CN114251317A - Steel tube rolling mill core rod limiting hydraulic pump control device - Google Patents
Steel tube rolling mill core rod limiting hydraulic pump control device Download PDFInfo
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- CN114251317A CN114251317A CN202111406396.6A CN202111406396A CN114251317A CN 114251317 A CN114251317 A CN 114251317A CN 202111406396 A CN202111406396 A CN 202111406396A CN 114251317 A CN114251317 A CN 114251317A
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- 229910000831 Steel Inorganic materials 0.000 title claims abstract description 20
- 239000010959 steel Substances 0.000 title claims abstract description 20
- 238000009785 tube rolling Methods 0.000 title claims abstract description 14
- 230000000670 limiting effect Effects 0.000 title description 18
- 239000010720 hydraulic oil Substances 0.000 claims abstract description 57
- 238000006073 displacement reaction Methods 0.000 claims abstract description 24
- 239000003921 oil Substances 0.000 claims description 44
- 230000002457 bidirectional effect Effects 0.000 claims description 17
- 238000005086 pumping Methods 0.000 claims 1
- 238000005096 rolling process Methods 0.000 description 22
- 238000005265 energy consumption Methods 0.000 description 7
- 238000000034 method Methods 0.000 description 7
- 102100037573 Dual specificity protein phosphatase 12 Human genes 0.000 description 3
- 101000881110 Homo sapiens Dual specificity protein phosphatase 12 Proteins 0.000 description 3
- 230000002829 reductive effect Effects 0.000 description 3
- 101000617738 Homo sapiens Survival motor neuron protein Proteins 0.000 description 2
- 102100021947 Survival motor neuron protein Human genes 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 238000010248 power generation Methods 0.000 description 2
- 230000000717 retained effect Effects 0.000 description 2
- 208000032225 Proximal spinal muscular atrophy type 1 Diseases 0.000 description 1
- 208000033522 Proximal spinal muscular atrophy type 2 Diseases 0.000 description 1
- 208000026481 Werdnig-Hoffmann disease Diseases 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 239000003990 capacitor Substances 0.000 description 1
- 238000004891 communication Methods 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 201000006913 intermediate spinal muscular atrophy Diseases 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000002360 preparation method Methods 0.000 description 1
- 238000003825 pressing Methods 0.000 description 1
- 230000000452 restraining effect Effects 0.000 description 1
- 238000006467 substitution reaction Methods 0.000 description 1
- 239000013589 supplement Substances 0.000 description 1
- 208000032471 type 1 spinal muscular atrophy Diseases 0.000 description 1
- 208000032521 type II spinal muscular atrophy Diseases 0.000 description 1
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Classifications
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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
- F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21B—ROLLING OF METAL
- B21B37/00—Control devices or methods specially adapted for metal-rolling mills or the work produced thereby
- B21B37/78—Control of tube rolling
-
- 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
-
- 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
- F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
- F15B15/20—Other details, e.g. assembly with regulating devices
- F15B15/28—Means for indicating the position, e.g. end of stroke
- F15B15/2815—Position sensing, i.e. means for continuous measurement of position, e.g. LVDT
-
- 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
- F15B19/00—Testing; Calibrating; Fault detection or monitoring; Simulation or modelling of fluid-pressure systems or apparatus not otherwise provided for
Abstract
The invention discloses a hydraulic control device for a mandrel restraint of a steel tube rolling mill, which comprises a controller, a displacement sensor, a plug cavity hydraulic oil adjusting unit and a rod cavity hydraulic oil adjusting unit, wherein the displacement sensor is arranged on a hydraulic cylinder and used for detecting the stroke of the hydraulic cylinder; the displacement sensor is electrically connected with the input end of the controller, and the output end of the controller is electrically connected with the control input end of the rod cavity hydraulic oil adjusting unit; the controller is used for acquiring the stroke detected by the displacement sensor to calculate the stretching speed of the hydraulic cylinder, and controlling the rod cavity hydraulic oil adjusting unit to adjust the flow of hydraulic oil flowing through the rod cavity hydraulic oil adjusting unit according to the stretching speed of the hydraulic cylinder.
Description
Technical Field
The invention relates to a limiting hydraulic pump control device for a core rod of a steel tube rolling mill.
Background
In the field of steel pipe rolling, a hollow billet punched by a puncher needs to be penetrated into a core rod before entering a rolling mill for rolling, and the core rod plays a role in supporting the inner wall of the hollow billet. In order to reduce the length of the mandrel, the advancing speed of the mandrel is smaller than the advancing speed of the hollow billet rolling, the action is called mandrel stopping, the advancing speed of the mandrel is called mandrel stopping speed, and the force applied to the mandrel in the opposite advancing direction is called mandrel stopping force. When the specifications of the hollow billets are different, the retaining speed of the core rods is also different, and the retaining speed of the core rods of the hollow billets with the same specifications is usually kept constant.
In the process of rolling the hollow billet, the hollow billet is subjected to metal deformation under the combined action of rotation and pressing of a mandrel and a roller of a rolling mill. Starting from the seizure of the tube into the steel, the mandrel advances at a fixed speed lower than the rolling speed of the steel tube. At this time, the mandrel bar is driven by the rolling force of the rolling mill, and if not limited, the mandrel bar advances synchronously with the steel pipe. In order to control the advancing speed of the mandrel, a motor or a hydraulic cylinder is usually adopted to give a certain force to the mandrel in the opposite direction of the rolling advancing, namely, the limited power of the mandrel, and the limited power of the mandrel varies from tens of tons to more than 100 tons according to different steel pipe specifications. Usually, a motor is used for long-distance mandrel restraint, and a hydraulic cylinder is used for short-distance mandrel restraint. The hydraulic control system for core rod restraint by adopting the hydraulic cylinder has the characteristics of large restraint force, long stroke of the oil cylinder, large cylinder diameter size, stable restraint speed, high retraction speed, large hydraulic flow and the like. The action process of the mandrel restraint under the action of the hydraulic cylinder is as follows:
1. the mandrel fast running motor drives the mandrel trolley and the mandrel to fast advance, so that the mandrel is inserted into the capillary and is limited and stopped at the position of the hydraulic stopper.
2. The hydraulic cylinder of the limiting device extends out at a set limiting speed, the quick mandrel operation motor adopts torque control to apply certain torque to the mandrel, the mandrel advances along with the extending speed of the hydraulic cylinder, and the hollow billet is bitten by the roller of the rolling mill to start rolling.
3. And applying a limiting force to the mandrel by a rod cavity of the hydraulic cylinder of the limiting device, so that the mandrel is not influenced by the rolling force and continues to extend at a limiting speed until the rolling of the hollow billet is finished.
4. The quick-running motor drives the mandrel trolley and the mandrel to quickly return and is separated from the hydraulic retaining device; and simultaneously, the restraint hydraulic cylinder also retracts rapidly, and the core rod and the restraint hydraulic cylinder are both in an initial state to wait for rolling of the next hollow billet.
From the process, the extending direction and the stress direction of the hydraulic cylinder are consistent in the process of the mandrel restraint, and the hydraulic cylinder is in a negative load state. At this point, the plug chamber of the restraining cylinder only needs to be replenished with oil, while the rod chamber needs to create a large back pressure to limit the speed of the cylinder. In the conventional design, because the pressure of a pump station is constant, when an oil cylinder extends, a plug cavity enters pressure oil, the extending direction of a hydraulic cylinder generates large pressure, and a horizontal component of rolling force is added, so that a high back pressure needs to be generated in a rod cavity to limit the speed of the hydraulic cylinder, and the energy consumption is high. Meanwhile, the core rod has larger limiting force, so that the cylinder diameter of the hydraulic cylinder is large, and in addition, the stretching speed is high, the flow of a hydraulic pump station is required to be large, and the installation power is very large.
The horizontal component of the force exerted by the roller on the mandrel during the period from the biting of the steel to the end of the rolling is not a constant force. On the contrary, this force varies from time to time due to the variation of the initial and final rolling speeds, the continuous decrease of the temperature of the hollow billet, the variation of the internal diameter of the hollow billet, and the like. Because the flow capacity changes when the pressure difference at the two ends of the fixed throttle valve is increased or decreased, the fixed throttle valve can not meet the speed requirement when the speed of the hydraulic cylinder is controlled to be a fixed value.
Therefore, in order to solve the problem of high energy consumption of the existing retained hydraulic cylinder, the developed hydraulic control system for the mandrel retained hydraulic pump of the steel tube rolling mill, which can reduce energy consumption in the operation process on the premise of meeting the requirement of controllable extension and retraction speeds of the hydraulic cylinder, is a technical problem to be solved urgently at present.
Disclosure of Invention
The invention aims to provide a steel tube rolling mill mandrel limiting hydraulic pump control device to solve the problem that an existing limiting hydraulic cylinder is large in energy consumption.
In order to solve the technical problem, the invention provides a hydraulic pump control device for the mandrel restraint of a steel tube rolling mill, which comprises a controller, a displacement sensor, a plug cavity hydraulic oil adjusting unit and a rod cavity hydraulic oil adjusting unit, wherein the displacement sensor is arranged on a hydraulic cylinder and used for detecting the stroke of the hydraulic cylinder; the displacement sensor is electrically connected with the input end of the controller, and the output end of the controller is electrically connected with the control input end of the rod cavity hydraulic oil adjusting unit; the controller is used for acquiring the stroke detected by the displacement sensor to calculate the stretching speed of the hydraulic cylinder, and controlling the rod cavity hydraulic oil adjusting unit to adjust the flow of hydraulic oil flowing through the rod cavity hydraulic oil adjusting unit according to the stretching speed of the hydraulic cylinder.
Furthermore, the plug cavity hydraulic oil adjusting unit comprises an oil source hydraulic oil control unit and an oil tank hydraulic oil control unit; the oil source hydraulic oil control unit comprises a second motor pump set and a second one-way valve, the second motor pump set is connected between the oil source and the oil inlet end of the second one-way valve, and the oil outlet end of the second one-way valve is connected with the plug cavity of the hydraulic cylinder; the oil tank hydraulic oil control unit comprises a cartridge valve and a first one-way valve, the oil inlet end of the first one-way valve is connected with the plug cavity of the hydraulic cylinder, and the oil outlet end of the first one-way valve is connected with the oil tank through the cartridge valve.
Furthermore, the first motor-pump group comprises a first bidirectional hydraulic pump and a first servo motor connected with the first bidirectional hydraulic pump, the first servo motor is connected with a displacement sensor through a controller, and the controller is used for acquiring the stroke of a hydraulic cylinder acquired by the displacement sensor to control the rotating speed of the first bidirectional hydraulic pump driven by the first servo motor.
Furthermore, the oil outlet end of the second one-way valve is provided with a pressure sensor electrically connected with a second driving unit of the second motor pump group; the second motor-pump set comprises a second bidirectional hydraulic pump and a second servo motor connected with the second bidirectional hydraulic pump, the second servo motor is connected with the pressure sensor through the controller, and the controller is further used for acquiring a pressure signal acquired by the pressure sensor to control the second servo motor to drive the rotating speed of the second motor-pump set.
Further, the fixed opening pressure of the first check valve is 0.5 MPa.
The invention has the beneficial effects that: the telescopic speed of the hydraulic cylinder is calculated through the stroke detected by the controller displacement sensor, the rod cavity hydraulic oil adjusting unit is controlled according to the telescopic speed of the hydraulic cylinder to adjust the flow of the hydraulic oil flowing through the rod cavity hydraulic oil adjusting unit, and the requirement that the extension and retraction speeds of the hydraulic cylinder can be controlled can be automatically adjusted; when the hydraulic cylinder extends out, the pump control device forms a differential circuit, so that the installed power of the hydraulic pump station can be reduced; in addition, the extension and retraction of the hydraulic cylinder in the hydraulic cylinder are directly controlled by the first motor-pump set and the second motor-pump set, and an intermediate link for controlling the hydraulic valve assembly is omitted, so that the complexity of a loop is reduced, and the energy consumption in the production process is reduced.
Drawings
The accompanying drawings, which are included to provide a further understanding of the application and are incorporated in and constitute a part of this application, illustrate embodiment(s) of the application and together with the description serve to explain the application and not to limit the application. In the drawings:
FIG. 1 is a schematic structural diagram of one embodiment of the present invention;
wherein: 1. a displacement sensor; 2. a hydraulic cylinder; 3. a cartridge valve; 4. a first check valve; 5. a first motor-pump set; 6. a pressure sensor; 7. a second one-way valve; 8. and a second motor-pump set.
Detailed Description
The hydraulic control device for the mandrel restraint of the steel tube rolling mill shown in fig. 1 comprises a controller, a displacement sensor 1 which is arranged on a hydraulic cylinder 2 and used for detecting the stroke of the hydraulic cylinder 2, a plug cavity hydraulic oil adjusting unit which is connected with a plug cavity of the hydraulic cylinder 2 and used for adjusting the plug cavity hydraulic pressure of the hydraulic cylinder 2, and a rod cavity hydraulic oil adjusting unit which is respectively connected with the plug cavity hydraulic oil adjusting unit and a rod cavity of the hydraulic cylinder 2 and used for adjusting the rod cavity hydraulic pressure of the hydraulic cylinder 2; the displacement sensor 1 is electrically connected with the input end of a controller, and the output end of the controller is electrically connected with the control input end of a rod cavity hydraulic oil adjusting unit; the controller is used for acquiring the stroke detected by the displacement sensor 1 and calculating the stretching speed of the hydraulic cylinder 2, and controlling the rod cavity hydraulic oil adjusting unit to adjust the flow rate of the hydraulic oil flowing through the rod cavity hydraulic oil adjusting unit according to the stretching speed of the hydraulic cylinder 2. When the hydraulic cylinder 2 is in an extending state, hydraulic oil in the rod cavity of the hydraulic cylinder 2 passes through the rod cavity hydraulic oil adjusting unit and then is supplied to the plug cavity of the hydraulic cylinder 2 together with hydraulic oil provided by the plug cavity hydraulic oil adjusting unit; when the hydraulic cylinder 2 retracts, hydraulic oil flowing out of the plug cavity of the hydraulic cylinder 2 pushes the hydraulic cylinder to retract to the rod cavity of the hydraulic cylinder 2 through the rod cavity hydraulic oil adjusting unit pump, and meanwhile, redundant hydraulic oil is adjusted to an oil tank through the plug cavity hydraulic oil adjusting unit.
The plug cavity hydraulic oil adjusting unit comprises an oil source hydraulic oil control unit and an oil tank hydraulic oil control unit; the oil source hydraulic oil control unit comprises a second motor pump set 8 and a second one-way valve 7, the second motor pump set 8 is connected between the oil source and the oil inlet end of the second one-way valve 7, and the oil outlet end of the second one-way valve 7 is connected with the plug cavity of the hydraulic cylinder 2; the oil tank hydraulic oil control unit comprises a cartridge valve 3 and a first one-way valve 4, the oil inlet end of the first one-way valve 4 is connected with the plug cavity of the hydraulic cylinder 2, and the oil outlet end of the first one-way valve 4 is connected with the oil tank through the cartridge valve 3.
The first motor-pump group 5 comprises a first bidirectional hydraulic pump and a first servo motor connected with the first bidirectional hydraulic pump, the first servo motor is connected with the displacement sensor 1 through a controller, and the controller is used for acquiring the stroke of the hydraulic cylinder 2 acquired by the displacement sensor 1 and controlling the rotating speed of the first servo motor for driving the first bidirectional hydraulic pump. The oil outlet end of the second one-way valve 7 is provided with a pressure sensor 6 which is electrically connected with a second driving unit of the second motor-pump set 8; the second motor-pump set 8 comprises a second bidirectional hydraulic pump and a second servo motor connected with the second bidirectional hydraulic pump, the second servo motor is connected with the pressure sensor 6 through the controller, and the controller is further used for acquiring a pressure signal acquired by the pressure sensor 6 to control the second servo motor to drive the rotating speed of the second motor-pump set 8. The first one-way valve 4 is provided with a fixed opening pressure of 0.5MPa, so that when the hydraulic cylinder 2 retracts, the pressure of the plug cavity is at least 0.5MPa, and the second motor pump group 8 can absorb oil.
The working principle of the hydraulic pump control device for limiting the mandrel of the steel tube rolling mill is described in detail as follows:
in the preparation stage: the hydraulic cylinder 2 is in a fully retracted state, the servo motor SMA2 of the second motor-pump group 8 stops running, the first servo motor SMA1 of the first motor-pump group 5 is in torque control, certain initial pressure is applied to a rod cavity of the hydraulic cylinder 2, and the arrival of a mandrel trolley is waited. At this stage, the pilot valve solenoid YVH1 of the cartridge valve 3 is energized, and the plug chamber of the hydraulic cylinder 2 is in a non-pressure state. The mandrel fast running motor drives the mandrel trolley and the mandrel to fast advance, the mandrel is inserted into the capillary and is limited and stopped at the position of the hydraulic limiting device.
In the limiting stage: after the mandrel reaches the position of the retaining device, the hydraulic cylinder 2 extends out at the retaining speed, and the mandrel advances with the hydraulic cylinder 2 at the retaining speed under the limitation of the retaining device and the driving of the motor. The hollow billet enters a rolling mill to start rolling, and the core rod starts to receive the horizontal component force of the hollow billet rolled by the roller. In order to ensure that the hydraulic cylinder 2 extends out of the limited speed, the first servo motor is in a power generation state at the moment, the first bidirectional hydraulic pump of the first motor-pump group 5 is prevented from rotating rapidly, and limited power is provided for the hydraulic cylinder 2. The stroke of the hydraulic cylinder 2 is detected by the displacement sensor 1, the speed of the hydraulic cylinder is calculated by the controller, and then the rotating speed of the first bidirectional hydraulic pump 5 is controlled by the first servo motor to control the extending limiting speed of the hydraulic cylinder 2; the hydraulic oil flows out from the rod cavity of the hydraulic cylinder 2, the hydraulic oil flowing out through the first motor-pump set 5 is insufficient to completely supplement the volume of the piston cavity of the hydraulic cylinder 2, and the insufficient hydraulic oil is provided by the second motor-pump set 8. At this time, the second motor-pump group 8 works to form a closed loop with the pressure sensor 6, and a constant low-pressure oil source is provided for the plug cavity of the hydraulic cylinder 2, so that the plug cavity of the hydraulic cylinder 2 is prevented from being sucked empty. In the process, the first servo motor of the first motor-pump group 5 is in a power generation state, so that energy consumption is avoided, and electric energy can be stored by connecting a capacitor plate. Because the hydraulic oil that first motor-pump package 5 flowed out directly gets into the stopper chamber of pneumatic cylinder 2, consequently second motor-pump package 8 only need to provide not enough low pressure hydraulic oil can to the stopper chamber of pneumatic cylinder 2. Therefore, in the limiting process, the oil supply flow of the second motor pump group 8 is small, the pressure is low, the power consumption of the corresponding servo motor is low, and the electric energy consumption in the production link can be saved. At this stage, the solenoid YVH1 of the pilot control valve of the cartridge valve 3 is de-energized, and the plug chamber of the hydraulic cylinder 2 and the tank are in a cut-off state.
After the rolling is finished, the quick operation motor drives the mandrel trolley and the mandrel to quickly return to be separated from the stopper device. Meanwhile, the hydraulic cylinder 2 of the limiting device also retracts rapidly at a speed lower than the speed of returning the mandrel, stops at the complete retraction position at a low speed and waits for the rolling of the next hollow billet. At this stage, the solenoid YVH1 of the pilot control valve of the cartridge valve 3 is energized, and the plug chamber of the hydraulic cylinder 2 is in a state of communication with the tank. The second motor-pump set 8 stops, the first motor-pump set 5 supplies oil to the rod cavity of the hydraulic cylinder 2 and controls the speed of the hydraulic cylinder 2; one part of the hydraulic oil in the plug cavity of the hydraulic cylinder 2 reenters the oil suction port of the first motor-pump group 5, and the redundant part flows back to the oil tank from the one-way valve 4 and the cartridge valve 3.
Finally, the above embodiments are only for illustrating the technical solutions of the present invention and not for limiting, although the present invention has been described in detail with reference to the preferred embodiments, it should be understood by those skilled in the art that modifications or equivalent substitutions may be made to the technical solutions of the present invention without departing from the spirit and scope of the technical solutions of the present invention, and all of them should be covered in the claims of the present invention.
Claims (5)
1. A hydraulic control device for a mandrel restraint of a steel tube rolling mill is characterized by comprising a controller, a displacement sensor, a plug cavity hydraulic oil adjusting unit and a rod cavity hydraulic oil adjusting unit, wherein the displacement sensor is arranged on a hydraulic cylinder and used for detecting the stroke of the hydraulic cylinder; the displacement sensor is electrically connected with the input end of the controller, and the output end of the controller is electrically connected with the control input end of the rod cavity hydraulic oil adjusting unit; the controller is used for acquiring the stroke detected by the displacement sensor to calculate the stretching speed of the hydraulic cylinder, and controlling the rod cavity hydraulic oil adjusting unit to adjust the flow of hydraulic oil flowing through the rod cavity hydraulic oil adjusting unit according to the stretching speed of the hydraulic cylinder.
2. The hydraulic control device for the mandrel restraint of the steel tube rolling mill as claimed in claim 1, wherein the plug cavity hydraulic oil adjusting unit comprises an oil source hydraulic oil control unit and an oil tank hydraulic oil control unit; the oil source hydraulic oil control unit comprises a second motor pump set and a second one-way valve, the second motor pump set is connected between the oil source and the oil inlet end of the second one-way valve, and the oil outlet end of the second one-way valve is connected with the plug cavity of the hydraulic cylinder; the oil tank hydraulic oil control unit comprises a cartridge valve and a first one-way valve, the oil inlet end of the first one-way valve is connected with the plug cavity of the hydraulic cylinder, and the oil outlet end of the first one-way valve is connected with the oil tank through the cartridge valve.
3. The hydraulic control device for the mandrel bar restraint hydraulic pump of the steel tube rolling mill as claimed in claim 2, wherein the first motor pump group comprises a first bidirectional hydraulic pump and a first servo motor connected with the first bidirectional hydraulic pump, the first servo motor is connected with a displacement sensor through a controller, and the controller is used for acquiring the stroke of a hydraulic cylinder acquired by the displacement sensor and controlling the rotating speed of the first bidirectional hydraulic pump driven by the first servo motor.
4. The hydraulic control device for the mandrel retaining hydraulic pump of the steel tube rolling mill as claimed in claim 3, wherein the oil outlet end of the second one-way valve is provided with a pressure sensor electrically connected with the second driving unit of the second motor-pump set; the second motor-pump set comprises a second bidirectional hydraulic pump and a second servo motor connected with the second bidirectional hydraulic pump, the second servo motor is connected with the pressure sensor through the controller, and the controller is further used for acquiring a pressure signal acquired by the pressure sensor to control the second servo motor to drive the rotating speed of the second motor-pump set.
5. The hydraulic pumping device for mandrel restraint of steel tube rolling mill according to claim 2, wherein the fixed opening pressure of the first check valve is 0.5 MPa.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202111406396.6A CN114251317A (en) | 2021-11-24 | 2021-11-24 | Steel tube rolling mill core rod limiting hydraulic pump control device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202111406396.6A CN114251317A (en) | 2021-11-24 | 2021-11-24 | Steel tube rolling mill core rod limiting hydraulic pump control device |
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| Publication Number | Publication Date |
|---|---|
| CN114251317A true CN114251317A (en) | 2022-03-29 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202111406396.6A Pending CN114251317A (en) | 2021-11-24 | 2021-11-24 | Steel tube rolling mill core rod limiting hydraulic pump control device |
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| CN (1) | CN114251317A (en) |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0338467A (en) * | 1989-07-04 | 1991-02-19 | Toyota Autom Loom Works Ltd | Hydraulic device of industrial vehicle |
| JPH05305321A (en) * | 1992-05-06 | 1993-11-19 | Nippon Steel Corp | Method for taperingly rolling tube end in steel tube rolling mill |
| CN101691877A (en) * | 2009-09-04 | 2010-04-07 | 佛山市顺德区震德塑料机械有限公司 | Servo motor control-based multi-pump combination controlled hydraulic power system |
| CN201896802U (en) * | 2010-11-25 | 2011-07-13 | 上海梅山钢铁股份有限公司 | Unidirectional differential speed-regulation hydraulic control device |
| CN103302099A (en) * | 2013-04-26 | 2013-09-18 | 太原重工股份有限公司 | Back-up roll hydraulic control system of mandrel pipe mill |
| CN108252983A (en) * | 2017-12-29 | 2018-07-06 | 太原重型机械集团工程技术研发有限公司 | The hydraulic control system of mandrel movement limiting mechanism |
-
2021
- 2021-11-24 CN CN202111406396.6A patent/CN114251317A/en active Pending
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0338467A (en) * | 1989-07-04 | 1991-02-19 | Toyota Autom Loom Works Ltd | Hydraulic device of industrial vehicle |
| JPH05305321A (en) * | 1992-05-06 | 1993-11-19 | Nippon Steel Corp | Method for taperingly rolling tube end in steel tube rolling mill |
| CN101691877A (en) * | 2009-09-04 | 2010-04-07 | 佛山市顺德区震德塑料机械有限公司 | Servo motor control-based multi-pump combination controlled hydraulic power system |
| CN201896802U (en) * | 2010-11-25 | 2011-07-13 | 上海梅山钢铁股份有限公司 | Unidirectional differential speed-regulation hydraulic control device |
| CN103302099A (en) * | 2013-04-26 | 2013-09-18 | 太原重工股份有限公司 | Back-up roll hydraulic control system of mandrel pipe mill |
| CN108252983A (en) * | 2017-12-29 | 2018-07-06 | 太原重型机械集团工程技术研发有限公司 | The hydraulic control system of mandrel movement limiting mechanism |
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