CN210789152U - Rolling mill roll hydraulic control valve platform under continuous casting billet heavy reduction - Google Patents
Rolling mill roll hydraulic control valve platform under continuous casting billet heavy reduction Download PDFInfo
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Abstract
A rolling mill roller hydraulic control valve table under a continuous casting billet large press belongs to the technical field of hydraulic systems in the metallurgical industry. The hydraulic control system comprises an energy accumulator stop block, a pressure sensor I, an energy accumulator I, a hydraulic control one-way valve I, a servo valve I, a hydraulic control one-way valve II, a pressure gauge I, an electromagnetic unloading valve I, a pressure sensor II, an operation side hydraulic cylinder I, a pressure sensor III, an electromagnetic reversing valve I, an energy accumulator II, a pressure sensor IV, a transmission side hydraulic cylinder I, an electromagnetic unloading valve II, a hydraulic control one-way valve III, a servo valve II, a one-way valve II, a hydraulic control one-way valve IV, an overflow valve, a pressure reducing valve and an electromagnetic reversing valve. The rolling mill large reduction technology is realized through hydraulic loop control of the roller pressing valve table, so that the loosening defect of the center of a casting blank is improved or eliminated, the density of the casting blank is improved, and stable production of thick plates and large-specification sectional materials under the condition of low rolling compression ratio is realized. The technical transformation is easy to realize, and the market demand is large.
Description
Technical Field
The utility model belongs to the technical field of metallurgical industry hydraulic system, a rolling mill roll hydraulic control valve platform is pushed down greatly to continuous casting billet is provided. The large reduction technology of the large reduction rolling mill is used for improving or eliminating the loose defect at the center of the casting blank, improving the density of the casting blank and realizing the stable production of thick plates and large-specification sectional materials under the condition of low rolling compression ratio. The method is suitable for upgrading and reconstructing the existing domestic steelmaking continuous casting machine in the metallurgical industry and newly adding a new steelmaking continuous casting machine production line.
Background
The large reduction technology of the solidification tail end of the continuous casting billet is developed based on the small reduction technology of the solidification tail end, and is suitable for the next generation continuous casting new technology of the continuous casting billet with a large section.
The purpose of adopting the technology of solidifying the tail end under high pressure is as follows: aiming at the problem of loosening defect which is often caused by rolling an extra-thick plate with the thickness of more than 100mm, the common solution is to produce a casting blank by adopting a die casting steel ingot, an electroslag remelting steel ingot or an ultra-thick vertical casting machine, and ensure the quality of a steel plate core by a large rolling compression ratio (more than or equal to 4-5). The large reduction technology for the solidification tail end of the continuous casting blank is characterized in that a pair of large-diameter rollers is adopted to implement large reduction (more than or equal to 10mm) at the solidification tail end of a slab, so that metal flowing deformation and feeding (filling shrinkage holes and looseness generated by solidification shrinkage) are generated in the center of the casting blank, the defect of looseness in the center of the casting blank is obviously improved or eliminated, the density of the casting blank is improved, and stable production of thick plates and large-specification sections under the condition of low rolling compression ratio is realized.
At present, the technical practice cases under large reduction at the solidification end of the continuous casting slab are mainly in Japan and Korea. The great reduction process is also practiced in the Tang steel plate works in China in the form of sector reduction. The domestic rolling mill type high reduction technology is still in the research stage. The Beijing university of science and technology makes prospective research on the large reduction technology of the solidification tail end of a continuous casting slab, and obtains a plurality of patents on the technical aspect of the technology large reduction technology. The first-steel international engineering technology company and Beijing university of science and technology cooperate to perform engineering application on related research results for the first time, and the related research results are applied to the project of No. 1 slab caster in the second-stage steelmaking and continuous casting project of Jingtang.
The Jingtang second-stage 1# slab continuous casting machine is upgraded and modified into a novel device with a large reduction function, and the large reduction technology is implemented by adjusting the solidification tail end of a casting blank through a cooling system of the continuous casting machine. However, the hydraulic control of the 2-roll mill is crucial to achieving this high reduction technique. The key role is the control of the 2 upper rolling hydraulic cylinders. Mainly comprises the pressure and position control of a hydraulic cylinder. At present, no technical standard of a continuous casting billet high-pressure hydraulic control technology in a rolling mill form exists in China.
Disclosure of Invention
An object of the utility model is to provide a rolling mill roll hydraulic control valve platform under continuous casting billet is big pushes down, through full-hydraulic pressure control circuit, carries out the control of pressure and position to the hydro-cylinder, reaches the requirement that the main rolling mill carries out control to two kinds of main technological parameters of rolling force and reduction. The functionality is that the function of large reduction is realized by controlling according to a control instruction sent by an automatic control system along with a tracking signal of the solidification tail end of a casting blank; tracking the solidification position of the core part of the casting blank, and controlling a roll gap to realize a soft reduction function; and tracking the solidification tail end position of the casting blank, and matching with low-pressure clamping actions of the front auxiliary clamping roller and the rear auxiliary clamping roller when the casting blank is completely solidified to realize a low-pressure clamping function.
The utility model discloses an energy storage ware cut-off block 1, pressure sensor 2, energy storage ware 3, hydraulic control check valve 4, check valve 5, servo valve 7, hydraulic control check valve two 8, manometer 9, electromagnetism off-load valve 10, pressure sensor two 12, operation side pneumatic cylinder 13, pressure sensor three 15, electromagnetism reversing valve 16, energy storage ware two 17, pressure sensor four 18, transmission side pneumatic cylinder 19, electromagnetism off-load valve two 20, hydraulic control check valve three 22, servo valve two 23, check valve two 25, hydraulic control check valve four 26, overflow valve 27, relief pressure valve 28, electromagnetism reversing valve two 30.
The port P of the energy accumulator stopping block 1 is connected with a pressure oil pipe P1, and the port T of the energy accumulator stopping block 1 is connected with a valve table main oil return pipe T. The first accumulator 3 is connected with the port p of the accumulator stop block 1. The first pressure sensor 2 is installed on a pressure oil pipe P1 of the valve platform.
The port b of the first pilot-controlled check valve 4 is connected with the pressure oil pipe P1, the port a of the first pilot-controlled check valve 4 is connected with the port P of the first servo valve 7, the port a of the first servo valve 7 is connected with the port a of the second pilot-controlled check valve 8, and the port b of the second pilot-controlled check valve 8 is connected with the rodless cavity of the first operating-side hydraulic cylinder 13 through a ball valve and a hose. Similarly, the port b of the pilot-controlled check valve IV 26 is connected with the pressure oil pipe P1, the port a of the pilot-controlled check valve IV 26 is connected with the port P of the servo valve II 23, the port a of the servo valve II 23 is connected with the port a of the pilot-controlled check valve III 22, and the port b of the pilot-controlled check valve III 22 is connected with the rodless cavity of the transmission-side hydraulic cylinder I19 through a ball valve and a hose.
A P port of the second electromagnetic directional valve 30 is connected with a pressure oil pipe P1 of the valve table, a port a of the second electromagnetic directional valve 30 is connected with a control oil x port of the first hydraulic control one-way valve 4, the second hydraulic control one-way valve 8, the third hydraulic control one-way valve 22 and the fourth hydraulic control one-way valve 26, a port T of the second electromagnetic directional valve 30 is connected with a main oil return pipe T of the valve table, and oil drainage Y ports of the first hydraulic control one-way valve 4, the second hydraulic control one-way valve 8, the third hydraulic control one-way valve 22 and the fourth hydraulic control one-way valve 26 are respectively connected with a main oil drainage.
And a T port of the servo valve I7 is connected with a main oil return pipe T of the valve table through a one-way valve I5. Similarly, the port T of the second servo valve 23 is connected with the main valve table oil return pipe T through a second check valve 25.
And a port p of the electromagnetic unloading valve I10 is connected with a port b of the hydraulic control one-way valve II 8 and a rodless cavity of the operating side hydraulic cylinder I13. Similarly, the p port of the second electromagnetic unloading valve 20 is connected with the b port of the third pilot operated check valve 22 and the rodless cavity of the first transmission side hydraulic cylinder 19.
The second pressure sensor 12 is connected with a rodless cavity of the first hydraulic cylinder 13 on the operating side, a port p of the first electromagnetic unloading valve 10 and a port b of the first hydraulic control one-way valve 8 through a ball valve and a hose. The fourth pressure sensor 18 is connected with a rodless cavity of the first transmission side hydraulic cylinder 19, a port p of the second electromagnetic unloading valve 20 and a port b of the third pilot-controlled check valve 22 through a ball valve and a hose.
The port P of the pressure reducing valve 28 is connected with a valve table total pressure oil pipe P1, and the port a of the pressure reducing valve 28 is connected with the port P of the overflow valve 27, the port P of the first electromagnetic directional valve 16 and the port P of the second accumulator 17. The T port of the pressure reducing valve 28 is connected with the T port of the overflow valve 27 and the T port of the second accumulator 17 and then is commonly connected with the valve table main oil return pipe T. The port a of the first electromagnetic directional valve 16 is connected with the rod chamber of the first operation side hydraulic cylinder 13 and the rod chamber of the first transmission side hydraulic cylinder 19. And the third pressure sensor 15 is connected with the rod cavity of the first transmission side hydraulic cylinder 19, the rod cavity of the first operation side hydraulic cylinder 13 and the port a of the first electromagnetic directional valve 16 through a ball valve and a hose.
The first pressure gauge 9 is arranged on the valve table panel and is connected with pressure display at pressure measuring joints at each position of the valve table through a hose
The pressure sensor I2, the pressure sensor II 12, the pressure sensor III 15 and the pressure sensor IV 18 have an analog quantity output function and are mechanical.
The first hydraulic control check valve 4, the second hydraulic control check valve 8, the third hydraulic control check valve 22 and the fourth hydraulic control check valve 26 are external control leakage and hydraulic control check valves.
The first servo valve 7 and the second servo valve 23 are direct-acting type, current control, three-position four-way type and servo valves.
The first electromagnetic directional valve 16 is a 2-position 2-way directional valve.
The second electromagnetic directional valve 30 is a 2-position 4-way directional valve.
The first electromagnetic unloading valve 10 and the second electromagnetic unloading valve 20 are normally open unloading valves.
The first operating side hydraulic cylinder 13 and the first transmission side hydraulic cylinder 19 are pressing hydraulic cylinders with displacement sensors.
The first overflow valve 27 is of a direct-acting type.
The first pressure reducing valve 28 is of a direct-acting type.
The utility model has the advantages that: the large reduction technology of the rolling mill is realized through the hydraulic loop control of the roll pressing valve table, so that the defect of looseness of the center of a casting blank is improved or eliminated, the density of the casting blank is improved, and the stable production of thick plates and large-specification sectional materials under the condition of low rolling compression ratio is realized. The technical transformation is easy to realize, and the market demand is large.
Drawings
Fig. 1 is a schematic diagram of a valve station. The hydraulic control type hydraulic control valve comprises an energy accumulator stopping block 1, a pressure sensor I2, an energy accumulator I3, a hydraulic control one-way valve I4, a one-way valve I5, an electromagnet I6, a servo valve I7, a hydraulic control one-way valve II 8, a pressure gauge I9, an electromagnetic unloading valve I10, an electromagnet II 11, a pressure sensor II 12, an operation side hydraulic cylinder I13, an electromagnet III 14, a pressure sensor III 15, an electromagnetic reversing valve I16, an energy accumulator II 17, a pressure sensor IV 18, an electromagnetic unloading valve II 20, an electromagnet IV 21, a hydraulic control one-way valve III 22, a servo valve II 23, an electromagnet IV 24, a one-way valve II 25, a hydraulic control one-way valve IV 26, an overflow valve 27, a pressure reducing valve 28, an electromagnet V29 and an electromagnetic reversing valve.
Detailed Description
The utility model discloses an energy storage ware cut-off block 1, pressure sensor 2, energy storage ware 3, hydraulic control check valve 4, check valve 5, servo valve 7, hydraulic control check valve two 8, manometer 9, electromagnetism off-load valve 10, pressure sensor two 12, operation side pneumatic cylinder 13, pressure sensor three 15, electromagnetism reversing valve 16, energy storage ware two 17, pressure sensor four 18, transmission side pneumatic cylinder 19, electromagnetism off-load valve two 20, hydraulic control check valve three 22, servo valve two 23, check valve two 25, hydraulic control check valve four 26, overflow valve 27, relief pressure valve 28, electromagnetism reversing valve two 30.
The following describes embodiments of the present invention with reference to the drawings.
The port b of the first pilot-controlled check valve 4 is connected with the pressure oil pipe P1, the port a of the first pilot-controlled check valve 4 is connected with the port P of the first servo valve 7, the port a of the first servo valve 7 is connected with the port a of the second pilot-controlled check valve 8, and the port b of the second pilot-controlled check valve 8 is connected with the rodless cavity of the first operating-side hydraulic cylinder 13 through a ball valve and a hose. Similarly, the port b of the pilot-controlled check valve IV 26 is connected with the pressure oil pipe P1, the port a of the pilot-controlled check valve IV 26 is connected with the port P of the servo valve II 23, the port a of the servo valve II 23 is connected with the port a of the pilot-controlled check valve III 22, and the port b of the pilot-controlled check valve III 22 is connected with the rodless cavity of the transmission-side hydraulic cylinder I19 through a ball valve and a hose. At the moment, the five electromagnets 29 are electrified to enable the second electromagnetic directional valve 30 to be electrified and switched, the port p of the second electromagnetic directional valve is communicated with the port a of the second electromagnetic directional valve, then the port a of the second electromagnetic directional valve is communicated with the port x of the first pilot-controlled one-way valve 4, the port x of the second pilot-controlled one-way valve 8, the port x of the third pilot-controlled one-way valve 22 and the port x of the fourth pilot-controlled one-way valve 26 respectively, so that the port a and the port b of the first pilot-controlled one-way valve 4 are communicated, the port a and the port b of the second pilot-controlled one-way valve 8 are communicated, the port a and the port b of the second pilot-controlled one-way valve. Meanwhile, the electromagnet I6 inputs a current signal, and the servo valve I7 is reversed to connect the port p and the port a of the servo valve I7. Similarly, the electromagnet four 24 inputs a current signal, and the servo valve two 23 is reversed, so that the port p and the port a of the servo valve two 23 are communicated. Meanwhile, the second electromagnet 11 is electrified, the p port and the t port of the first normally-open type electromagnetic unloading valve 10 are disconnected, and similarly, the fourth electromagnet 21 is electrified, and the p port and the t port of the second normally-open type electromagnetic unloading valve 20 are disconnected. Thus, the pressure oil is communicated with the rodless cavity of the first operation side hydraulic cylinder 13 through a ball valve and a hose through a port b of the second pilot operated check valve 8, and the pressure oil enters the rodless cavity of the first operation side hydraulic cylinder 13. Similarly, the port b of the hydraulic control one-way valve III 22 is connected with the rodless cavity of the transmission side hydraulic cylinder I19 through a ball valve and a hose, and pressure oil enters the rodless cavity of the transmission side hydraulic cylinder I19. And a rod cavity of the operating side hydraulic cylinder I13 and a rod cavity of the transmission side hydraulic cylinder I19 are combined into an oil path which is communicated with an a port of the electromagnetic directional valve I16 through a ball valve and a rubber tube. Meanwhile, the electromagnet III 14 is not electrified, so that the port a of the electromagnetic directional valve I16 is communicated with the port p, and the port p of the electromagnetic directional valve I16 is connected with the port p of the overflow valve 27. When the pressure of the rod cavity of the first transmission side hydraulic cylinder 19 and the pressure of the rod cavity of the first operation side hydraulic cylinder 13 reach the set value of the overflow valve 27 along with the downward movement of the cylinder rod of the hydraulic cylinder, the port p of the overflow valve 27 is communicated with the port T, and the oil in the rod cavity returns to the main oil return pipe T of the valve table. Thus, the pressing action of the large-pressing rolling mill is completed. The magnitude of the pressing force of the pressing roller and the position control of the pressing roller need to automatically carry out current input control on a servo valve, so that the functions of large pressing, light pressing and clamping of the casting blank are realized.
The port P of the pressure reducing valve 28 is connected with a valve stand total pressure oil pipe P1, pressure oil reaches the port a of the pressure reducing valve 28 through the pressure reducing valve 28, the port a of the pressure reducing valve 28 is connected with the port P of the first electromagnetic directional valve 16, the third electromagnetic magnet 14 is not electrified, the pressure oil reaches the port a of the first electromagnetic directional valve 16 through the first electromagnetic directional valve 16, and the port a of the first electromagnetic directional valve 16 is respectively connected with the rod cavity of the first transmission side hydraulic cylinder 19 and the rod cavity of the first operation side hydraulic cylinder 13 through a ball valve and a hose. Meanwhile, the second electromagnet 11 is electrified, the p port and the t port of the first normally-open type electromagnetic unloading valve 10 are disconnected, and similarly, the fourth electromagnet 21 is electrified, and the p port and the t port of the second normally-open type electromagnetic unloading valve 20 are disconnected. Meanwhile, the five electromagnets 29 are electrified, so that the second electromagnetic directional valve 30 is electrified and switched, the p port of the second electromagnetic directional valve is communicated with the a port of the second electromagnetic directional valve, and then the a port of the second electromagnetic directional valve is communicated with the x port of the first pilot-controlled one-way valve 4, the x port of the second pilot-controlled one-way valve 8, the x port of the third pilot-controlled one-way valve 22 and the x port of the fourth pilot-controlled one-way valve 26 respectively, so that the a port and the b port of the first pilot-controlled one-way valve 4 are communicated, the a port and the b port of the second pilot-controlled one-way valve 8. Meanwhile, the electromagnet I6 inputs a current signal, and the servo valve I7 is reversed, so that the port a and the port t of the servo valve I7 are communicated. Oil flows back to the valve table main oil return pipe T from the port T of the first servo valve 7 through the first check valve 5. Similarly, the electromagnet four 24 inputs a current signal, and the servo valve two 23 is reversed, so that the port a and the port t of the servo valve two 23 are connected. The oil flows back to the valve table main oil return pipe T from the port T of the second servo valve 23 through the second check valve 25. Thus, the lifting action of the rolling mill under large pressure is completed. The raised pressure is set by the spring of the pressure relief valve 28.
When the rolling mill is under a high pressure and the rolling mill is under a reduced state, in order to protect rolling mill equipment, firstly, pressure overflow is set through springs of a first electromagnetic unloading valve 10 and a second electromagnetic unloading valve 20, at the moment, a rodless cavity of a first operating side hydraulic cylinder 13 and a first transmission side hydraulic cylinder 19 is in a high-pressure state, if the pressure continues to rise, a set value of a second pressure sensor 12 is reached, at the moment, a second electromagnet 11 and a fourth electromagnet 21 are de-energized, the first electromagnetic unloading valve 10 and the second electromagnetic unloading valve 20 are decompressed, and a rolling mill lower press roll is lifted.
In the normal production process, when a hydraulic system has a fault, pressure oil cannot be normally supplied, oil supplied by the second energy accumulator 17 can ensure that the rolling mill under the high pressure is lifted up, and oil supplied by the first energy accumulator 3 can ensure that all the 4 groups of auxiliary rollers are lifted up under the high pressure. So that the casting blank can smoothly pass through until the pouring of the furnace steel is finished.
Pressure sensor I2 realizes detection of valve table inlet oil supply pressure
The second pressure sensor 12 realizes the detection of the oil supply pressure of the rodless cavity of the first hydraulic cylinder 13 on the operating side
The third pressure sensor 15 detects the oil supply pressure of the rod cavity of the first valve operation side hydraulic cylinder 13 and the rod cavity of the first transmission side hydraulic cylinder 19, and the fourth pressure sensor 18 detects the oil supply pressure of the rodless cavity of the first operation side hydraulic cylinder 19.
Claims (10)
1. The hydraulic control valve table for the press-down roller of the rolling mill under the large reduction of the continuous casting billet is characterized by comprising an energy accumulator stopping block (1), a pressure sensor I (2), an energy accumulator I (3), a hydraulic control one-way valve I (4), a one-way valve I (5), a servo valve I (7), a hydraulic control one-way valve II (8), a pressure gauge I (9), an electromagnetic unloading valve I (10), a pressure sensor II (12), an operation side hydraulic cylinder I (13), a pressure sensor III (15), an electromagnetic reversing valve I (16), an energy accumulator II (17), a pressure sensor IV (18), a transmission side hydraulic cylinder I (19), an electromagnetic unloading valve II (20), a hydraulic control one-way valve III (22), a servo valve II (23), a one-way valve II (25), a hydraulic control one-way valve IV (26), an overflow valve (27), a pressure reducing valve (28) and an electromagnetic reversing;
a port P of the energy accumulator stopping block (1) is connected with a pressure oil pipe P1, and a port T of the energy accumulator stopping block (1) is connected with a valve table main oil return pipe T; the first energy accumulator (3) is connected with a p port of the energy accumulator stopping block (1); the first pressure sensor (2) is arranged on a pressure oil pipe P1 of the valve table;
a port b of the first hydraulic control check valve (4) is connected with a pressure oil pipe P1, a port a of the first hydraulic control check valve (4) is connected with a port P of the first servo valve (7), a port a of the first servo valve (7) is connected with a port a of the second hydraulic control check valve (8), and the port b of the second hydraulic control check valve (8) is connected with a rodless cavity of the first operation side hydraulic cylinder (13) through a ball valve and a hose; a port b of the hydraulic control one-way valve IV (26) is connected with a pressure oil pipe P1, a port a of the hydraulic control one-way valve IV (26) is connected with a port P of the servo valve II (23), a port a of the servo valve II (23) is connected with a port a of the hydraulic control one-way valve III (22), and the port b of the hydraulic control one-way valve III (22) is connected with a rodless cavity of the transmission side hydraulic cylinder I (19) through a ball valve and a hose;
a P port of the second electromagnetic directional valve (30) is connected with a pressure oil pipe P1 of the valve table, a port a of the second electromagnetic directional valve (30) is connected with a control oil x port of a first hydraulic control one-way valve (4), a second hydraulic control one-way valve (8), a third hydraulic control one-way valve (22) and a fourth hydraulic control one-way valve (26), a port T of the second electromagnetic directional valve (30) is connected with a main oil return pipe T of the valve table, and oil drainage Y ports of the first hydraulic control one-way valve (4), the second hydraulic control one-way valve (8), the third hydraulic control one-way valve (22) and the fourth hydraulic control one-way valve (26) are respectively connected with a main oil drainage pipe Y;
a T port of the servo valve I (7) is connected with a valve table main oil return pipe T through a one-way valve I (5); similarly, a T port of the second servo valve (23) is connected with a main oil return pipe T of the valve table through a second one-way valve (25);
a port p of the electromagnetic unloading valve I (10) is connected with a port b of the hydraulic control one-way valve II (8) and a rodless cavity of the operation side hydraulic cylinder I (13); a port p of the electromagnetic unloading valve II (20) is connected with a port b of the hydraulic control one-way valve III (22) and a rodless cavity of the transmission side hydraulic cylinder I (19);
the second pressure sensor (12) is connected with a rodless cavity of the first hydraulic cylinder (13) on the operation side, a p port of the first electromagnetic unloading valve (10) and a b port of the first hydraulic control one-way valve (8) through a ball valve and a hose; a pressure sensor IV (18) is connected with a rodless cavity of the transmission side hydraulic cylinder I (19), a port p of the electromagnetic unloading valve II (20) and a port b of the hydraulic control one-way valve III (22) through a ball valve and a hose;
a port P of the reducing valve (28) is connected with a valve table total pressure oil pipe P1, and a port a of the reducing valve (28) is connected with a port P of the overflow valve (27), a port P of the first electromagnetic directional valve (16) and a port P of the second energy accumulator (17); a T port of the reducing valve (28) is connected with a T port of the overflow valve (27) and a T port of the second energy accumulator (17) and then is commonly connected with a valve table main oil return pipe T; the port a of the first electromagnetic directional valve (16) is connected with a rod cavity of the first operation side hydraulic cylinder (13) and a rod cavity of the first transmission side hydraulic cylinder (19); a third pressure sensor (15) is connected with a rod cavity of the first transmission side hydraulic cylinder (19), a rod cavity of the first operation side hydraulic cylinder (13) and an a port of the first electromagnetic directional valve (16) through a ball valve and a hose;
the first pressure gauge (9) is installed on the valve table panel and is connected with pressure display at pressure measuring joints at all positions of the valve table through a hose.
2. The valve station of claim 1, wherein the pressure sensor I (2), the pressure sensor II (12), the pressure sensor III (15) and the pressure sensor IV (18) have analog quantity output function and are mechanical.
3. The valve table of claim 1, wherein the first pilot-controlled check valve (4), the second pilot-controlled check valve (8), the third pilot-controlled check valve (22) and the fourth pilot-controlled check valve (26) are external-control leakage and pilot-controlled check valves.
4. The valve station as claimed in claim 1, wherein the first servo valve (7) and the second servo valve (23) are direct-acting, current-controlled, three-position four-way, servo valves.
5. The valve station as claimed in claim 1, characterized in that said first electromagnetic directional valve (16) is a 2-position 2-way directional valve.
6. The valve stand of claim 1, wherein said second electromagnetic directional valve (30) is a 2-position 4-way directional valve.
7. The valve stand as claimed in claim 1, wherein the first electromagnetic unloading valve (10) and the second electromagnetic unloading valve (20) are normally open type unloading valves.
8. The valve station as claimed in claim 1, wherein the first operating side hydraulic cylinder (13) and the first transmission side hydraulic cylinder (19) are depressing hydraulic cylinders, and the hydraulic cylinders are provided with displacement sensors.
9. Valve station according to claim 1, characterized in that the overflow valve (27) is of the direct-acting type.
10. Valve station according to claim 1, characterized in that the pressure reducing valve (28) is of the direct-acting type.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201921263862.8U CN210789152U (en) | 2019-08-06 | 2019-08-06 | Rolling mill roll hydraulic control valve platform under continuous casting billet heavy reduction |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201921263862.8U CN210789152U (en) | 2019-08-06 | 2019-08-06 | Rolling mill roll hydraulic control valve platform under continuous casting billet heavy reduction |
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| Publication Number | Publication Date |
|---|---|
| CN210789152U true CN210789152U (en) | 2020-06-19 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201921263862.8U Active CN210789152U (en) | 2019-08-06 | 2019-08-06 | Rolling mill roll hydraulic control valve platform under continuous casting billet heavy reduction |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110394434A (en) * | 2019-08-06 | 2019-11-01 | 北京首钢国际工程技术有限公司 | A kind of big pressure rolling mill screwdown roller hydraulic control valve platform of continuous casting billet |
-
2019
- 2019-08-06 CN CN201921263862.8U patent/CN210789152U/en active Active
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110394434A (en) * | 2019-08-06 | 2019-11-01 | 北京首钢国际工程技术有限公司 | A kind of big pressure rolling mill screwdown roller hydraulic control valve platform of continuous casting billet |
| 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 |
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