A hydraulic system for a coke quencher and its control method

Abstract

This invention provides a hydraulic system and control method for a coke quencher. The system includes a pump station hydraulic system and a valve station hydraulic system. The valve station hydraulic system includes a gate trolley forward / backward control circuit, a coke guide grid movement control circuit, and at least one actuator circuit. The pump station hydraulic system adopts the control principle of an AC servo motor paired with a vane pump. The gate trolley forward / backward control circuit uses an electro-hydraulic directional valve, and the coke guide grid movement control circuit uses an electro-hydraulic directional valve and two superimposed check valves. This invention overcomes the problems of overheating and high energy loss in existing coke quencher hydraulic systems. By eliminating the use of proportional directional valves, the contamination level of the hydraulic medium can be reduced. The improved hydraulic control principle for the gate trolley and coke guide grid movement enables the coke quencher to operate efficiently, stably, and energy-savingly.

Description

Technical Field

[0001] This invention relates to the field of coking machinery and equipment technology, and more particularly to a hydraulic system for a coke quencher and its control method. Background Technology

[0002] The coke quencher is one of the main pieces of equipment in coking machinery. Its primary function is to guide the hot coke from the carbonization chamber into the quenching car, acting as a working bridge between the coke pusher and the quenching car. It consists of a traveling device, a coke guiding device, a door removal device, a furnace frame cleaning device, a furnace door cleaning device, a head and tail coke processing device, a dust collection device, and a steel frame. The main movements of the coke quencher are all controlled by an advanced hydraulic system, which offers advantages such as automated operation, low pressure, and minimal damage to the furnace body. The hydraulic system of the coke quencher is a crucial core component, primarily controlling the opening and closing of the furnace door, cleaning the furnace frame and door, and collecting head and tail coke.

[0003] Currently, the most widely used hydraulic systems for coke oven quenchers in the domestic coke oven market employ three-phase asynchronous motors combined with vane pumps or piston pumps. Because the coke oven is a typical periodic, heavy-duty process equipment, the hydraulic station is in an unloaded state for 40% of the cycle and in an effective working state for 60%. This prolonged high-volume, low-pressure unloading during the working cycle results in high energy consumption and widespread overheating. Furthermore, many current coke oven models utilize a hydraulic control principle for the movement of the coke guide grid. This is achieved by using a proportional directional valve, two externally controlled check valves connected to the A and B ports of the proportional valve, an externally controlled internally controlled check valve connecting the rod-side and rodless-side chambers of the coke guide grid cylinder, and a solenoid valve connected to the pressure relief valve's drain port to control the pressure in the pressure circuit. Meanwhile, the hydraulic control principle of the gate retrieval trolley also consists of one proportional directional valve plus two externally controlled, externally venting check valves connected to the A and B ports of the proportional valve. A solenoid valve connected to the drain port of a pressure reducing valve controls whether the pressure in the pressure oil circuit is reduced. A solenoid valve plus two check valves create a floating circuit for the gate retrieval trolley, enabling various actions of the trolley. The overall control is complex, and the proportional control has high requirements for the contamination level of the hydraulic system medium. Summary of the Invention

[0004] To address the aforementioned technical problems, a hydraulic system for a coke quencher and its control method are provided.

[0005] The technical means employed in this invention are as follows:

[0006] A coke quenching machine hydraulic system includes: a pump station hydraulic system and a valve station hydraulic system connected to the pump station hydraulic system. The pump station hydraulic system includes at least a servo driver connected to a host computer PLC, a synchronous AC servo motor connected to the servo driver, a vane pump connected to the synchronous AC servo motor, and a pressure sensor connected to the servo driver. The synchronous AC servo motor, vane pump, and pressure sensor form a small closed-loop branch. The synchronous AC servo motor is equipped with a rotary encoder. After inputting a command signal through the host computer PLC, the servo driver controls and adjusts the pressure and speed of the vane pump according to the pressure of the hydraulic system pump outlet pressure sensor and the feedback signal of the rotary encoder of the synchronous AC servo motor, and outputs the pressure and flow rate actually required by the system.

[0007] The valve station hydraulic system includes a gate trolley advance and retreat control circuit, a coke guide grid movement control circuit, and at least one actuator circuit.

[0008] The gate retrieval trolley forward and backward control circuit includes an electromagnetic directional valve I, an electro-hydraulic directional valve I, a hydraulically controlled check valve I, a hydraulically controlled check valve II, a sequence valve I, a sequence valve II, a high-pressure ball valve I, a high-pressure ball valve IV, and a gate retrieval trolley cylinder. The electromagnetic directional valve I and the electro-hydraulic directional valve I are connected to the pump station hydraulic system. The electromagnetic directional valve I is connected to the hydraulically controlled check valve I and the hydraulically controlled check valve II. The electro-hydraulic directional valve I is connected to the hydraulically controlled check valve I and the hydraulically controlled check valve II. The hydraulically controlled check valve I is connected to the rodless chamber of the gate retrieval trolley cylinder in sequence through the sequence valve I and the high-pressure ball valve I. The hydraulically controlled check valve II is connected to the rod chamber of the gate retrieval trolley cylinder in sequence through the sequence valve II and the high-pressure ball valve IV.

[0009] The coke guide grid movement control circuit includes an electromagnetic directional valve II, a stacked check valve, a sequence valve III, a sequence valve IV, an electro-hydraulic directional valve II, a stacked hydraulically controlled check valve I, a high-pressure ball valve II, a high-pressure ball valve III, a high-pressure ball valve V, a high-pressure ball valve VI, a hydraulically controlled check valve, a coke guide grid cylinder I, and a coke guide grid cylinder II. The electro-hydraulic directional valve II and the electromagnetic directional valve II are connected to the pump station hydraulic system. The electro-hydraulic directional valve II is stacked and connected to the stacked hydraulically controlled check valve I and the stacked check valve. The stacked hydraulically controlled check valve I is connected to the sequence valve III. Valve III is connected to the rodless chambers of coke guide cylinder I and coke guide cylinder II via high-pressure ball valve II and high-pressure ball valve III, respectively; the superimposed check valve is connected to sequence valve IV, and sequence valve IV is connected to the rod chambers of coke guide cylinder I and coke guide cylinder II via high-pressure ball valve V and high-pressure ball valve VI, respectively; the hydraulically controlled check valve is connected to the rodless chamber and the rod chamber of coke guide cylinder I and coke guide cylinder II; the electromagnetic directional valve II is connected to the hydraulically controlled check valve to control whether the hydraulic oil in the rod chamber of the coke guide cylinder can flow back to the rodless chamber of the coke guide cylinder.

[0010] Furthermore, during the synchronous AC servo motor control process, based on PID regulation, the servo driver executes a speed closed-loop control mode before the set pressure is reached, and the synchronous AC servo motor rotates at the set maximum speed; once the set pressure is reached, the servo driver executes a pressure closed-loop control mode, and the servo system is only responsible for maintaining a constant pressure, with speed adaptive; when the coke quencher hydraulic system is unloaded, the synchronous AC servo motor stops rotating in standby mode; since the flow required for the operation of each actuator of the coke quencher is different, when the flow required by the system changes, the speed of the synchronous AC servo motor changes with the magnitude of the flow command, and the flow is adaptive.

[0011] Furthermore, the hydraulic system of the pump station includes an oil tank, a first drain ball valve, a second drain ball valve, a level gauge, an air filter, a first heater, a second heater, a pressure gauge, a pressure sensor, a first servo driver, a second servo driver, a level relay, a temperature sensor, a first butterfly valve, a second butterfly valve, a first vibration isolator, a second vibration isolator, a first pressure testing hose, a second pressure testing hose, a first synchronous AC servo motor, a second synchronous AC servo motor, a first vane pump, a second vane pump, a ball valve, a manual pump, a first high-pressure ball valve, a first check valve, a second check valve, a first solenoid relief valve, a second solenoid relief valve, a first pressure testing connector, a second pressure testing connector, a third pressure testing connector, and a fourth pressure testing connector. The oil tank is equipped with a first drain ball valve, a second drain ball valve, a level gauge, an air filter, a first heater, a second heater, a level relay, and a temperature sensor.

[0012] The outlet of the fuel tank is connected to a main pipeline, which in turn connects to multiple branch pipelines, among which...

[0013] A branch pipeline is connected to the oil inlet P in sequence via a ball valve, a manual pump, and the first high-pressure ball valve;

[0014] A branch pipeline is connected to the first vane pump via the first butterfly valve and the first vibration damper. The first vane pump is connected to the first servo driver via the first synchronous AC servo motor. The first servo driver is connected to the host computer PLC. The first vane pump is connected to the oil inlet P via the first check valve.

[0015] A branch pipeline is connected to the second vane pump via the second butterfly valve and the second vibration damper. The second vane pump is connected to the second servo driver via the second synchronous AC servo motor. The second servo driver is connected to the host computer PLC. The second vane pump is connected to the oil inlet P via the second check valve.

[0016] The pipeline between the first vane pump and the first check valve is connected to one end of the first pipeline, and the other end of the first pipeline is connected to the pipeline between the second vane pump and the second check valve. A first electromagnetic relief valve is connected to the first pipeline near the first check valve, and a second electromagnetic relief valve is connected to the first pipeline near the second check valve. A first pressure testing connector is connected between the first electromagnetic relief valve and the first check valve, and a third pressure testing connector is connected between the second electromagnetic relief valve and the second check valve.

[0017] The pressure gauge is connected to one end of the first pressure testing hose, the other end of the first pressure testing hose is connected to the second pressure testing connector, and the second pressure testing connector is connected to the pipeline between the first check valve and the oil inlet P.

[0018] The pressure sensor is connected to one end of the second pressure measuring hose, and the other end of the second pressure measuring hose is connected to the fourth pressure measuring connector. The fourth pressure measuring connector is connected to the pipeline between the second check valve and the oil inlet P. The pressure sensor is also connected to the first servo driver and the second servo driver.

[0019] Furthermore, the P and T chambers of the electro-hydraulic directional valve I are connected to the pump station hydraulic system; the A and B chambers of the electro-hydraulic directional valve I are respectively connected to the A ports of the externally controlled and leaking hydraulic check valve I and hydraulic check valve II; the B ports of the hydraulic check valve I and hydraulic check valve II are respectively connected to the A ports of the sequence valve I and sequence valve II; the B ports of the sequence valve I and sequence valve II are respectively connected to the rodless chamber and rod chamber of the gate trolley cylinder through high-pressure ball valve I and high-pressure ball valve IV; the A and B ports of the electromagnetic directional valve I are respectively connected to the Y and X ports of the hydraulic check valve I and hydraulic check valve II; and the P and T ports of the electromagnetic directional valve I are connected to the pump station hydraulic system.

[0020] Furthermore, the P and T ports of the electro-hydraulic directional valve II are connected to the hydraulic system of the pump station; the electro-hydraulic directional valve II is superimposed and connected to the stacked hydraulically controlled check valve I and the stacked check valve; the B port of the stacked hydraulically controlled check valve I is connected to the A port of the sequence valve III, and the B port of the sequence valve III is connected to the rodless chambers of the coke guide cylinder I and the coke guide cylinder II respectively through high-pressure ball valve II and high-pressure ball valve III; the B port of the stacked check valve is connected to the A port of the sequence valve IV, and the sequence... The B port of valve IV is connected to the rod chambers of coke guide cylinder I and coke guide cylinder II via high-pressure ball valves five and six, respectively; the A port of the hydraulically controlled check valve is connected to the rodless chambers of coke guide cylinder I and coke guide cylinder II, and the B port of the hydraulically controlled check valve is connected to the rod chambers of coke guide cylinder I and coke guide cylinder II; the B port of the solenoid directional valve II is connected to the X port of the hydraulically controlled check valve via high-pressure ball valve seven, and the P and T ports of the solenoid directional valve II are connected to the pump station hydraulic system.

[0021] Furthermore, the actuator circuit includes an actuator cylinder, a solenoid directional valve, a stacked hydraulic control check valve II, a stacked one-way throttle valve, and high-pressure ball valves VIII and IX. The P and T ports of the solenoid directional valve are connected to the pump station hydraulic system; the A and B ports of the solenoid directional valve are connected to the stacked hydraulic control check valve II; the stacked hydraulic control check valve II is connected to the stacked one-way throttle valve; the stacked one-way throttle valve is connected to the high-pressure ball valves VIII and IX; and the high-pressure ball valves VIII and IX are connected to the rodless chamber and rod chamber of the actuator cylinder, respectively.

[0022] Furthermore, the hydraulic cylinder of the door retrieval trolley is equipped with a displacement sensor.

[0023] Furthermore, both the coking grid cylinder I and the coking grid cylinder II are equipped with displacement sensors.

[0024] The present invention also provides a control method for the hydraulic system of a coke quencher, used to control the forward and backward movement of the gate trolley, comprising the following steps:

[0025] The host PLC inputs pressure P1 and flow rate Q1 commands to the servo driver, energizing electromagnets YH01 / YH02 and YH2b, and electromagnet YH1a. Hydraulic check valves I and II open in reverse, extending the door trolley cylinder. Based on PID control, before reaching the set pressure, the servo driver executes a speed closed-loop control mode, causing the synchronous AC servo motor to rotate at a set high speed. When the door trolley cylinder extends to a set position close to the furnace door, its displacement sensor sends a signal, causing the synchronous AC servo motor to rotate at a set low speed and low pressure to prevent damage to the furnace frame due to excessive pressure. When the door trolley cylinder reaches the set position, its displacement sensor sends a signal, de-energizing electromagnets YH01 / YH02 and YH2b, and electromagnet YH1a, stopping the door trolley cylinder's operation. When YH02 and YH2a are energized, solenoid YH1a is energized, hydraulic check valve I and hydraulic check valve II open in reverse, and the door trolley cylinder retracts. According to PID regulation, before the set pressure is reached, the servo driver executes the speed closed-loop control mode, and the synchronous AC servo motor rotates at the set speed. When the door trolley cylinder retracts to the set position, the displacement sensor of the door trolley cylinder sends a signal, solenoids YH01 / YH02 and YH2a are de-energized, solenoid YH1a is de-energized, and the door trolley cylinder stops moving. When the door trolley cylinder needs to float backward, electro-hydraulic directional valve I is de-energized and in the neutral position, and the oil ports A, B, and T of electro-hydraulic directional valve I are connected. Solenoid YH1a is energized, and hydraulic check valve I and hydraulic check valve II open in reverse. At this time, the rod chamber and rodless chamber of the door trolley cylinder are connected through the A, B, and T ports of electro-hydraulic directional valve I to achieve the floating function.

[0026] The present invention also provides a control method for a hydraulic system of a coke quencher, for realizing the movement of the coke guide grid, comprising the following steps:

[0027] The host PLC inputs pressure P1 and flow rate Q1 commands to the servo driver, energizing electromagnets YH01 / YH02 and YH3b, and electromagnet YH4a. The hydraulic check valve opens in the reverse direction, extending the coke guide cylinders I and II. Based on PID control, before reaching the set pressure, the servo driver executes a speed closed-loop control mode, with the synchronous AC servo motor rotating at the set high speed. Hydraulic oil from the rod chambers of coke guide cylinders I and II enters the rodless chambers through the hydraulic check valve, forming a differential circuit and reducing the displacement requirement of the vane pump. When coke guide cylinders I and II extend to the set position, the synchronous AC servo motor rotates at the set low speed and low pressure to prevent damage to the furnace frame due to excessive pressure. When the cylinders extend to the set position, the displacement sensors of the coking grid cylinders I and II send signals, de-energizing electromagnets YH01 / YH02 and YH3b, and de-energizing electromagnet YH4a, causing the coking grid cylinders I and II to stop operating. When electromagnets YH01 / YH02 and YH3a are energized, and electromagnet YH4a is de-energized, the hydraulic check valve closes in the reverse direction, and the coking grid cylinders I and II retract. According to PID regulation, before the set pressure is reached, the servo drive executes the speed closed-loop control mode, and the synchronous AC servo motor rotates at the set speed. When the coking grid cylinders I and II retract to the set position, the displacement sensors of the coking grid cylinders I and II send signals, de-energizing electromagnets YH01 / YH02 and YH3a, causing the coking grid cylinders I and II to stop operating.

[0028] Compared with the prior art, the present invention has the following advantages:

[0029] 1. This invention employs novel energy-saving control technology, employing a synchronous AC servo motor paired with a vane pump control principle. The AC servo driver adjusts the servo motor's speed, and based on system pressure and speed feedback signals, controls and adjusts the pump's pressure and speed, outputting the required pressure and flow rate. When the system's required flow rate changes, the servo motor's speed changes accordingly, causing the pump's displacement to change. This ensures that when the coke quencher is unloaded, the motor remains in standby mode, resulting in zero pump output. When the actuator needs to operate, it achieves "just the required amount" control, reducing high and low pressure overflow losses, completely solving the hydraulic system's overheating problem, avoiding hydraulic system leakage caused by high temperatures, reducing environmental pollution, extending the service life of seals in the hydraulic system, and saving significant amounts of electricity. This achieves a comprehensive energy-saving and emission-reduction effect, aligning with national green environmental protection policies.

[0030] 2. This invention employs novel energy-saving control technology. The hydraulic system eliminates key components such as coolers, pressure reducing valves, and proportional valves, simplifying the system's structure and reducing the system's oil contamination level from NAS1638-7 to NAS1638-9. Because the synchronous AC servo motor itself features low-speed, high-torque operation, standby capability, field weakening speed amplification, multi-speed range, and high overload capacity, the installed capacity of the hydraulic system can be reduced, the pump specifications can be lowered, and consequently, the overall hydraulic system size is reduced, improving manufacturing efficiency. Furthermore, the elimination of components such as coolers, pressure reducing valves, and proportional valves effectively reduces on-site maintenance.

[0031] 3. This invention adopts novel energy-saving control technology, which lays a certain technical foundation for the unmanned operation scheme of the coke quenching machine system in the future, and provides convenience for remote operation and maintenance and remote fault analysis in the future.

[0032] 4. In terms of the coke guide grid movement control principle of this invention, an electromagnetic reversing valve is used to replace the proportional reversing valve, and a hydraulic control check valve is added to connect the cylinder chamber and rodless chamber of the coke guide grid cylinder to form a simple and stable differential circuit, which reduces the displacement requirement of the vane pump and greatly improves the reliability of the coke quencher operation.

[0033] Based on the above reasons, this invention can be widely promoted in fields such as coke clogging machines. Attached Figure Description

[0034] To more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0035] Figure 1 This is a schematic diagram of the hydraulic system of the coke quencher pump station of the present invention.

[0036] Figure 2 This is a schematic diagram of the hydraulic system of the coke quencher valve station of the present invention.

[0037] In the diagram: 01, Oil tank; 02.1, First drain ball valve; 02.2, Second drain ball valve; 03, Level gauge; 04, Air filter; 05.1, First heater; 05.2, Second heater; 06, Pressure gauge; 07, Pressure sensor; 08.1, First servo driver; 08.2, Second servo driver; 09, Level relay; 010, Temperature sensor; 011.1, First butterfly valve; 011.2, Second butterfly valve; 012.1, First vibration isolator; 012.2, Second vibration isolator; 013.1, First pressure testing hose; 013.2 014.1 Second pressure testing hose; 014.2 First synchronous AC servo motor; 015.1 First vane pump; 015.2 Second vane pump; 016 Ball valve; 017 Manual pump; 018 First high-pressure ball valve; 019.1 First check valve; 019.2 Second check valve; 020.1 First solenoid relief valve; 020.2 Second solenoid relief valve; 021.1 First pressure testing connector; 021.2 Second pressure testing connector; 021.3 Third pressure testing connector; 021.4 Fourth pressure testing connector;

[0038] 1.2 High-pressure ball valve; 2.2 Check valve; 3.1 Pressure test connector one; 3.1 Pressure test connector one; 3.2 Pressure test connector two; 3.3 Pressure test connector three; 3.4 Pressure test connector four; 3.5 Pressure test connector five; 3.6 Pressure test connector six; 3.7 Pressure test connector seven; 3.8 Pressure test connector eight; 3.9 Pressure test connector nine; 3.10 Pressure test connector ten; 3.11 Pressure test connector eleven; 3.12 Pressure test connector twelve; 4.2 Solenoid directional valve I; 4.3 Solenoid directional valve II; 5 Stacked check valve; 6 Electro-hydraulic directional valve I; 7.1 Hydraulic control check valve I; 7.2 Hydraulic control check valve II; 8 Actuator cylinder; 9.1 9.1 Sequence Valve I; 9.2 Sequence Valve II; 9.3 Sequence Valve III; 9.4 Sequence Valve IV; 10 Electro-hydraulic Directional Valve II; 11.1 High-Pressure Ball Valve I; 11.2 High-Pressure Ball Valve II; 11.3 High-Pressure Ball Valve III; 12.1 High-Pressure Ball Valve IV; 12.2 High-Pressure Ball Valve V; 12.3 High-Pressure Ball Valve VI; 13 High-Pressure Ball Valve VII; 14 Hydraulic Controlled Check Valve; 15 Stacked Hydraulic Controlled Check Valve I; 16 Solenoid Directional Valve; 17 Stacked Hydraulic Controlled Check Valve II; 18 Stacked One-Way Throttle Valve; 19.1 High-Pressure Ball Valve VIII; 19.2 High-Pressure Ball Valve IX; 20 Door Retrieval Car Cylinder; 21.1 Coke Guide Cylinder I; 21.2 Coke Guide Cylinder II. Detailed Implementation

[0039] It should be noted that, unless otherwise specified, the embodiments and features described in the present invention can be combined with each other. The present invention will now be described in detail with reference to the accompanying drawings and embodiments.

[0040] To make the objectives, technical solutions, and advantages of the embodiments of the present invention clearer, the technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. The following description of at least one exemplary embodiment is merely illustrative and is in no way intended to limit the present invention or its application or use. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0041] It should be noted that the terminology used herein is for the purpose of describing particular embodiments only and is not intended to limit the scope of exemplary embodiments according to the invention. As used herein, the singular form is intended to include the plural form as well, unless the context clearly indicates otherwise. Furthermore, it should be understood that when the terms "comprising" and / or "including" are used in this specification, they indicate the presence of features, steps, operations, devices, components, and / or combinations thereof.

[0042] Unless otherwise specifically stated, the relative arrangement, numerical expressions, and values ​​of the components and steps set forth in these embodiments do not limit the scope of the invention. It should also be understood that, for ease of description, the dimensions of the various parts shown in the drawings are not drawn to actual scale. Techniques, methods, and devices known to those skilled in the art may not be discussed in detail, but where appropriate, such techniques, methods, and devices should be considered part of the specification. In all examples shown and discussed herein, any specific values ​​should be interpreted as merely exemplary and not as limitations. Therefore, other examples of exemplary embodiments may have different values. It should be noted that similar reference numerals and letters in the following figures denote similar items; therefore, once an item is defined in one figure, it need not be further discussed in subsequent figures.

[0043] In the description of this invention, it should be understood that the orientation or positional relationship indicated by directional terms such as "front, back, up, down, left, right", "horizontal, vertical, horizontal" and "top, bottom" is generally based on the orientation or positional relationship shown in the accompanying drawings, and is only for the convenience of describing this invention and simplifying the description. Unless otherwise stated, these directional terms do not 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 on the scope of protection of this invention. The directional terms "inner" and "outer" refer to the inner and outer contours relative to the outline of each component itself.

[0044] For ease of description, spatial relative terms such as "above," "over," "on the upper surface of," "above," etc., are used herein to describe the spatial positional relationship of a device or feature as shown in the figures to other devices or features. It should be understood that spatial relative terms are intended to encompass different orientations in use or operation besides the orientation of the device as described in the figures. For example, if the device in the figures is inverted, a device described as "above" or "above" other devices or structures would subsequently be positioned as "below" or "under" other devices or structures. Thus, the exemplary term "above" can include both "above" and "below." The device may also be positioned in other different ways (rotated 90 degrees or in other orientations), and the spatial relative descriptions used herein will be interpreted accordingly.

[0045] Furthermore, it should be noted that the use of terms such as "first" and "second" to define components is merely for the purpose of distinguishing the corresponding components. Unless otherwise stated, the above terms have no special meaning and therefore should not be construed as limiting the scope of protection of this invention.

[0046] This invention provides a hydraulic system for a coke quencher, aiming to overcome the problems of overheating and high energy loss in existing coke quencher hydraulic systems. By eliminating the use of proportional directional valves, the contamination level of the hydraulic medium can be reduced. The improved hydraulic control principle for the door trolley and coke guide grid movement enables the coke quencher to operate efficiently, stably, and in an energy-saving manner.

[0047] Based on the problems existing in the prior art, the present invention provides an improvement on the existing hydraulic system and control method for the coke quencher, solving the problems of overheating and large power loss in the existing hydraulic system, reducing the level of hydraulic medium contamination, and simplifying the hydraulic control principle of the coke quencher's door trolley and coke guide grid movement, enabling the coke quencher to operate efficiently, stably, and in an energy-saving manner.

[0048] Therefore, this invention employs a novel energy-saving control technology, utilizing an AC servo motor paired with a vane pump control principle, falling under the category of electro-hydraulic servo systems. The AC servo driver adjusts the servo motor's speed, and based on system pressure and speed feedback signals, controls and adjusts the pump's pressure and speed, outputting the required system pressure and flow. When the system's required flow changes, the servo motor's speed changes accordingly, altering the pump's displacement. This ensures that when the coke quencher is unloaded, the motor remains in standby mode, resulting in zero pump output. When the actuator operates, it achieves "just the amount needed" control, reducing high and low pressure overflow losses, lowering system heat generation, and saving energy. Furthermore, in the control principle of the coke guide grid movement, a conventional electro-hydraulic directional valve replaces the proportional directional valve, and two stacked check valves replace the two externally controlled and leaking check valves. The circuit that connects the solenoid valve to the pressure reducing valve's drain port to control whether the pressure at the pressure port is reduced is eliminated. This eliminates the need for proportional control and the pressure reduction control of the solenoid valve plus pressure reducing valve. Similarly, in the control principle of the gate retrieval trolley, a conventional electro-hydraulic directional valve replaces the proportional directional valve, eliminating the hydraulic circuit that connects the solenoid valve to the pressure reducing valve's drain port to control whether the pressure at the pressure port is reduced, and eliminating the hydraulic circuit that adds two check valves to the solenoid valve to achieve floating (the floating of the gate trolley is achieved by reversing the opening of the two hydraulically controlled check valves connected to ports A and B of the conventional electro-hydraulic directional valve, thus de-energizing the electro-hydraulic directional valve). This reduces the external design size of the valve plate, lowers product costs, and makes the control of the coke guide grid movement and the gate retrieval trolley simpler and more efficient.

[0049] The principle of the novel coke quencher hydraulic system of this invention is shown in the appendix. Figure 1 and attached Figure 2 .

[0050] Appendix Figure 1The hydraulic system of the coke quencher pump station consists of the following components, mainly including: oil tank 01, first drain ball valve 02.1, second drain ball valve 02.2, level gauge 03, air filter 04, first heater 05.1, second heater 05.2, pressure gauge 06, pressure sensor 07, first servo driver 08.1, second servo driver 08.2, level relay 09, temperature sensor 010, first butterfly valve 011.1, second butterfly valve 011.2, first vibration isolator 012.1, second vibration isolator 012.2, and first pressure measuring hose 012.2. 13.1 Second pressure testing hose 013.2 First synchronous AC servo motor 014.1 Second synchronous AC servo motor 014.2 First vane pump 015.1 Second vane pump 015.2 Ball valve 016 Manual pump 017 First high-pressure ball valve 018 First check valve 019.1 Second check valve 019.2 First solenoid relief valve 020.1 Second solenoid relief valve 020.2 First pressure testing connector 021.1 Second pressure testing connector 021.2 Third pressure testing connector 021.3 Fourth pressure testing connector 021.4.

[0051] Appendix Figure 2 The hydraulic system of the coke quencher valve station consists of the following components, mainly including: 1. High-pressure ball valve; 2. Check valve; 3. Pressure test connector 1; 3. Pressure test connector 2; 3. Pressure test connector 3; 3. Pressure test connector 4; 3. Pressure test connector 5; 3. Pressure test connector 6; 3. Pressure test connector 7; 3. Pressure test connector 8; 3. Pressure test connector 9; 3. Pressure test connector 10; 3. Pressure test connector 11; 3. Pressure test connector 12; 3. Solenoid directional valve I; 4. Solenoid directional valve II; 4. Stacked check valve; 5. Electro-hydraulic directional valve I; 6. Hydraulic control check valve I; 7.1 Hydraulic control check valve II; 7.2 Actuator cylinder; 9. Sequence valve I; 10. Sequential valve. Sequence valve II 9.2, sequence valve III 9.3, sequence valve IV 9.4, electro-hydraulic directional valve II 10, high-pressure ball valve I 11.1, high-pressure ball valve II 11.2, high-pressure ball valve III 11.3, high-pressure ball valve IV 12.1, high-pressure ball valve V 12.2, high-pressure ball valve VI 12.3, high-pressure ball valve VII 13, hydraulically controlled check valve 14, stacked hydraulically controlled check valve I 15, solenoid directional valve 16, stacked hydraulically controlled check valve II 17, stacked one-way throttle valve 18, high-pressure ball valve VIII 19.1, high-pressure ball valve IX 19.2, door retrieval trolley cylinder with displacement sensor 20, guide grid moving cylinder with displacement sensor (guide grid cylinder I 21.1, guide grid cylinder II 21.2).

[0052] Based on the characteristics of the new principle (see appendix) Figure 1In the power source design of the pump station, a synchronous AC servo motor (first synchronous AC servo motor 014.1 / second synchronous AC servo motor 014.2) is used with a vane pump (first vane pump 015.1 / second vane pump 015.2) and pressure sensor 07 to form a small closed-loop branch. Since the synchronous AC servo motor (first synchronous AC servo motor 014.1 / second synchronous AC servo motor 014.2) itself has a rotary encoder, after inputting command signals through the host PLC, the servo driver (first servo driver 08.1 / second servo driver 08.2) controls and adjusts the pressure and speed of the vane pump (first vane pump 015.1 / second vane pump 015.2) according to the pressure of the hydraulic system pump outlet pressure sensor 07 and the feedback signal of the rotary encoder built into the synchronous AC servo motor (first synchronous AC servo motor 014.1 / second synchronous AC servo motor 014.2), and outputs the pressure and flow rate actually required by the system. During servo motor control, based on PID regulation, before the set pressure is reached, the servo driver (first servo driver 08.1 / second servo driver 08.2) executes a speed closed-loop control mode, and the synchronous AC servo motor (first synchronous AC servo motor 014.1 / second synchronous AC servo motor 014.2) rotates at the set maximum speed. Once the set pressure is reached, the servo driver (first servo driver 08.1 / second servo driver 08.2) executes a pressure closed-loop control mode, and the servo system is only responsible for maintaining constant pressure while the speed adapts. Furthermore, because the synchronous AC servo motor (first synchronous AC servo motor 014.1 / second synchronous AC servo motor 014.2) itself also possesses characteristics such as low speed, standby, field weakening speed amplification, multi-stage speed, high overload capacity, and fast response, the servo motor stops rotating in standby mode when the coke quencher hydraulic system is unloaded, avoiding low-pressure overflow conditions of the large-displacement pump. Since the flow rate required for the operation of each actuator of the coke quencher is different, when the flow rate required by the system changes, the speed of the servo motor changes with the magnitude of the flow rate command, and the flow rate is adaptive. This can eliminate the high pressure overflow loss caused by the difference in flow rate for different actions. Because the characteristics of the servo motor are extremely suitable for the periodic operation process of the coke quencher, the disadvantages of the hydraulic system of the coke quencher, such as large size, high heat generation and high energy consumption, are eliminated.The oil tank 01 is equipped with a first drain ball valve 02.1, a second drain ball valve 02.2, a level gauge 03, an air filter 04, a first heater 05.1, a second heater 05.2, a level relay 09, and a temperature sensor 010. The outlet of the oil tank 01 is connected to a main pipeline, which in turn connects to multiple branch pipelines. The first branch pipeline connects to the oil inlet P via a ball valve 016, a manual pump 017, and a first high-pressure ball valve 018. The second branch pipeline connects to the first vane pump 015.1 via a first butterfly valve 011.1 and a first vibration damper 012.1. The first vane pump 015.1 is powered by a first synchronous AC servo motor. 014.1 is connected to the first servo driver 08.1, which in turn is connected to the host computer PLC. The first vane pump 015.1 is connected to the oil inlet P via the first check valve 019.1. The third branch pipeline is connected to the second vane pump 015.2 via the second butterfly valve 011.2 and the second vibration damper 012.2. The second vane pump 015.2 is connected to the second servo driver 08.2 via the second synchronous AC servo motor 014.2, which in turn is connected to the host computer PLC. The second vane pump 015.2 is connected to the oil inlet P via the second check valve 019.2. The first vane pump 015... One end of the pipeline between the first check valve 019.1 and the second check valve 019.2 is connected to the first pipeline. The other end of the first pipeline is connected to the pipeline between the second vane pump 015.2 and the second check valve 019.2. A first electromagnetic relief valve 020.1 is connected to the first pipeline near the first check valve 019.1, and a second electromagnetic relief valve 020.2 is connected to the first electromagnetic relief valve 020.1 near the second check valve 019.2. A first pressure testing connector 021.1 is connected between the first electromagnetic relief valve 020.1 and the first check valve 019.1, and a third pressure testing connector 021 is connected between the second electromagnetic relief valve 020.2 and the second check valve 019.2. 3; Pressure gauge 06 is connected to one end of the first pressure measuring hose 013.1, and the other end of the first pressure measuring hose 013.1 is connected to the second pressure measuring connector 021.2. The second pressure measuring connector 021.2 is connected to the pipeline between the first one-way valve 019.1 and the oil inlet P; Pressure sensor 07 is connected to one end of the second pressure measuring hose 013.2, and the other end of the second pressure measuring hose 013.2 is connected to the fourth pressure measuring connector 021.4. The fourth pressure measuring connector 021.4 is connected to the pipeline between the second one-way valve 019.2 and the oil inlet P; Pressure sensor 07 is also connected to the first servo driver 08.1 and the second servo driver 08.2.

[0053] Based on the characteristics of the new principle (see appendix) Figure 2The gate trolley's forward and backward control circuit does not require additional pressure reducing valves, proportional directional valves to adjust the gate trolley's forward and backward speeds, or independent components to achieve its floating mechanism. Due to the use of a servo motor closed-loop system, after inputting command signals via the host PLC, it provides the appropriate flow and pressure according to the actual needs of the gate trolley's cylinders. This reduces pressure differential loss from the pressure reducing valve, reduces system heat generation, and simplifies the complex control of the proportional valve. Specifically, the A and B chambers of the electro-hydraulic directional valve I6 are connected to the A ports of the externally controlled, externally leaking hydraulic check valves I7.1 and II7.2, respectively. The B ports of the hydraulic check valves I7.1 and II7.2 are connected to the A ports of the sequence valves I9.1 and II9.2, respectively. The B ports of the sequence valves I9.1 and II9.2 are connected to the rodless and rod-side chambers of the gate trolley cylinder 20 via high-pressure ball valves 11.1 and 12.1, respectively. The A and B ports of the electromagnetic directional valve I 4.2 are connected to the Y and X ports of the hydraulic control check valve I 7.1 and the hydraulic control check valve II 7.2, respectively.

[0054] Based on the characteristics of the new principle (see appendix) Figure 2 The guide grid movement control circuit does not require an additional pressure reducing valve or a proportional directional valve to adjust the advance and retreat speed of the guide grid cylinder. Due to the use of a servo motor closed-loop system, after inputting command signals through the host PLC, it provides the appropriate flow and pressure according to the actual needs of the guide grid cylinder. This reduces the pressure difference loss of the pressure reducing valve, reduces system heat generation, and also reduces the complexity of proportional valve control. Specifically, the electro-hydraulic directional valve II10 is stacked with a superimposed hydraulic control check valve I15 and a superimposed check valve 5. The B port of the superimposed hydraulic control check valve I15 and the B port of the superimposed check valve 5 are connected to the A ports of sequence valve III9.3 and sequence valve IV9.4, respectively. The B ports of sequence valves III9.3 and IV9.4 are connected to the rodless and rod-side chambers of the two guide grid cylinders through high-pressure ball valves II11.2, III11.3, V12.2, and VI12.3, respectively. The A port of the hydraulic control check valve 14 is connected to the rodless chamber of the two coking grid cylinders, and the B port of the hydraulic control check valve 14 is connected to the rod chamber of the two coking grid cylinders (coking grid cylinder I 21.1 and coking grid cylinder II 21.2). The B port of the solenoid directional valve II 4.3 is connected to the X port of the hydraulic control check valve 14 through the high-pressure ball valve 7 13 to control whether the hydraulic oil in the rod chamber of the coking grid can flow back to the rodless chamber of the coking grid.

[0055] The remaining actuators of the coke quencher hydraulic system, referring to the control circuit of the actuators, consist of actuator cylinder 8, solenoid directional valve 16, stacked hydraulic control check valve II 17, stacked one-way throttle valve 18, and high-pressure ball valve 8 19.1 and high-pressure ball valve 9 19.2. The P and T ports of the solenoid directional valve 16 are connected to the pump station hydraulic system; the A and B ports of the solenoid directional valve 16 are connected to the stacked hydraulic control check valve II 17; the stacked hydraulic control check valve II 17 is connected to the stacked one-way throttle valve 18; the stacked one-way throttle valve 18 is connected to the high-pressure ball valve 8 19.1 and high-pressure ball valve 9 19.2; and the high-pressure ball valve 8 19.1 and high-pressure ball valve 9 19.2 are connected to the rodless chamber and rod chamber of actuator cylinder 8, respectively.

[0056] The P port of the pump station's hydraulic system is connected to the P ports of solenoid directional valves I 4.2, II 4.3, I 6, II 10, and 16 via high-pressure ball valve 1.2. The T port of the pump station's hydraulic system is connected to the T ports of solenoid directional valves I 4.2, II 4.3, I 6, II 10, and 16 via check valve 2.2.

[0057] Because proportional control has been eliminated in the entire coke quencher control system, the contamination level of the hydraulic medium in the coke quencher hydraulic system has been directly reduced from NAS1638-7 to NAS1638-9, which greatly improves the performance of the entire coke quencher hydraulic system and reduces maintenance costs.

[0058] The detailed control process of the hydraulic cylinder of the gate-removing trolley in the hydraulic system of the coke quencher of this invention is as follows:

[0059] According to the appendix Figure 2As shown, the host PLC inputs pressure P1 and flow rate Q1 commands to the servo driver, energizing electromagnets YH01 (or YH02) and YH2b, and electromagnet YH1a. Hydraulic check valves I 7.1 and II 7.2 open in reverse, extending the door trolley cylinder 20 (a door trolley cylinder with a displacement sensor). Based on PID control, before reaching the set pressure, the servo driver executes a speed closed-loop control mode, causing the synchronous AC servo motor to operate at the set high speed. When the door trolley cylinder 20 extends to a set position close to the furnace door, the displacement sensor of the door trolley cylinder 20 sends a signal, and the synchronous AC servo motor rotates at a set low speed and low pressure to prevent excessive pressure from damaging the furnace frame. When the door trolley cylinder 20 extends to the set position, the displacement sensor of the door trolley cylinder 20 sends a signal, and electromagnets YH01 (or YH02) and YH2b are de-energized, and electromagnet YH1a is de-energized, and the door trolley cylinder 20 stops operating. When electromagnets YH01 (or YH02) and YH2a are energized, and electromagnet YH1a is energized, hydraulic check valves I 7.1 and II 7.2 open in reverse, and the trolley cylinder 20 retracts. According to PID regulation, before the set pressure is reached, the servo driver 8 executes the speed closed-loop control mode, and the synchronous AC servo motor 14 rotates at the set speed. When the trolley cylinder 20 retracts to the set position, the displacement sensor of the trolley cylinder 20 sends a signal, and electromagnets YH01 (or YH02) and YH2a are de-energized, and electromagnet YH1a is de-energized, and the trolley cylinder 20 stops moving. When the trolley cylinder 20 needs to float backward, the electro-hydraulic directional valve I6 is de-energized and in the neutral position. The oil ports A, B, and T of the electro-hydraulic directional valve I6 are connected, the electromagnet YH1a is energized, and the hydraulic control check valves I7.1 and II7.2 open in reverse. At this time, the rod chamber and rodless chamber of the trolley cylinder 20 are connected through the A, B, and T ports of the electro-hydraulic directional valve I6 to achieve the floating function.

[0060] The detailed control method for moving the coke guide grid cylinders I 21.1 and II 21.2 (both are coke guide grid moving cylinders equipped with displacement sensors) in the hydraulic system of the coke quencher is as follows:

[0061] According to the appendix Figure 2As shown, the host PLC inputs pressure P1 and flow rate Q1 commands to the servo driver, energizing electromagnets YH01 (or YH02) and YH3b, and electromagnet YH4a. The hydraulic check valve 14 opens in reverse, extending the coke guide cylinders I 21.1 and II 21.2. According to PID regulation, before reaching the set pressure, the servo driver executes the speed closed-loop control mode, and the synchronous AC servo motor rotates at the set high speed. The hydraulic oil in the rod chambers of coke guide cylinders I 21.1 and II 21.2 enters the rodless chambers of coke guide cylinders I 21.1 and II 21.2 through the hydraulic check valve 14, thus forming a differential circuit and reducing the displacement requirement of the vane pump. When the coke guide cylinder I 21.1 and coke guide cylinder II 21.2 extend to the set position, the synchronous AC servo motor rotates at the set low speed and low pressure to prevent excessive pressure from damaging the furnace frame. When the coke guide cylinder I 21.1 and coke guide cylinder II 21.2 extend to the set position, the displacement sensors of the coke guide cylinder I 21.1 and coke guide cylinder II 21.2 send signals, electromagnets YH01 (or YH02) and YH3b are de-energized, electromagnet YH4a is de-energized, and the coke guide cylinder I 21.1 and coke guide cylinder II 21.2 stop operating. When electromagnets YH01 (or YH02) and YH3a are energized, and electromagnet YH4a is de-energized, the hydraulic check valve 14 closes in the reverse direction, and the coke guide cylinders I 21.1 and II 21.2 retract. According to PID regulation, before the set pressure is reached, the servo drive executes the speed closed-loop control mode, and the synchronous AC servo motor rotates at the set speed. When the coke guide cylinders I 21.1 and II 21.2 retract to the set position, the displacement sensors of the coke guide cylinders I 21.1 and II 21.2 send signals, electromagnets YH01 (or YH02) and YH3a are de-energized, and the coke guide cylinders I 21.1 and II 21.2 stop operating.

[0062] This invention is applicable to the hydraulic system of coke quenchers in various coke oven equipment of 7 meters and above. The technology of this invention can be widely applied to the renovation of existing coke quenchers and the installation of new equipment. It ensures system reliability and effectively reduces related maintenance and replacement costs caused by system overheating, including labor costs, hoisting costs, and spare parts procurement costs. Simultaneously, due to the reduced failure rate, high energy efficiency, and environmental friendliness of this type of product, it directly enhances the company's reputation in the coke quencher supply field and strengthens the company's core competitiveness.

[0063] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of the present invention, and not to limit them; although the present invention has been described in detail with reference to the foregoing embodiments, those skilled in the art should understand that modifications can still be made to the technical solutions described in the foregoing embodiments, or equivalent substitutions can be made to some or all of the technical features; and these modifications or substitutions do not cause the essence of the corresponding technical solutions to deviate from the scope of the technical solutions of the embodiments of the present invention.

Claims

1. A hydraulic system for a pusher, characterized in that, include: The pump station hydraulic system and the valve station hydraulic system connected to the pump station hydraulic system, wherein the pump station hydraulic system includes at least a servo driver connected to a host computer PLC, a synchronous AC servo motor connected to the servo driver, a vane pump connected to the synchronous AC servo motor, and a pressure sensor (07) connected to the servo driver. The synchronous AC servo motor, the vane pump, and the pressure sensor (07) form a small closed-loop branch. The synchronous AC servo motor is equipped with a rotary encoder. After the host computer PLC inputs the command signal, the servo driver controls and adjusts the pressure and speed of the vane pump according to the pressure of the hydraulic system pump outlet pressure sensor (07) and the feedback signal of the rotary encoder of the synchronous AC servo motor, and outputs the pressure and flow rate actually required by the system. The valve station hydraulic system includes a gate trolley advance and retreat control circuit, a coke guide grid movement control circuit, and at least one actuator circuit. The gate retrieval trolley forward and backward control circuit includes an electromagnetic directional valve I (4.2), an electro-hydraulic directional valve I (6), a hydraulically controlled check valve I (7.1), a hydraulically controlled check valve II (7.2), a sequence valve I (9.1), a sequence valve II (9.2), a high-pressure ball valve I (11.1), a high-pressure ball valve IV (12.1), and a gate retrieval trolley cylinder (20). The electromagnetic directional valve I (4.2) and the electro-hydraulic directional valve I (6) are connected to the pump station hydraulic system; the electromagnetic directional valve I (4.2) and the hydraulically controlled check valve I (7.1) are connected to the hydraulically controlled check valve I (7.2). 7.1) and hydraulic check valve II (7.2) are connected. The electro-hydraulic directional valve I (6) is connected to hydraulic check valve I (7.1) and hydraulic check valve II (7.2). The hydraulic check valve I (7.1) is connected to the rodless chamber of the door retrieval trolley cylinder (20) in sequence through sequence valve I (9.1) and high-pressure ball valve I (11.1). The hydraulic check valve II (7.2) is connected to the rod chamber of the door retrieval trolley cylinder (20) in sequence through sequence valve II (9.2) and high-pressure ball valve IV (12.1). The coke guide grid movement control circuit includes an electromagnetic directional valve II (4.3), a stacked check valve (5), a sequence valve III (9.3), a sequence valve IV (9.4), an electro-hydraulic directional valve II (10), a stacked hydraulically controlled check valve I (15), a high-pressure ball valve II (11.2), a high-pressure ball valve III (11.3), a high-pressure ball valve V (12.2), a high-pressure ball valve VI (12.3), a hydraulically controlled check valve (14), a coke guide grid cylinder I (21.1), and a coke guide grid cylinder II (21.2). The electro-hydraulic directional valve II (10) and the electromagnetic directional valve II (4.3) are connected to the pump station hydraulic system. The electro-hydraulic directional valve II (10) is stacked with the stacked hydraulically controlled check valve I (15) and the stacked check valve (5). The stacked hydraulically controlled check valve I (15) is connected to the sequence valve III (9.3). Sequence valve III (9.3) is connected to the rodless chambers of coke grid cylinder I (21.1) and coke grid cylinder II (21.2) via high-pressure ball valve II (11.2) and high-pressure ball valve III (11.3), respectively; the superimposed check valve (5) is connected to sequence valve IV (9.4), and the sequence valve IV (9.4) is connected to the rod chambers of coke grid cylinder I (21.1) and coke grid cylinder II (21.2) via high-pressure ball valve V (12.2) and high-pressure ball valve VI (12.3), respectively; the hydraulically controlled check valve (14) is connected to the rodless chamber and the rod chamber of coke grid cylinder I (21.1) and coke grid cylinder II (21.2); the electromagnetic directional valve II (4.3) is connected to the hydraulically controlled check valve (14) to control whether the hydraulic oil in the rod chamber of the coke grid cylinder can flow back to the rodless chamber of the coke grid cylinder.

2. The hydraulic system for the coke quencher according to claim 1, characterized in that, During the control of the synchronous AC servo motor, according to PID regulation, before the set pressure is reached, the servo driver executes the speed closed-loop control mode, and the synchronous AC servo motor rotates at the set maximum speed; when the set pressure is reached, the servo driver executes the pressure closed-loop control mode, and the servo system is only responsible for maintaining constant pressure and adaptive speed. When the hydraulic system of the coke quencher is unloaded, the synchronous AC servo motor stops rotating. Since the flow required for the operation of each actuator of the coke quencher is different, when the flow required by the system changes, the speed of the synchronous AC servo motor changes with the magnitude of the flow command, and the flow is adaptive.

3. The hydraulic system for the coke quencher according to claim 2, characterized in that, The hydraulic system of the pump station includes an oil tank (01), a first drain ball valve (02.1), a second drain ball valve (02.2), a level gauge (03), an air filter (04), a first heater (05.1), a second heater (05.2), a pressure gauge (06), a pressure sensor (07), a first servo driver (08.1), a second servo driver (08.2), a level relay (09), a temperature sensor (010), a first butterfly valve (011.1), a second butterfly valve (011.2), a first vibration isolator (012.1), a second vibration isolator (012.2), a first pressure testing hose (013.1), a second pressure testing hose (013.2), a first synchronous AC servo motor (014.1), and a second synchronous AC servo motor (014.2). The system includes a first vane pump (015.1), a second vane pump (015.2), a ball valve (016), a manual pump (017), a first high-pressure ball valve (018), a first check valve (019.1), a second check valve (019.2), a first electromagnetic overflow valve (020.1), a second electromagnetic overflow valve (020.2), a first pressure test connector (021.1), a second pressure test connector (021.2), a third pressure test connector (021.3), and a fourth pressure test connector (021.4). The oil tank (01) is equipped with a first drain ball valve (02.1), a second drain ball valve (02.2), a level gauge (03), an air filter (04), a first heater (05.1), a second heater (05.2), a level relay (09), and a temperature sensor (010). The outlet of the oil tank (01) is connected to a main pipeline, which is connected to multiple branch pipelines, among which... A branch pipeline is connected to the oil inlet P in sequence through a ball valve (016), a manual pump (017), and a first high-pressure ball valve (018); A branch pipeline is connected to a first vane pump (015.1) via a first butterfly valve (011.1) and a first vibration damper (012.1). The first vane pump (015.1) is connected to a first servo driver (08.1) via a first synchronous AC servo motor (014.1). The first servo driver (08.1) is connected to a host computer PLC. The first vane pump (015.1) is connected to the oil inlet P via a first check valve (019.1). A branch pipeline is connected to a second vane pump (015.2) via a second butterfly valve (011.2) and a second vibration damper (012.2). The second vane pump (015.2) is connected to a second servo driver (08.2) via a second synchronous AC servo motor (014.2). The second servo driver (08.2) is connected to a host computer PLC. The second vane pump (015.2) is connected to the oil inlet P via a second check valve (019.2). The pipeline between the first vane pump (015.1) and the first check valve (019.1) is connected to one end of the first pipeline, and the other end of the first pipeline is connected to the pipeline between the second vane pump (015.2) and the second check valve (019.2). A first electromagnetic relief valve (020.1) is connected to the first pipeline near the first check valve (019.1), and a second electromagnetic relief valve (020.2) is connected to the first pipeline near the second check valve (019.2). A first pressure test connector (021.1) is connected between the first electromagnetic relief valve (020.1) and the first check valve (019.1), and a third pressure test connector (021.3) is connected between the second electromagnetic relief valve (020.2) and the second check valve (019.2). The pressure gauge (06) is connected to one end of the first pressure measuring hose (013.1), the other end of the first pressure measuring hose (013.1) is connected to the second pressure measuring connector (021.2), and the second pressure measuring connector (021.2) is connected to the pipeline between the first check valve (019.1) and the oil inlet P; The pressure sensor (07) is connected to one end of the second pressure measuring hose (013.2), and the other end of the second pressure measuring hose (013.2) is connected to the fourth pressure measuring connector (021.4). The fourth pressure measuring connector (021.4) is connected to the pipeline between the second one-way valve (019.2) and the oil inlet P. The pressure sensor (07) is also connected to the first servo driver (08.1) and the second servo driver (08.2).

4. The hydraulic system for the coke quencher according to claim 3, characterized in that, The P and T chambers of the electro-hydraulic directional valve I (6) are connected to the hydraulic system of the pump station. The A and B chambers of the electro-hydraulic directional valve I (6) are respectively connected to the A ports of the externally controlled and leaking hydraulic check valve I (7.1) and hydraulic check valve II (7.2). The B ports of the hydraulic check valve I (7.1) and hydraulic check valve II (7.2) are respectively connected to the A ports of the sequence valve I (9.1) and sequence valve II (9.2). The B port of the sequence valve II (9.2) is connected to the rodless chamber and rod chamber of the trolley cylinder (20) through the high-pressure ball valve I (11.1) and the high-pressure ball valve IV (12.1), respectively; the A port and B port of the electromagnetic directional valve I (4.2) are connected to the Y port and X port of the hydraulic control check valve I (7.1) and the hydraulic control check valve II (7.2), respectively; the P port and T port of the electromagnetic directional valve I (4.2) are connected to the pump station hydraulic system.

5. The hydraulic system for the coke quencher according to claim 3, characterized in that, The P and T ports of the electro-hydraulic directional valve II (10) are connected to the hydraulic system of the pump station; the electro-hydraulic directional valve II (10) is connected to the stacked hydraulic control check valve I (15) and the stacked check valve (5); the B port of the stacked hydraulic control check valve I (15) is connected to the A port of the sequence valve III (9.3), and the B port of the sequence valve III (9.3) is connected to the rodless chambers of the coking grid cylinder I (21.1) and the coking grid cylinder II (21.2) through the high-pressure ball valve II (11.2) and the high-pressure ball valve III (11.3); the B port of the stacked check valve (5) is connected to the A port of the sequence valve IV (9.4), and the B port of the sequence valve IV (9.4) is connected to the rodless chambers of the coking grid cylinder I (21.1) and the coking grid cylinder II (21.2) through the high-pressure ball valve II (11.2) and the high-pressure ball valve III (11.3) respectively; The high-pressure ball valve five (12.2) and high-pressure ball valve six (12.3) are connected to the rod chambers of the coking grid cylinder I (21.1) and the coking grid cylinder II (21.2); the A port of the hydraulic control check valve (14) is connected to the rodless chambers of the coking grid cylinder I (21.1) and the coking grid cylinder II (21.2), and the B port of the hydraulic control check valve (14) is connected to the rod chambers of the coking grid cylinder I (21.1) and the coking grid cylinder II (21.2); the B port of the electromagnetic directional valve II (4.3) is connected to the X port of the hydraulic control check valve (14) through the high-pressure ball valve seven (13), and the P port and T port of the electromagnetic directional valve II (4.3) are connected to the pump station hydraulic system.

6. The hydraulic system for the coke quencher according to claim 3, characterized in that, The actuator circuit includes an actuator cylinder (8), an electromagnetic directional valve (16), a stacked hydraulic control check valve II (17), a stacked one-way throttle valve (18), and high-pressure ball valve eight (19.1) and high-pressure ball valve nine (19.2). The P port and T port of the electromagnetic directional valve (16) are connected to the pump station hydraulic system. The A port and B port of the electromagnetic directional valve (16) are connected to the stacked hydraulic control check valve II (17). The stacked hydraulic control check valve II (17) is connected to the stacked one-way throttle valve (18). The stacked one-way throttle valve (18) is connected to the high-pressure ball valve eight (19.1) and the high-pressure ball valve nine (19.2). The high-pressure ball valve eight (19.1) and the high-pressure ball valve nine (19.2) are connected to the rodless chamber and the rod chamber of the actuator cylinder (8), respectively.

7. The hydraulic system for the coke quencher according to claim 4, characterized in that, The door retrieval trolley cylinder (20) is equipped with a displacement sensor.

8. The hydraulic system for a coke quencher according to claim 5, characterized in that, Both the coking grid cylinder I (21.1) and the coking grid cylinder II (21.2) are equipped with displacement sensors.

9. A control method for the hydraulic system of a coke quencher as described in any one of claims 1-8, characterized in that, The control for moving the door retrieval trolley forward and backward includes the following steps: The host PLC inputs pressure P1 and flow Q1 commands to the servo drive, energizing electromagnets YH01 / YH02 and YH2b, and electromagnet YH1a. Hydraulic check valves I (7.1) and II (7.2) open in reverse, and the trolley cylinder (20) extends. According to PID control, before reaching the set pressure, the servo drive executes a speed closed-loop control mode, and the synchronous AC servo motor rotates at the set high speed. When the trolley cylinder (20) extends to the distance... When the furnace door is near the set position, the displacement sensor of the door trolley cylinder (20) sends a signal, and the synchronous AC servo motor rotates at the set low speed and low pressure to prevent the furnace frame from being damaged by excessive pressure. When the door trolley cylinder (20) extends to the set position, the displacement sensor of the door trolley cylinder (20) sends a signal, and the electromagnets YH01 / YH02 and YH2b are de-energized, the electromagnet YH1a is de-energized, and the door trolley cylinder (20) stops operating; the electromagnets YH01 / YH02 and YH2b are de-energized, and the door trolley cylinder (20) stops operating; When 2a is energized, electromagnet YH1a is energized, and hydraulic check valve I (7.1) and hydraulic check valve II (7.2) open in reverse, causing the door trolley cylinder (20) to retract. According to PID regulation, before the set pressure is reached, the servo drive executes the speed closed-loop control mode, and the synchronous AC servo motor rotates at the set speed. When the door trolley cylinder (20) retracts to the set position, the displacement sensor of the door trolley cylinder (20) sends a signal, and electromagnets YH01 / YH02 and YH2a lose power. When the electromagnet YH1a is de-energized, the trolley cylinder (20) stops moving. When the trolley cylinder (20) needs to float backward, the electro-hydraulic directional valve I (6) is de-energized and in the neutral position. The oil ports A, B, and T of the electro-hydraulic directional valve I (6) are connected, the electromagnet YH1a is energized, and the hydraulic control check valve I (7.1) and hydraulic control check valve II (7.2) open in reverse. At this time, the rod chamber and rodless chamber of the trolley cylinder (20) are connected through the A, B, and T ports of the electro-hydraulic directional valve I (6) to achieve the floating function.

10. A control method for the hydraulic system of a coke quencher as described in any one of claims 1-8, characterized in that, To achieve the movement of the focus guide grid, the following steps are included: The host computer PLC inputs pressure P1 and flow Q1 commands to the servo drive, energizing electromagnets YH01 / YH02 and YH3b, and electromagnet YH4a. The hydraulic check valve (14) opens in reverse, and the coking grid cylinder I (21.1) and coking grid cylinder II (21.2) extend. According to PID regulation, before the set pressure is reached, the servo drive executes the speed closed-loop control mode, and the synchronous AC servo motor rotates at the set high speed. The coking grid cylinder I (21.1) and coking grid cylinder II (21.2) extend. 1.2) The hydraulic oil in the rod chamber of the coke grid cylinder I (21.1) and the rodless chamber of the coke grid cylinder II (21.2) enters through the hydraulic control check valve (14) to form a differential circuit, reducing the displacement requirement of the vane pump; when the coke grid cylinder I (21.1) and the coke grid cylinder II (21.2) extend to the set position, the synchronous AC servo motor rotates at the set low speed and low pressure to prevent the furnace frame from being damaged by excessive pressure. When the position is fixed, the displacement sensors of the coking grid cylinder I (21.1) and the coking grid cylinder II (21.2) send signals, the electromagnets YH01 / YH02 and YH3b are de-energized, the electromagnet YH4a is de-energized, and the coking grid cylinders I (21.1) and II (21.2) stop operating; the electromagnets YH01 / YH02 and YH3a are energized, the electromagnet YH4a is de-energized, the hydraulic check valve (14) closes in the reverse direction, and the coking grid cylinders I (21.1) and II (21.2) retract. According to PID regulation, before the set pressure is reached, the servo drive executes the speed closed-loop control mode, and the synchronous AC servo motor rotates at the set speed. When the coking grid cylinder I (21.1) and the coking grid cylinder II (21.2) retract to the set position, the displacement sensors of the coking grid cylinder I (21.1) and the coking grid cylinder II (21.2) send a signal, the electromagnets YH01 / YH02 and YH3a are de-energized, and the coking grid cylinder I (21.1) and the coking grid cylinder II (21.2) stop moving.

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