Crystallizer vibration hydraulic system of continuous casting machine

Abstract

The utility model discloses a vibration hydraulic system for a crystallizer of a continuous casting machine. The vibration hydraulic system comprises an oil tank, an oil way loop and an oil cylinder. The oil way loop comprises an in-use valve set and a standby valve set. The in-use valve group comprises a first servo valve, a P1 port of the first servo valve is communicated with an oil outlet of the oil tank, a T1 port of the first servo valve is communicated with an oil return port of the oil tank, an A1 port of the first servo valve is communicated with a rodless cavity of the oil cylinder, and a B1 port of the first servo valve is communicated with a rod cavity of the oil cylinder. The standby valve group comprises a second servo valve, a P2 port of the second servo valve is communicated with an oil outlet of the oil tank, a T2 port of the second servo valve is communicated with an oil return port of the oil tank, an A2 port of the second servo valve is communicated with a rodless cavity of the oil cylinder, and a B2 port of the second servo valve is communicated with a rod cavity of the oil cylinder. According to the continuous casting machine crystallizer vibration hydraulic system, the in-use valve set and the standby valve set are arranged, the in-use valve set and the standby valve set can be manually and automatically switched in the production process, and effective guarantee is provided for stable production of a continuous casting machine.

Description

Technical Field

[0001] This application belongs to the field of hydraulic technology, specifically relating to a vibration hydraulic system for a continuous casting machine crystallizer. Background Technology

[0002] The crystallizer vibration device is the core of the continuous casting machine's hydraulic vibration system. Its precision and stability are crucial for ensuring stable operation, safe and efficient production, and product quality. Traditionally, crystallizer vibration is mostly driven mechanically. However, with the increasing demands for billet quality and production efficiency in the steel industry, hydraulic vibration systems have emerged. To ensure the response speed of the crystallizer vibration cylinder, the vibration valve assembly is generally installed on the hydraulic cylinder body. During crystallizer vibration operation, the temperature of the vibration servo valve rises. High temperatures pose a certain risk to the hydraulic valves in the hydraulic system, shortening the service life of hydraulic components and making them prone to failure. This can lead to shutdown of the continuous casting machine's crystallizer vibration hydraulic system, affecting normal production. Utility Model Content

[0003] To solve the above-mentioned technical problems, this application provides a vibration hydraulic system for a continuous casting machine crystallizer.

[0004] The technical solution adopted to achieve the purpose of this application is as follows: This utility model discloses a vibration hydraulic system for a continuous casting machine crystallizer, including an oil tank, an oil circuit, an oil control circuit, an oil drain circuit, and an oil cylinder. The oil circuit includes an active valve group and a standby valve group. The active valve group includes a first servo valve, the P1 port of which is connected to the oil outlet of the oil tank, the T1 port of which is connected to the oil return port of the oil tank, the A1 port of which is connected to the rodless chamber of the oil cylinder, and the B1 port of which is connected to the rod chamber of the oil cylinder. The standby valve group includes a second servo valve, the P2 port of which is connected to the oil outlet of the oil tank, the T2 port of which is connected to the oil return port of the oil tank, the A2 port of which is connected to the rodless chamber of the oil cylinder, and the B2 port of which is connected to the rod chamber of the oil cylinder. The oil control circuit is used to control the flow direction of the hydraulic oil, and the oil drain circuit is used to drain the oil in the hydraulic system.

[0005] In some embodiments, the valve group in use further includes a first two-position four-way directional valve, wherein the P3 port of the first two-position four-way directional valve is connected to the oil outlet of the oil tank, and the A3 port of the first two-position four-way directional valve is connected to the A1 port of the first servo valve.

[0006] The backup valve group also includes a second two-position four-way directional valve, the P4 port of which is connected to the oil outlet of the oil tank, and the A4 port of which is connected to the A2 port of the second servo valve.

[0007] In some embodiments, the valve group in use further includes a first hydraulically controlled check valve, a second hydraulically controlled check valve, and a third hydraulically controlled check valve. The first hydraulically controlled check valve is connected to the oil outlet of the oil tank, the P1 port of the first servo valve, the A3 port of the first two-position four-way directional valve, and the T3 port of the first two-position four-way directional valve, respectively. The second hydraulically controlled check valve is connected to the rod chamber of the cylinder, the B1 port of the first servo valve, the A3 port of the first two-position four-way directional valve, and the T3 port of the first two-position four-way directional valve, respectively. The third hydraulically controlled check valve is connected to the rodless chamber of the cylinder, the A1 port of the first servo valve, the A3 port of the first two-position four-way directional valve, and the T3 port of the first two-position four-way directional valve, respectively.

[0008] The backup valve group further includes a fourth hydraulically controlled check valve, a fifth hydraulically controlled check valve, and a sixth hydraulically controlled check valve. The fourth hydraulically controlled check valve is connected to the oil outlet of the oil tank, the P2 port of the second servo valve, the A4 port of the second two-position four-way directional valve, and the T4 port of the second two-position four-way directional valve, respectively. The fifth hydraulically controlled check valve is connected to the rod chamber of the cylinder, the B2 port of the second servo valve, the A4 port of the second two-position four-way directional valve, and the T4 port of the second two-position four-way directional valve, respectively. The sixth hydraulically controlled check valve is connected to the rodless chamber of the cylinder, the A2 port of the second servo valve, the A4 port of the second two-position four-way directional valve, and the T4 port of the second two-position four-way directional valve, respectively.

[0009] In some embodiments, the valve assembly in use further includes a first throttle valve, which is installed between the P3 port of the first two-position four-way directional valve and the oil outlet of the oil tank.

[0010] The backup valve group also includes a second throttle valve, which is installed between the P4 port of the second two-position four-way directional valve and the oil outlet of the oil tank.

[0011] In some embodiments, the drain circuit is equipped with a check valve, a check valve is also provided between the T1 port of the first servo valve and the oil tank, and a check valve is also provided between the T2 port of the second servo valve and the oil tank.

[0012] In some embodiments, a measuring point is set between the one-way valve and the oil tank, a measuring point is set at the oil outlet of the oil tank, a measuring point is set at the oil return port of the oil tank, a measuring point is set at the P1 port of the first servo valve, a measuring point is set at the A3 port of the first two-position four-way directional valve, a measuring point is set at the P2 port of the second servo valve, and a measuring point is set at the A4 port of the second two-position four-way directional valve.

[0013] In some embodiments, a high-pressure accumulator is provided at the oil outlet of the oil tank, and a low-pressure accumulator is provided at the oil return port of the oil tank.

[0014] In some embodiments, the oil control circuit is equipped with a plate ball valve for controlling the flow direction of hydraulic oil, and measuring points for testing the pressure of hydraulic oil are respectively provided before and after the plate ball valve.

[0015] In some embodiments, the cylinder is provided with a first relief valve and a second relief valve, the first relief valve being connected to the rod chamber and the second relief valve being connected to the rodless chamber.

[0016] In some embodiments, a first relay and a first quick-connect are provided at the oil outlet of the oil tank, a second relay and a second quick-connect are provided at the rodless chamber of the oil cylinder, and a third relay and a third quick-connect are provided at the rod chamber of the oil cylinder.

[0017] As can be seen from the above technical solution, the continuous casting machine crystallizer vibration hydraulic system disclosed in this application includes an oil tank, an oil circuit, an oil control circuit, an oil drain circuit, and an oil cylinder. The oil circuit includes an active valve group and a standby valve group. The active valve group includes a first servo valve, the P1 port of which is connected to the oil outlet of the oil tank, the T1 port of which is connected to the oil return port of the oil tank, the A1 port of which is connected to the rodless chamber of the oil cylinder, and the B1 port of which is connected to the rod chamber of the oil cylinder. The standby valve group includes a second servo valve, the P2 port of which is connected to the oil outlet of the oil tank, the T2 port of which is connected to the oil return port of the oil tank, the A2 port of which is connected to the rodless chamber of the oil cylinder, and the B2 port of which is connected to the rod chamber of the oil cylinder. The oil control circuit is used to control the flow direction of the hydraulic oil, and the oil drain circuit is used to drain the oil in the hydraulic system.

[0018] The continuous casting machine crystallizer vibration hydraulic system disclosed in this application provides effective assurance for stable production by setting up active and standby valve groups, and allowing manual or automatic switching between active and standby valves during production. This redundancy design significantly improves the reliability of the entire hydraulic system and reduces the risk of downtime due to the failure of a single component. The independent configuration of the active and standby valve groups allows for flexible adjustment of the system under different operating conditions. For example, at a specific production stage, the active or standby valve groups can be selected as needed to optimize vibration performance or adapt to different billet specifications. Attached Figure Description

[0019] To enable those skilled in the art to more clearly understand this application, the technical solutions in the embodiments of this application will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only a part of the embodiments of this application, and not all of the embodiments. Based on the embodiments of this application, all other embodiments obtained by those of ordinary skill in the art without creative effort are within the scope of protection of this application.

[0020] Figure 1 This is a schematic diagram of the vibration hydraulic system of the continuous casting machine crystallizer in one or more embodiments of this application.

[0021] Explanation of reference numerals in the attached figures:

[0022] 101-Measuring point, 201-First relay, 202-Second relay, 203-Third relay, 301-First quick-connect, 302-Second quick-connect, 303-Third quick-connect, 401-Plate ball valve, 501-First throttle valve, 502-Second throttle valve, 601-Check valve, 701-Low-pressure accumulator, 702-High-pressure accumulator, 801-First relief valve, 802-Second relief valve, 901-First hydraulic control unit 902-Second hydraulic check valve, 903-Third hydraulic check valve, 904-Fourth hydraulic check valve, 905-Fifth hydraulic check valve, 906-Sixth hydraulic check valve, 1001-First two-position four-way directional valve, 1002-Second two-position four-way directional valve, 1101-First servo valve, 1102-Second servo valve, 1201-Cylinder, 1301-In-use valve assembly, 1302-Spare valve assembly, 1401-Oil tank. Detailed Implementation

[0023] To enable those skilled in the art to more clearly understand this application, the technical solutions in the embodiments of this application will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only a part of the embodiments of this application, and not all of the embodiments. Based on the embodiments of this application, all other embodiments obtained by those of ordinary skill in the art without creative effort are within the scope of protection of this application.

[0024] Furthermore, reference numerals and / or reference letters may be repeated in different examples in this application. Such repetition is for simplification and clarity purposes and does not in itself indicate a relationship between the various embodiments and / or settings discussed. In addition, this application provides examples of various specific processes and materials; however, those skilled in the art will recognize the application of other processes and / or the use of other materials.

[0025] It should be noted that, unless otherwise specified, the embodiments and features described in these embodiments of the present invention can be combined with each other.

[0026] This utility model discloses a vibration hydraulic system for a continuous casting machine crystallizer, which can solve the technical problem of easy component failure in the prior art, thereby providing an effective guarantee for the stable production of the continuous casting machine.

[0027] The technical solution of this application will be described in detail below through specific embodiments:

[0028] See Figure 1 This application discloses a vibration hydraulic system for a continuous casting machine crystallizer, comprising an oil tank 1401, an oil circuit, an oil control circuit, an oil drain circuit, and an oil cylinder 1201. The oil circuit includes an active valve group 1301 and a standby valve group 1302. The active valve group 1301 includes a first servo valve 1101, the P1 port of which is connected to the oil outlet of the oil tank 1401, the T1 port of which is connected to the oil return port of the oil tank 1401, the A1 port of which is connected to the rodless chamber of the oil cylinder 1201, and the B1 port of which is connected to the rod chamber of the oil cylinder 1201. The standby valve assembly 1302 includes a second servo valve 1102. The P2 port of the second servo valve 1102 is connected to the oil outlet of the oil tank 1401, the T2 port of the second servo valve 1102 is connected to the oil return port of the oil tank 1401, the A2 port of the second servo valve 1102 is connected to the rodless chamber of the cylinder 1201, and the B2 port of the second servo valve 1102 is connected to the rod chamber of the cylinder 1201. The oil control circuit is used to control the flow direction of the hydraulic oil, and the drain circuit is used to drain excess oil from the hydraulic system.

[0029] The continuous casting machine crystallizer vibration hydraulic system disclosed in this embodiment provides effective assurance for stable production by setting up a working valve group 1301 and a standby valve group 1302, and allowing manual or automatic switching between the working and standby valves during production. This redundant design significantly improves the reliability of the entire hydraulic system and reduces the risk of downtime due to the failure of a single component. The independent configuration of the working valve group 1301 and the standby valve group 1302 allows for flexible adjustment of the system under different operating conditions. For example, at a specific production stage, the working valve group 1301 or the standby valve group 1302 can be selected as needed to optimize vibration performance or adapt to different billet specifications.

[0030] In one embodiment, the valve assembly 1301 in use further includes a first two-position four-way directional valve 1001. The P3 port of the first two-position four-way directional valve 1001 is connected to the oil outlet of the oil tank 1401, the A3 port of the first two-position four-way directional valve 1001 is connected to the A1 port of the first servo valve 1101, and the B3 port of the first two-position four-way directional valve 1001 is a fixed closed port. The standby valve assembly 1302 further includes a second two-position four-way directional valve 1002. The P4 port of the second two-position four-way directional valve 1002 is connected to the oil outlet of the oil tank 1401, the A4 port of the second two-position four-way directional valve 1002 is connected to the A2 port of the second servo valve 1102, and the B4 port of the second two-position four-way directional valve 1002 is a fixed closed port.

[0031] The addition of the first and second two-position four-way directional valves 1001 and 1002 allows for more flexible control of the hydraulic oil flow direction between the in-use valve group 1301 and the standby valve group 1302. This not only enables more precise vibration control but also allows for rapid adjustment of the vibration mode according to production needs. By switching between the first and second two-position four-way directional valves 1001 and 1002, the system can automatically or manually select the optimal oil circuit path under different operating conditions, thereby improving the response speed and adaptability of the entire hydraulic system.

[0032] In one embodiment, the valve assembly 1301 further includes a first hydraulically controlled check valve 901, a second hydraulically controlled check valve 902, and a third hydraulically controlled check valve 903. The first hydraulically controlled check valve 901 is connected to the oil outlet of the oil tank 1401, the P1 port of the first servo valve 1101, the A3 port of the first two-position four-way directional valve 1001, and the T3 port of the first two-position four-way directional valve 1001, respectively. The second hydraulically controlled check valve 902 is connected to the rod chamber of the cylinder 1201, the B1 port of the first servo valve 1101, the A3 port of the first two-position four-way directional valve 1001, and the T3 port of the first two-position four-way directional valve 1001, respectively. The third hydraulically controlled check valve 903 is connected to the rodless chamber of the cylinder 1201, the A1 port of the first servo valve 1101, the A3 port of the first two-position four-way directional valve 1001, and the T3 port of the first two-position four-way directional valve 1001, respectively.

[0033] The backup valve group 1302 also includes a fourth hydraulically controlled check valve 904, a fifth hydraulically controlled check valve 905, and a sixth hydraulically controlled check valve 906. The fourth hydraulically controlled check valve 904 is connected to the oil outlet of the oil tank 1401, the P2 port of the second servo valve 1102, the A4 port of the second two-position four-way directional valve 1002, and the T4 port of the second two-position four-way directional valve 1002, respectively. The fifth hydraulically controlled check valve 905 is connected to the rod chamber of the cylinder 1201, the B2 port of the second servo valve 1102, the A4 port of the second two-position four-way directional valve 1002, and the T4 port of the second two-position four-way directional valve 1002, respectively. The sixth hydraulically controlled check valve 906 is connected to the rodless chamber of the cylinder 1201, the A2 port of the second servo valve 1102, the A4 port of the second two-position four-way directional valve 1002, and the T4 port of the second two-position four-way directional valve 1002, respectively.

[0034] The addition of a hydraulically controlled check valve, especially between the servo valve and the oil outlet of tank 1401 and the cylinder 1201 chamber, effectively prevents reverse flow of the oil, ensuring unidirectional flow and pressure stability of the oil circuit. Precise control of the hydraulically controlled check valve further optimizes the supply and discharge of hydraulic oil, reduces pressure fluctuations, and thus improves the stability and consistency of the continuous casting machine's crystallizer vibration.

[0035] The addition of a hydraulically controlled check valve enhances the system's resistance to external shocks and disturbances. During the vibration of the continuous casting machine's mold, the system may be subjected to shocks and disturbances due to factors such as billet movement and temperature changes. The hydraulically controlled check valve can respond quickly and stabilize the oil circuit pressure, thereby protecting the system from damage.

[0036] In one embodiment, the valve assembly 1301 in use further includes a first throttle valve 501, which is installed between the P3 port of the first two-position four-way directional valve 1001 and the oil outlet of the oil tank 1401.

[0037] The standby valve assembly 1302 also includes a second throttle valve 502, which is installed between the P4 port of the second two-position four-way directional valve 1002 and the oil outlet of the oil tank 1401.

[0038] The addition of the first throttle valve 501 and the second throttle valve 502 enables the system to control the flow rate of hydraulic oil more precisely. By adjusting the opening of the first throttle valve 501 and the second throttle valve 502, the hydraulic oil supply can be precisely adjusted, thereby optimizing key parameters such as the vibration frequency and amplitude of the continuous casting machine crystallizer.

[0039] In one embodiment, the oil drain circuit is provided with a one-way valve 601, a one-way valve 601 is also provided between the T1 port of the first servo valve 1101 and the oil tank 1401, and a one-way valve 601 is also provided between the T2 port of the second servo valve 1102 and the oil tank 1401.

[0040] The main function of the check valve 601 is to prevent oil backflow and ensure the one-way flow of the oil circuit. Installing the check valve 601 in the drain circuit effectively prevents hydraulic oil from flowing back into the high-pressure part of the system during the return process, thereby protecting system components from damage.

[0041] Meanwhile, a check valve 601 is provided between the T port of the first servo valve 1101 and the second servo valve 1102 and the oil tank 1401 to prevent oil backflow when the servo valve is closed or malfunctions, thereby further protecting the servo valve and other critical components.

[0042] The addition of check valve 601 enhances the stability and reliability of the system. By preventing oil backflow, check valve 601 helps maintain a clear and unobstructed oil path in the system, reducing system pressure and flow fluctuations caused by oil backflow.

[0043] In one embodiment, a measuring point 101 is provided between the one-way valve 601 and the oil tank 1401, a measuring point 101 is provided at the oil outlet of the oil tank 1401, a measuring point 101 is provided at the oil return port of the oil tank 1401, a measuring point 101 is provided at the P1 port of the first servo valve 1101, a measuring point 101 is provided at the A3 port of the first two-position four-way directional valve 1001, a measuring point 101 is provided at the P2 port of the second servo valve 1102, and a measuring point 101 is provided at the A4 port of the second two-position four-way directional valve 1002.

[0044] The installation of measuring point 101 allows operators to monitor the status of the hydraulic system in real time, including key parameters such as oil pressure, oil temperature, and oil flow. When the system malfunctions or requires maintenance, the data provided by measuring point 101 can help operators quickly locate the problem, reduce diagnostic time, and improve maintenance efficiency.

[0045] In one embodiment, a high-pressure accumulator 702 is provided at the oil outlet of the oil tank 1401, and a low-pressure accumulator 701 is provided at the oil return port of the oil tank 1401.

[0046] The high-pressure accumulator 702 can absorb and release energy fluctuations in the high-pressure section of the system, effectively stabilizing the system's operating pressure. The low-pressure accumulator 701 can absorb excess oil and energy during the oil return process, further stabilizing the system pressure and preventing pressure fluctuations from damaging the system.

[0047] In one embodiment, the oil control circuit is provided with a plate ball valve 401 for controlling the flow direction of hydraulic oil, and measuring points 101 for testing the pressure of hydraulic oil are provided before and after the plate ball valve 401.

[0048] The plate ball valve 401 features a simple structure, convenient operation, and good sealing performance, enabling precise control of the hydraulic oil flow. By opening or closing the plate ball valve 401, operators can flexibly adjust the hydraulic oil flow path to meet different production needs.

[0049] Measuring points 101 are installed before and after the plate ball valve 401 to monitor the pressure changes of the hydraulic oil in real time. This helps to promptly detect and resolve potential hydraulic problems, such as excessively high or low pressure, pressure fluctuations, etc., ensuring the stable operation of the system.

[0050] In one embodiment, the cylinder 1201 is provided with a first overflow valve 801 and a second overflow valve 802, the first overflow valve 801 being connected to the rod chamber and the second overflow valve 802 being connected to the rodless chamber.

[0051] The first relief valve 801 and the second relief valve 802 are respectively located in the rod chamber and the rodless chamber, which can precisely control the pressure of the two chambers.

[0052] The relief valve has an overload protection function. When the cylinder 1201 or system components are subjected to excessive pressure, the relief valve will automatically open to release excess oil and pressure, preventing damage to the cylinder 1201 and system components due to overload.

[0053] In one embodiment, a first relay 201 and a first quick-connector 301 are provided at the oil outlet of the oil tank 1401, a second relay 202 and a second quick-connector 302 are provided in the rodless cavity of the oil cylinder 1201, and a third relay 203 and a third quick-connector 303 are provided in the rod cavity of the oil cylinder 1201.

[0054] As an electrical control element, the relay enables precise control of the on / off state of the hydraulic oil circuit. By setting the first relay 201, the second relay 202, and the third relay 203, the hydraulic oil circuits of the oil tank 1401 outlet, the rodless chamber, and the rod chamber of the cylinder 1201 can be controlled respectively, improving the flexibility and accuracy of system control.

[0055] In one embodiment, the oil control circuit mainly involves high-pressure oil from the X-pipe passing through a plate ball valve 401 to reach the first servo valve 1101 and the second servo valve 1102 respectively. Measuring points 101 are provided before and after the plate ball valve 401 to test the pressure of the X-pipe and the pressure of the main pipe after the plate ball valve 401 respectively. The X-pipe mainly provides power for the pilot valve to control the vibration servo action.

[0056] In one embodiment, the oil drain circuit mainly involves the oil drained from the vibration servo valve, the first hydraulic check valve 901, the second hydraulic check valve 902, and the third hydraulic check valve 903 entering the main oil drain pipeline L of the oil tank 1401 through the first check valve 601; the oil drained from the vibration servo valve, the fourth hydraulic check valve 904, the fifth hydraulic check valve 905, and the sixth hydraulic check valve 906 entering the main oil drain pipeline L of the oil tank 1401 through the third check valve 601; and a measuring point 101 is installed on the oil drain pipeline L to measure the pressure of the oil drain pipeline after the first check valve 601 and the third check valve 601.

[0057] In one embodiment, the oil circuit mainly consists of an in-use valve group 1301 and a standby valve group 1302. In-use valve group 1301: High-pressure oil from the P pipe of the oil tank 1401 flows through the high-pressure accumulator 702 to the first throttle valve 501, the first hydraulic check valve 901, the second hydraulic check valve 902, and the third hydraulic check valve 903. The high-pressure oil flows through the first throttle valve 501 and the first two-position four-way directional valve 1001P3-A3, and then reaches the first hydraulic check valve 901, the second hydraulic check valve 902, and the third hydraulic check valve 903. The hydraulic check valves are open, and at this time, the high-pressure oil flows through the first hydraulic check valve 901, through the first servo valve 1101P1-A1, and through the third hydraulic check valve 903 to reach the rodless chamber of the hydraulic cylinder.

[0058] Backup valve group 1302: The high-pressure oil from the P pipe of the oil tank 1401 flows to the second throttle valve 502, the fourth hydraulic check valve 904, the fifth hydraulic check valve 905 and the sixth hydraulic check valve 906 after passing through the high-pressure accumulator 702. The high-pressure oil passes through the second throttle valve 502, flows through P4-A4 of the second two-position four-way directional valve 1002, and then reaches the fourth hydraulic check valve 904, the fifth hydraulic check valve 905 and the sixth hydraulic check valve 906. The hydraulic check valves open, and at this time the high-pressure oil passes through the fourth hydraulic check valve 904, flows through P2-A2 of the second servo valve 1102, passes through the third hydraulic check valve 903, and reaches the rodless chamber of the hydraulic cylinder.

[0059] After the P3-A3 of the first two-position four-way directional valve 1001 and the P4-A4 of the second two-position four-way directional valve 1002 are connected, the second hydraulically controlled check valve 902 and the fifth hydraulically controlled check valve 905 are opened. The hydraulic oil in the rod chamber of the cylinder 1201 flows through the second hydraulically controlled check valve 902 or the fifth hydraulically controlled check valve 905, through the B1-T1 of the first two-position four-way directional valve 1001 or the B2-T2 of the second two-position four-way directional valve 1002, and then returns to the oil tank 1401; the hydraulic oil in the rodless chamber of the cylinder 1201 flows through the third hydraulically controlled check valve 903 or the sixth hydraulically controlled check valve 906, through the A3-T3 of the first two-position four-way directional valve 1001 or the A4-T4 of the second two-position four-way directional valve 1002, and then returns to the oil tank 1401 through the second check valve 601 or the fourth check valve 601.

[0060] Through the above embodiments, this application has the following beneficial effects or advantages: The continuous casting machine crystallizer vibration hydraulic system disclosed in this application, by setting up the active valve group 1301 and the standby valve group 1302, allows the standby valve group 1302 to immediately take over when the active valve group 1301 fails, ensuring continuous operation of the system and improving system stability and reliability. The setting of the two-position four-way directional valve and the hydraulically controlled check valve can effectively prevent the reverse flow of hydraulic oil, reduce the impact and wear of the servo valve, and extend the service life of hydraulic components. The setting of the throttle valve can adjust the flow rate of hydraulic oil, thereby controlling the vibration speed of the cylinder 1201 and improving the system's response speed and accuracy. The oil tank 1401 is equipped with a high-pressure accumulator 702 and a low-pressure accumulator 701 at the oil outlet and return port, respectively, as well as multiple measuring points 101 and relay quick-connects, which can monitor the system's operating status in real time, promptly detect and handle faults, and reduce maintenance costs. The hydraulic system disclosed in this application can ensure the efficient and stable operation of the continuous casting machine, thereby improving the quality of the cast billet and production efficiency, and meeting the needs of the modern steel industry.

[0061] To make the objectives, technical solutions, and advantages of the embodiments of this utility model clearer, the technical solutions of the embodiments of this utility model have been clearly and completely described above with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of this utility model, and not all embodiments. The components of the embodiments of this utility model described and shown in the accompanying drawings can generally be arranged and designed in various different configurations.

[0062] Therefore, the above detailed description of the embodiments of the present invention provided in the accompanying drawings is not intended to limit the scope of the claimed invention, but merely to illustrate selected embodiments of the invention. All other embodiments obtained by those skilled in the art based on the embodiments of the present invention without inventive effort are within the scope of protection of the present invention.

[0063] It should be noted that similar labels and letters in the following figures indicate similar items. Therefore, once an item is defined in one figure, it does not need to be further defined and explained in subsequent figures.

[0064] In the description of this utility model, it should be understood that the terms indicating orientation or positional relationship are based on the orientation or positional relationship shown in the drawings, and are only for the convenience of describing this utility model and simplifying the description, and are not intended to indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of this utility model.

[0065] In this utility model, unless otherwise explicitly specified and limited, the terms "installation," "connection," "joining," and "fixing," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication of two components or the interaction between two components. Those skilled in the art can understand the specific meaning of the above terms in this utility model according to the specific circumstances.

[0066] In this invention, unless otherwise expressly specified and limited, "above or below" the first feature may include direct contact between the first and second features, or contact between the first and second features through another feature between them. Furthermore, "above," "over," and "on" the first feature includes the first feature directly above or diagonally above the second feature, or simply indicates that the first feature is at a higher horizontal level than the second feature. "Below," "below," and "under" the first feature includes the first feature directly below or diagonally below the second feature, or simply indicates that the first feature is at a lower horizontal level than the second feature.

[0067] Although preferred embodiments of this application have been described, those skilled in the art, upon learning the basic inventive concept, can make other changes and modifications to these embodiments. Therefore, the appended claims are intended to be interpreted as including the preferred embodiments as well as all changes and modifications falling within the scope of this application.

[0068] Obviously, those skilled in the art can make various modifications and variations to this application without departing from the spirit and scope of this application. Therefore, if such modifications and variations fall within the scope of the claims of this application and their equivalents, this application also intends to include such modifications and variations.

Claims

1. A vibration hydraulic system for a continuous casting machine crystallizer, characterized in that, The hydraulic system comprises an oil tank, an oil circuit, a control oil circuit, a drain circuit and an oil cylinder, the oil circuit comprises an in-use valve group and a standby valve group, the in-use valve group comprises a first servo valve, a P1 port of the first servo valve is communicated with an oil outlet of the oil tank, a T1 port of the first servo valve is communicated with an oil return port of the oil tank, an A1 port of the first servo valve is communicated with a rodless cavity of the oil cylinder, a B1 port of the first servo valve is communicated with a rod cavity of the oil cylinder, the standby valve group comprises a second servo valve, a P2 port of the second servo valve is communicated with the oil outlet of the oil tank, a T2 port of the second servo valve is communicated with the oil return port of the oil tank, an A2 port of the second servo valve is communicated with the rodless cavity of the oil cylinder, a B2 port of the second servo valve is communicated with the rod cavity of the oil cylinder, the control oil circuit is used for controlling the flow direction of the hydraulic oil, and the drain circuit is used for draining the oil leakage in the hydraulic system.

2. The continuous caster mold oscillation hydraulic system according to claim 1, characterized by, The in-use valve group further comprises a first two-position four-way directional valve, a P3 port of the first two-position four-way directional valve is communicated with the oil outlet of the oil tank, and an A3 port of the first two-position four-way directional valve is communicated with the A1 port of the first servo valve. The standby valve group further comprises a second two-position four-way directional valve, a P4 port of the second two-position four-way directional valve is communicated with the oil outlet of the oil tank, and an A4 port of the second two-position four-way directional valve is communicated with the A2 port of the second servo valve.

3. The continuous caster mold oscillation hydraulic system according to claim 2, characterized by, The in-use valve group further comprises a first hydraulic control check valve, a second hydraulic control check valve and a third hydraulic control check valve, the first hydraulic control check valve is respectively communicated with the oil outlet of the oil tank, the P1 port of the first servo valve, the A3 port of the first two-position four-way directional valve and the T3 port of the first two-position four-way directional valve, the second hydraulic control check valve is respectively communicated with the rod cavity of the oil cylinder, the B1 port of the first servo valve, the A3 port of the first two-position four-way directional valve and the T3 port of the first two-position four-way directional valve, and the third hydraulic control check valve is respectively communicated with the rodless cavity of the oil cylinder, the A1 port of the first servo valve, the A3 port of the first two-position four-way directional valve and the T3 port of the first two-position four-way directional valve. The standby valve group further comprises a fourth hydraulic control check valve, a fifth hydraulic control check valve and a sixth hydraulic control check valve, the fourth hydraulic control check valve is respectively communicated with the oil outlet of the oil tank, the P2 port of the second servo valve, the A4 port of the second two-position four-way directional valve and the T4 port of the second two-position four-way directional valve, the fifth hydraulic control check valve is respectively communicated with the rod cavity of the oil cylinder, the B2 port of the second servo valve, the A4 port of the second two-position four-way directional valve and the T4 port of the second two-position four-way directional valve, and the sixth hydraulic control check valve is respectively communicated with the rodless cavity of the oil cylinder, the A2 port of the second servo valve, the A4 port of the second two-position four-way directional valve and the T4 port of the second two-position four-way directional valve.

4. The continuous caster mold oscillation hydraulic system according to claim 2, characterized by, The in-use valve group further comprises a first throttle valve, and the first throttle valve is installed between the P3 port of the first two-position four-way directional valve and the oil outlet of the oil tank. The standby valve group further comprises a second throttling valve installed between the P4 port of the second two-position four-way directional valve and the oil outlet of the oil tank.

5. The continuous caster mold oscillation hydraulic system according to claim 2, characterized by, The oil discharge circuit is provided with a one-way valve, and a one-way valve is also arranged between the T1 port of the first servo valve and the oil tank, and between the T2 port of the second servo valve and the oil tank.

6. The continuous caster mold oscillation hydraulic system according to claim 5, characterized by, Measuring points are arranged between the one-way valve and the oil tank, at the oil outlet of the oil tank, at the oil return port of the oil tank, at the P1 port of the first servo valve, at the A3 port of the first two-position four-way directional valve, at the P2 port of the second servo valve, and at the A4 port of the second two-position four-way directional valve.

7. The continuous caster mould oscillation hydraulic system according to any one of claims 1 to 6, characterized in that, A high-pressure accumulator is arranged at the oil outlet of the oil tank, and a low-pressure accumulator is arranged at the oil return port of the oil tank.

8. The continuous caster mould oscillation hydraulic system according to any one of claims 1 to 6, characterized in that The oil control circuit is provided with a plate ball valve for controlling the flow direction of the hydraulic oil, and measuring points for testing the pressure of the hydraulic oil are arranged in front of and behind the plate ball valve, respectively.

9. The continuous caster mould oscillation hydraulic system according to any one of claims 1 to 6, characterized in that, The oil cylinder is provided with a first overflow valve and a second overflow valve, the first overflow valve is in communication with the rod cavity, and the second overflow valve is in communication with the rodless cavity.

10. The continuous caster mold oscillation hydraulic system according to any one of claims 1 to 6, characterized by, A first relay and a first quick connector are further arranged at the oil outlet of the oil tank, a second relay and a second quick connector are arranged at the rodless cavity of the oil cylinder, and a third relay and a third quick connector are arranged at the rod cavity of the oil cylinder.

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