a of the electromagnetic directional valve 3 in the common control loop is powered on, the electromagnet B of the differential electromagnetic directional valve 4 is powered on, and since the logic valve a501 and the logic valve B502 are already completely closed, the rolling hot blank pressure P2 is used for pressing in the common control loop, and the function of driving the rolling hot blank is realized as a standby control loop after the soft pressing control loop is in a failure state.
(2) Realizing continuous adjustable control of pressure
The electromagnet a of the electromagnetic directional valve 7 in the soft-pressure control loop is powered on, at the moment, the logic valve A501 and the logic valve B502 in the common control loop are automatically closed, the hydraulic control one-way valve B1002 and the hydraulic control one-way valve C1003 are automatically opened, the electromagnets B1 and a2 of the quick valve 11 are powered on, and the electromagnetic proportional overflow valve 13 is automatically controlled electrically by detecting the feedback values of the pressure transmitter A1601 and the pressure transmitter B1602, so that closed-loop automatic control of the pressure of the hydraulic cylinder 17 can be realized. At this time, the electromagnet a of the electromagnetic directional valve 3 in the common control loop is powered on, the electromagnet B of the differential electromagnetic directional valve 4 is powered on, and since the logic valve a501 and the logic valve B502 are already completely closed, the rolling hot blank pressure P2 is used for pressing in the common control loop, and the function of driving the rolling hot blank is realized as a standby control loop after the soft pressing control loop is in a failure state.
In the production processes of (1) and (2), if the soft-reduction control loop fails, the electromagnetic directional valve 7 is powered off, the control mode of the soft-reduction control loop fails, at this time, the hydraulic control one-way valve B1002 and the hydraulic control one-way valve C1003 are automatically closed by the control of the shuttle valve 8, the soft-reduction control loop is isolated, the logic valve a501 and the logic valve B502 in the normal control loop are automatically opened, at this time, the electromagnet a of the electromagnetic directional valve 3 in the normal control loop is powered on, and the electromagnet B of the differential electromagnetic directional valve 4 is powered on, so that the normal control loop is powered on by the hot-rolling billet pressure P2 and the function of driving the hot-rolling billet is realized, and the electromagnetic directional valve 3 and the differential electromagnetic directional valve 4 are electromagnetic valves with locking functions, even if the normal control loop is powered off, the loop can continuously be powered on by the hot-rolling billet pressure P2, the continuous production of the continuous casting machine is not affected, and the production efficiency is improved.
The invention has the advantages that the lifting and pressing control function of the driving rollers is realized by the common control loop, wherein the driving rollers are pressed down by adopting the differential control loop, the driving rollers are pressed down quickly, and the loop can greatly reduce the power configuration of the hydraulic power station especially when a plurality of driving rollers act simultaneously; the soft reduction control loop realizes the control function of continuously adjusting the position and the pressure of the driving roller, and can realize two soft reduction control strategies of the driving roller on the position or the pressure of the casting blank. Compared with the traditional driving roller hydraulic control system, the driving roller hydraulic control system has the advantages of high production efficiency, energy conservation, high automation degree, reliable work and the like.
The foregoing description is only of the preferred embodiments of the present invention, and is not intended to limit the invention in any way, and any simple modification, equivalent variation and modification made to the above embodiments according to the technical substance of the present invention falls within the scope of the technical solution of the present invention.
Claims (5)
1. A position and pressure continuously adjustable drive roller presses down hydraulic control system, its characterized in that: the hydraulic cylinder is provided with a displacement sensor, and a plug cavity and a rod cavity of the hydraulic cylinder are respectively connected with a common control loop and a soft depression control loop;
the common control loop consists of a ball valve A, a ball valve B, an electromagnetic directional valve, a differential electromagnetic directional valve, a logic valve A, a logic valve B, a throttle valve, an overflow valve A and a pressure measuring joint M; the pressure pipeline P1 is connected with an oil port P of the electromagnetic directional valve through a ball valve A, and the pressure pipeline P2 is connected with an oil port T of the electromagnetic directional valve through a ball valve B; the oil port A of the electromagnetic reversing valve is provided with a pressure measuring joint M and is connected with the oil port P of the differential electromagnetic reversing valve, and the oil port T of the differential electromagnetic reversing valve is connected with the oil port A of the one-way valve A and is connected with an oil return pipeline T through the one-way valve A; the oil port A of the differential electromagnetic directional valve is connected with the oil port A of the logic valve B, and the oil port B of the logic valve B is connected with a plug cavity of the hydraulic cylinder through a rubber pipe B; the oil port B of the differential electromagnetic directional valve is connected with the oil port A of the logic valve A, and the oil port B of the logic valve A is connected with a rod cavity of the hydraulic cylinder through a throttle valve and a rubber pipe A; a pressure measuring joint M is arranged between the throttle valve and the rubber pipe A and is connected with an oil port P of the overflow valve A; a pressure measuring joint M is arranged between the oil port B of the logic valve B and the rubber pipe B and is connected with the oil port T of the overflow valve A;
the soft depression control loop consists of a ball valve C, a one-way valve A, a one-way valve B, a one-way valve C, a one-way valve D, an electromagnetic reversing valve, a shuttle valve, a three-way overflow valve, a hydraulic control one-way valve A, a hydraulic control one-way valve B, a hydraulic control one-way valve C, a quick valve, an overflow valve B, an electromagnetic proportional overflow valve, a speed regulating valve, a pressure transmitter A, a pressure transmitter B and a pressure measuring joint M; the pressure pipeline P3 is connected with an oil port P of the electromagnetic reversing valve through a ball valve C, an oil port T of the electromagnetic reversing valve is connected with an oil port A of the one-way valve A and is connected with an oil return pipeline T through the one-way valve A, the oil port A of the electromagnetic reversing valve is respectively connected with an oil port A of the shuttle valve and an oil port A of the one-way valve C, and the oil port B of the electromagnetic reversing valve is respectively connected with an oil port B of the shuttle valve and an oil port P of the three-way pressure reducing valve; the oil port B of the one-way valve C is connected with the oil port P of the quick valve and is provided with a pressure measuring joint M; an oil port A of the three-way pressure reducing valve is connected with an oil port A of the hydraulic control one-way valve A, an oil port T of the three-way pressure reducing valve is connected with an oil port A of the one-way valve A and is connected with an oil return pipeline T through the one-way valve A, and an oil port L of the three-way pressure reducing valve is connected with an oil port P of the electromagnetic proportional overflow valve; an oil port P of the electromagnetic proportional overflow valve is connected with an oil port B of the electromagnetic reversing valve through a speed regulating valve, and an oil port T of the electromagnetic proportional overflow valve is connected with an oil port A of the one-way valve B and is connected with an oil discharge pipeline L through the one-way valve B; an oil port B of the hydraulic control one-way valve A is connected with an oil port P of the quick valve, a control oil port X of the hydraulic control one-way valve A is connected with an oil port B of the electromagnetic reversing valve, and an oil drain port Y of the hydraulic control one-way valve A is connected with an oil port A of the one-way valve B and is connected with an oil drain pipeline L through the one-way valve B; the oil port T of the quick valve is connected with the oil port A of the check valve A and is connected with the oil return pipeline T through the check valve A, the oil port A of the quick valve is connected with the oil port A of the hydraulic control check valve B, and the oil port B of the quick valve is connected with the oil port A of the hydraulic control check valve C; the hydraulic control one-way valve B is connected with a rod cavity of the hydraulic cylinder through a rubber pipe A, a pressure transmitter A is arranged at the oil port B of the hydraulic control one-way valve B, the oil port B of the hydraulic control one-way valve B is connected with the oil port B of the one-way valve D and is connected with the oil return pipeline T through the one-way valve A through the oil port A of the one-way valve D, and the oil drain port Y of the hydraulic control one-way valve B is connected with the oil drain pipeline L through the one-way valve B; the hydraulic control one-way valve C is characterized in that an oil port B of the hydraulic control one-way valve C is connected with a plug cavity of the hydraulic cylinder through a rubber pipe B, a pressure transmitter B is arranged at the oil port B of the hydraulic control one-way valve C, the oil port B of the hydraulic control one-way valve C is connected with an oil port P of an overflow valve B and is connected with an oil return pipeline T through an oil port T of the overflow valve A by the one-way valve A, and an oil drain port Y of the hydraulic control one-way valve C is connected with the oil drain pipeline L through the one-way valve B; the hydraulic fluid port X of the shuttle valve is provided with a pressure measuring joint M and is respectively connected with the control hydraulic fluid port X of the logic valve A, the control hydraulic fluid port X of the logic valve B, the control hydraulic fluid port X of the hydraulic control one-way valve B and the control hydraulic fluid port X of the hydraulic control one-way valve C.
2. A continuously adjustable position and pressure drive roller depressing hydraulic control system according to claim 1, wherein: the electromagnetic reversing valve is used for realizing the pressure selection function of the soft-pressing control loop; the electromagnet b of the electromagnetic directional valve is electrified, the pressure of the pressure pipeline P3 enters the quick valve through the electromagnetic directional valve and the one-way valve C, and the real-time position of the hydraulic cylinder is controlled by the quick valve according to the feedback of the displacement sensor, so that the closed-loop control function of the hydraulic cylinder is realized; when continuous casting production process is required to implement continuous pressure adjustable control on casting blanks, an electromagnet a of an electromagnetic reversing valve is powered on, the pressure of a pressure pipeline P3 enters a quick valve through the electromagnetic reversing valve, a three-way pressure reducing valve and a hydraulic control one-way valve A, the pressing pressure of a hydraulic cylinder is controlled by the quick valve, and the continuous pressure adjustable control function of the hydraulic cylinder is realized by setting the pressure of an electromagnetic proportional overflow valve according to feedback of pressure transmitters A and B.
3. A continuously adjustable position and pressure drive roller depressing hydraulic control system according to claim 1, wherein: the soft-press control loop realizes two kinds of pressure control; one is the pressure of a soft depression system acted on an oil port P of the quick valve by an oil port A of the electromagnetic directional valve through a one-way valve C, the pressure is directly from a pressure pipeline P3, and the other is the pressure acted on the oil port P of the quick valve by an oil port B of the electromagnetic directional valve through a three-way pressure reducing valve and a hydraulic control one-way valve A, and the pressure is controlled in a remote continuous adjustable way; the electromagnetic proportional overflow valve is used for realizing remote control, and the pressure of the electromagnetic proportional overflow valve is electrically set, namely, the oil return pressure applied to an oil drain port L of the three-way pressure reducing valve is controlled to realize a pressure continuous adjustable control function; the speed regulating valve is used for providing stable flow to improve the control precision and stability of the electromagnetic proportional relief valve; the one-way valve C and the hydraulic control one-way valve A realize mutual isolation of respective pressure control loops; the three-way pressure reducing valve can realize the rapid pressure relief function when the hydraulic cylinder is overloaded through the oil return port T, and protect casting blanks and equipment from being damaged.
4. A continuously adjustable position and pressure drive roller depressing hydraulic control system according to claim 1, wherein: the differential electromagnetic reversing valve has a position locking function, can maintain a state before a fault even in the fault state and is used for controlling the retraction of the hydraulic cylinder and the lifting of the driving roller; when the electromagnet B of the differential electromagnetic reversing valve is powered on, the oil port A of the differential electromagnetic reversing valve is communicated with the oil port B of the differential electromagnetic reversing valve, and oil discharged from the plug cavity enters the rod cavity of the hydraulic cylinder through the differential electromagnetic reversing valve due to the differential function of the hydraulic cylinder, so that the hydraulic cylinder is quickly pressed down; due to the differential effect of the hydraulic cylinder, the pressure of the rod cavity of the hydraulic cylinder can be increased, and the overflow valve A is used for protecting a rod cavity loop of the hydraulic cylinder to avoid equipment damage; the differential electromagnetic reversing valve is adopted to control the rapid pressing function of the hydraulic cylinders, so that the pressure oil source oil supply capacity of the hydraulic station can be greatly reduced, and particularly, when a plurality of hydraulic cylinders work simultaneously, the power configuration of the hydraulic station can be greatly reduced.
5. A continuously adjustable position and pressure drive roller depressing hydraulic control system according to claim 1, wherein: the function of the shuttle valve is to ensure that when the control loop is under action under light pressure, the logic valve A and the logic valve B of the common control loop are completely closed through the control oil port X of the shuttle valve, and simultaneously, the hydraulic control one-way valve B and the hydraulic control one-way valve C are opened; when the soft-reduction control loop is in a failure state, the hydraulic control one-way valve B and the hydraulic control one-way valve C are automatically closed, the logic valve A and the logic valve B are automatically opened, and the loops of the soft-reduction control loop are isolated, so that the common control loop can reliably work.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810810943.9A CN108843630B (en) | 2018-07-23 | 2018-07-23 | Position and pressure continuously adjustable driving roller depressing hydraulic control system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810810943.9A CN108843630B (en) | 2018-07-23 | 2018-07-23 | Position and pressure continuously adjustable driving roller depressing hydraulic control system |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN108843630A CN108843630A (en) | 2018-11-20 |
| CN108843630B true CN108843630B (en) | 2024-02-02 |
Family
ID=64196783
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201810810943.9A Active CN108843630B (en) | 2018-07-23 | 2018-07-23 | Position and pressure continuously adjustable driving roller depressing hydraulic control system |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN108843630B (en) |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110328244B (en) * | 2019-07-09 | 2020-09-08 | 东北大学 | Hydraulic tension system of straight pull type cold/warm rolling experiment machine and control method thereof |
| CN110394434B (en) * | 2019-08-06 | 2024-03-29 | 北京首钢国际工程技术有限公司 | Continuous casting billet large-reduction rolling mill reduction roll hydraulic control valve table |
| CN112211862A (en) * | 2020-08-25 | 2021-01-12 | 武汉船用机械有限责任公司 | Hydraulic system for controllable pitch propeller control |
| CN113124019B (en) * | 2021-04-30 | 2022-02-11 | 中国重型机械研究院股份公司 | Digital logic valve array hydraulic servo control system, control method and fault diagnosis method |
| CN113864254A (en) * | 2021-08-20 | 2021-12-31 | 宣化钢铁集团有限责任公司 | Withdrawal and straightening hydraulic control device |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2681115Y (en) * | 2004-01-20 | 2005-02-23 | 张新国 | Dynamic detector for steering wheel positioning of automobile |
| CN101531025A (en) * | 2009-04-15 | 2009-09-16 | 敦化市亚联机械制造有限公司 | Continuous calendar press with flexible hot pressboard |
| CN105604999A (en) * | 2016-03-10 | 2016-05-25 | 中国重型机械研究院股份公司 | Hydraulic control system for soft-reduction analog loading tests |
| CA2955713A1 (en) * | 2015-10-27 | 2017-04-27 | China University Of Mining And Technology | A multi-cylinder synchronous energy-saving and efficient hydraulic lift system and method thereof |
| CN208518981U (en) * | 2018-07-23 | 2019-02-19 | 中国重型机械研究院股份公司 | A kind of novel driven roller hydraulic control system |
-
2018
- 2018-07-23 CN CN201810810943.9A patent/CN108843630B/en active Active
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2681115Y (en) * | 2004-01-20 | 2005-02-23 | 张新国 | Dynamic detector for steering wheel positioning of automobile |
| CN101531025A (en) * | 2009-04-15 | 2009-09-16 | 敦化市亚联机械制造有限公司 | Continuous calendar press with flexible hot pressboard |
| CA2955713A1 (en) * | 2015-10-27 | 2017-04-27 | China University Of Mining And Technology | A multi-cylinder synchronous energy-saving and efficient hydraulic lift system and method thereof |
| CN105604999A (en) * | 2016-03-10 | 2016-05-25 | 中国重型机械研究院股份公司 | Hydraulic control system for soft-reduction analog loading tests |
| CN208518981U (en) * | 2018-07-23 | 2019-02-19 | 中国重型机械研究院股份公司 | A kind of novel driven roller hydraulic control system |
Non-Patent Citations (1)
| Title |
|---|
| 差动回路在连铸拉矫机液压系统上的应用;田明发;车丽平;;天津冶金(05);全文 * |
Also Published As
| Publication number | Publication date |
|---|---|
| CN108843630A (en) | 2018-11-20 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN108843630B (en) | Position and pressure continuously adjustable driving roller depressing hydraulic control system | |
| CN103148041B (en) | The controlling method of two electro-hydraulic servo valve control systems of the main passive load of a kind of energy-saving type | |
| CN103047208B (en) | Load-sensitive electro-hydraulic proportional multi-way valve | |
| CN101571155A (en) | Digital electric-hydraulic synchronous control system | |
| CN110594210A (en) | Hydraulic control system for press roll of withdrawal and straightening machine based on position and pressure double-control mode | |
| CN201396344Y (en) | Digital electro-hydraulic isochronous control system | |
| CN104074825B (en) | Two-way choice type interflow load-transducing multi-way valve | |
| CN104929992A (en) | Energy-saving design method for variable-load servo control system | |
| CN102248006B (en) | Double-closed-loop hydraulic control method for roll bending and balancing of working roll | |
| CN110394434B (en) | Continuous casting billet large-reduction rolling mill reduction roll hydraulic control valve table | |
| CN205823767U (en) | Hydraulic control circuit and blank turning machine | |
| WO2021169175A1 (en) | Oilway structure for achieving precise control of double-acting cylinder | |
| CN102248005B (en) | Method for realizing bending and balancing of working roll by virtue of bivalve linkage closed-loop control | |
| CN204099314U (en) | The automatic thickness hydraulic control system of high low pressure independence split | |
| CN208518981U (en) | A kind of novel driven roller hydraulic control system | |
| CN202356410U (en) | Double-closed-loop hydraulic control method for roll bending and balancing of working roll | |
| CN113083440B (en) | Control method of high-pressure roller mill roller gap dynamic control and deviation correction hydraulic system | |
| CN108672667A (en) | Low-power consumption hydraulic position holding system and control method with on-line proving function | |
| CN109915427B (en) | Three-pump direct-drive electro-hydrostatic actuator with back pressure control | |
| CN113529843B (en) | Pressure coupling hydraulic hybrid power driving circuit, control method thereof and excavator | |
| CN111594496A (en) | Low-power-consumption flow self-adaptive hydraulic position closed-loop control system and method | |
| CN210290307U (en) | Digital control non-interference signal and anti-saturation flow load sensitive integrated valve | |
| CN108533542B (en) | Double-cylinder hydraulic synchronous control system of deburring machine | |
| CN109501339B (en) | Hydraulic control system for pressurized oil cylinder of double-layer tire vulcanizer | |
| CN212744541U (en) | Low-power-consumption flow self-adaptive hydraulic position closed-loop control system |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |