Hydraulic control system of slewing mechanism and tunneling equipment

Abstract

The application relates to the technical field of mine tunneling construction equipment, in particular to a rotary mechanism hydraulic control system and tunneling equipment. The rotary mechanism hydraulic control system comprises a main oil supply reversing circuit, a start-stop control circuit, a first oil cylinder, a second oil cylinder, a first buffer brake circuit and a second buffer brake circuit. A first circuit component comprises a first balance valve and a second balance valve connected in parallel between a first main oil port and a second oil port, and the flow of the second balance valve is greater than that of the first balance valve. A second circuit component comprises a third balance valve and a fourth balance valve connected in parallel between a second main oil port and a first oil port, and the flow of the fourth balance valve is greater than that of the third balance valve. According to the rotary mechanism hydraulic control system and the tunneling equipment, the flow regulation range of the rotary mechanism is widened, wide-range speed regulation is realized, and the rotary mechanism of the mine tunneling equipment can stably run under the complex tunneling working conditions of high-frequency start-stop and wide-range speed regulation.

Description

Technical Field

[0001] This application relates to the field of mining tunnel excavation equipment technology, and in particular to a hydraulic control system for a rotary mechanism and tunneling equipment. Background Technology

[0002] Rapid rock-breaking tunneling equipment in mining includes types such as horizontal axis roadheaders, vertical axis roadheaders, roller crusher roadheaders, and disc vibratory crusher roadheaders. These machines are generally equipped with a cutting boom featuring a slewing support. The movement of the front cutterhead is controlled by the linkage between the slewing mechanism and the boom, completing the tunnel rock-breaking operation. Currently, most engineering machinery slewing mechanisms use traditional valve-controlled hydraulic control systems. These systems utilize conventional directional valves, fixed damping buffer valves, and pressure compensation structures to achieve slewing speed regulation and start / stop control. Such systems have fixed valve openings, limited flow regulation range, and insufficient speed adaptation capability. Furthermore, slewing start / stop impacts are significant, braking vibrations are substantial, and system parameters are calibrated according to rated load, resulting in a single adjustment method that is difficult to adapt to alternating no-load, light-load, and heavy-load conditions. Under complex conditions where wide-range speed regulation and variable load coexist, system pressure and flow are prone to coupling interference. Heavy-load low-speed slewing is prone to power lag, while light-load high-speed slewing experiences intensified impacts and poor anti-disturbance performance. The rock at the mine tunnel excavation site has uneven distribution of soft and hard materials, the excavation load fluctuates drastically, the equipment rotation action starts and stops frequently and the speed adjustment range is large, and the requirements for the continuity of excavation are high. The existing rotary hydraulic control system is difficult to meet the actual use requirements of smooth start and stop and stable operation of the rotary mechanism under complex mine tunneling conditions. Summary of the Invention

[0003] The purpose of this application is to provide a hydraulic control system and a slewing mechanism for a slewing mechanism, in order to address, to some extent, the existing problems in the current engineering machinery slewing mechanisms, which mostly adopt traditional valve-controlled hydraulic control systems. These systems rely on conventional directional valves, fixed damping buffer valves, and pressure compensation structures to achieve slewing speed regulation and start / stop control. Such systems have fixed valve openings, limited flow regulation ranges, and insufficient speed regulation adaptability. At the same time, the slewing start / stop impact is obvious, and the braking vibration is large. Furthermore, the system parameters are calibrated according to the rated load, and the adjustment method is singular, making it difficult to adapt to the alternating working conditions of no-load, light-load, and heavy-load. Under the complex working conditions of wide-range speed regulation and variable load, the system pressure and flow are prone to coupling interference. Heavy-load low-speed slewing is prone to power lag, and light-load high-speed slewing impact is aggravated, resulting in poor anti-disturbance performance. The uneven distribution of rock hardness at the mine tunnel excavation site, the drastic fluctuation of the excavation load, the frequent start-stop and large speed adjustment of the equipment rotation, and the high requirements for the continuity of excavation pose technical challenges. Existing rotary hydraulic control systems are unable to meet the actual needs of smooth start-stop and stable operation of the rotary mechanism under complex mine tunneling conditions.

[0004] According to a first aspect of this application, a hydraulic control system for a rotary mechanism is provided for controlling a rotary table. The hydraulic control system for the rotary mechanism includes a main oil supply reversing circuit, a start-stop control circuit, a first oil cylinder, a second oil cylinder, a first buffer brake circuit, and a second buffer brake circuit. Both the first and second hydraulic cylinders are rotary hydraulic cylinders. Each rotary hydraulic cylinder includes a cylinder body and a piston. The piston divides the cylinder body into a first chamber and a second chamber. The pistons of the first and second hydraulic cylinders are respectively connected to the two ends of the rotary table to drive the rotary table to perform a rotary action. The first buffer braking circuit is connected to the second chamber of the first cylinder and the second buffer braking circuit is connected to the second chamber of the second cylinder; The start-stop control circuit includes a balance brake valve assembly, which includes a first main oil port, a second main oil port, a first circuit assembly, a second circuit assembly, a first oil passage port, and a second oil passage port. The first main oil port and the second main oil port are respectively connected to the main oil supply reversing circuit. The first oil passage port is connected to the first chamber of the first cylinder, and the second oil passage port is connected to the first chamber of the second cylinder. The first circuit assembly is connected between the first main oil port and the second oil passage port, and the second circuit assembly is connected between the second main oil port and the first oil passage port. The first circuit assembly includes a first balancing valve and a second balancing valve connected in parallel between the first main oil port and the second oil outlet, wherein the flow rate of the second balancing valve is greater than that of the first balancing valve. The second circuit assembly includes a third balance valve and a fourth balance valve connected in parallel between the second main oil port and the first oil outlet, wherein the flow rate of the fourth balance valve is greater than that of the third balance valve.

[0005] Preferably, the balance brake valve assembly further includes a first one-way throttle valve and a second one-way throttle valve; The oil inlet of the first one-way throttle valve is connected to the first main oil port, and the oil outlet of the first one-way throttle valve is connected to the pilot port of the third balance valve. The oil inlet of the second one-way throttle valve is connected to the second main oil port, and the oil outlet of the second one-way throttle valve is connected to the pilot port of the first balance valve.

[0006] Preferably, the balance brake valve assembly further includes a first check valve and a second check valve; The inlet end of the first check valve is connected to the first main oil port, and the outlet end of the first check valve is connected to the main oil supply ports of both the third balance valve and the fourth balance valve. The pilot port of the second balancing valve is connected downstream of the first check valve; The inlet end of the second check valve is connected to the second main oil port, and the outlet end of the second check valve is connected to the main oil supply ports of both the first balance valve and the second balance valve. The pilot port of the fourth balancing valve is connected downstream of the second check valve.

[0007] Preferably, the balance brake valve assembly further includes damping; The damping is provided both upstream and downstream of the connection point between the pilot port of the second balancing valve and the downstream of the first check valve; And / or, the damping is provided both upstream and downstream of the connection point where the pilot port of the fourth balancing valve is connected to the downstream of the second one-way valve.

[0008] Preferably, both the first buffer braking circuit and the second buffer braking circuit are safety circuits; The safety circuit includes a pressure relief branch, an oil discharge port, and a first overflow valve, wherein the first overflow valve is disposed in the pressure relief branch; The pressure relief branch connects the unloading port and the second chamber of the first cylinder, or the pressure relief branch connects the unloading port and the second chamber of the second cylinder.

[0009] Preferably, the start-stop control circuit further includes a second overflow valve, a third overflow valve, a first unloading circuit, a second unloading circuit, and a main unloading port; The first unloading circuit is connected to the first buffer braking circuit and the main unloading port; The second unloading circuit is connected to the second buffer brake circuit and the main unloading port; The second overflow valve is located in the first oil unloading circuit, and the third overflow valve is located in the second oil unloading circuit.

[0010] Preferably, the safety circuit further includes an explosion-proof circuit and an explosion-proof valve, the explosion-proof valve being disposed in the explosion-proof circuit, the explosion-proof circuit being connected to the second chamber of the first oil cylinder and the first oil unloading circuit, or the explosion-proof circuit being connected to the second chamber of the second oil cylinder and the second oil unloading circuit.

[0011] Preferably, it also includes a low-pressure oil source, and the safety circuit further includes a pressure stabilizing branch and a third check valve. The third check valve is disposed in the pressure stabilizing branch, and the outlet end of the third check valve is disposed on the side close to the low-pressure oil source. The pressure stabilizing branch is connected to the low-pressure oil source and the second chamber of the first oil cylinder, or the pressure stabilizing branch is connected to the low-pressure oil source and the second chamber of the second oil cylinder.

[0012] Preferably, the main oil supply reversing circuit includes at least one set of load-sensitive multi-way valves.

[0013] According to a second aspect of this application, a tunneling equipment is provided, including the aforementioned rotary table and the rotary mechanism hydraulic control system described in any of the aforementioned technical solutions. Therefore, it has all the beneficial technical effects of the rotary mechanism hydraulic control system, which will not be repeated here.

[0014] Compared with the prior art, the beneficial effects of this application are as follows: The hydraulic control system for the slewing mechanism provided in this application uses a first circuit component with a small-flow first balancing valve and a large-flow second balancing valve connected in parallel, and a second circuit component with a small-flow third balancing valve and a large-flow fourth balancing valve connected in parallel. On the one hand, it can match the system output flow by combining balancing valves of different specifications, widen the flow adjustment range of the slewing mechanism, realize wide-range speed regulation, and adapt to the variable slewing speed requirements during tunneling. On the other hand, it can automatically form differentiated flow supply according to the load size. Under heavy load conditions, the large-flow balancing valve ensures sufficient slewing power, while under light load conditions, the small-flow balancing valve suppresses slewing impact, effectively reducing the shaking phenomenon during slewing start-stop phase, improving the system's adaptability to various variable load conditions such as no-load, light-load, and heavy-load, alleviating the problem of system pressure and flow coupling interference, and ensuring the stable operation of the slewing mechanism of mining tunneling equipment under complex tunneling conditions of high-frequency start-stop and wide-frequency speed regulation.

[0015] To make the above-mentioned objectives, features and advantages of this application more apparent and understandable, preferred embodiments are described below in detail with reference to the accompanying drawings. Attached Figure Description

[0016] To more clearly illustrate the technical solutions in the specific embodiments of this application or the prior art, the drawings used in the description of the specific embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are some embodiments of this application. For those skilled in the art, other drawings can be obtained from these drawings without creative effort.

[0017] Figure 1 A schematic diagram of the hydraulic control system for the slewing mechanism provided in the embodiments of this application; Figure 2 A schematic diagram of the start / stop control loop provided in an embodiment of this application; Figure 3 This is a schematic diagram of the safety circuit provided in the embodiments of this application.

[0018] Figure label: 1-Main oil supply reversing circuit; 2-Start-stop control circuit; 21-Balance brake valve assembly; 211-First balance valve; 212-Second balance valve; 213-Third balance valve; 214-Fourth balance valve; 215-First one-way throttle valve; 216-Second one-way throttle valve; 217-First one-way valve; 218-Second one-way valve; 219-Damping; 22-First unloading circuit; 221-Second relief valve; 23-Second unloading circuit; 231-Third relief valve; 301-First buffer brake circuit; 302-Second buffer brake circuit; 31-Pressure relief branch; 311-First relief valve; 32-Explosion-proof circuit; 321-Explosion-proof valve; 33-Pressure stabilizing branch; 331-Third check valve; 332-Oil source interface; 401-First cylinder; 402-Second cylinder; 41-Cylinder body; 411-First chamber; 412-Second chamber; 42-Piston; 5-Rotary table; V1 - First main oil port; V2 - Second main oil port; C21 - First oil passage port; C11 - Second oil passage port; C1 - First brake control oil port; C2 - Second brake control oil port; T1 - Main unloading oil port; T2 - Support unloading oil port. Detailed Implementation

[0019] The technical solutions of this application will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are some embodiments of this application, but not all embodiments.

[0020] The components of the embodiments of this application described and shown in the accompanying drawings can be arranged and designed in a variety of different configurations. Therefore, the following detailed description of the embodiments of this application provided in the drawings is not intended to limit the scope of the claimed application, but merely to illustrate selected embodiments of the application.

[0021] Based on the embodiments in this application, all other embodiments obtained by those skilled in the art without inventive effort are within the scope of protection of this application.

[0022] In the description of this application, it should be noted that the terms "center," "upper," "lower," "left," "right," "vertical," "horizontal," "inner," and "outer," etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are used only for the convenience of describing this application and simplifying the description, and 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. Therefore, they should not be construed as limitations on this application. Furthermore, the terms "first," "second," and "third" are used for descriptive purposes only and should not be construed as indicating or implying relative importance.

[0023] In the description of this application, it should be noted that, unless otherwise expressly specified and limited, the terms "installation," "connection," and "linking" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; 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; and they can refer to the internal connection between two components. Those skilled in the art can understand the specific meaning of the above terms in this application based on the specific circumstances.

[0024] The following reference Figures 1 to 3 This application describes a hydraulic control system for a slewing mechanism and a slewing mechanism according to some embodiments thereof.

[0025] See Figures 1 to 3 As shown, an embodiment of the first aspect of this application provides a hydraulic control system for a rotary mechanism, used to control a rotary table 5. The hydraulic control system includes a main oil supply reversing circuit 1, a start / stop control circuit 2, a first cylinder 401, a second cylinder 402, a first buffer brake circuit 301, and a second buffer brake circuit 302. Both the first cylinder 401 and the second cylinder 402 are rotary cylinders, each including a cylinder body 41 and a piston 42. The piston 42 divides the cylinder body 41 into a first chamber 411 and a second chamber 412. The pistons 42 of both the first cylinder 401 and the second cylinder 402 are respectively connected to the two ends of the rotary table 5 to drive the rotary table 5 to perform a rotary action. The first buffer brake circuit 301 is connected to the second chamber 412 of the first cylinder 401, and the second buffer brake circuit 302 is connected to the second chamber 412 of the second cylinder 402. The start-stop control circuit 2 includes a balance brake valve assembly 21. The balance brake valve assembly 21 includes a first main oil port V1, a second main oil port V2, a first circuit assembly, a second circuit assembly, a first oil passage port C21, and a second oil passage port C11. The first main oil port V1 and the second main oil port V2 are respectively connected to the main oil supply reversing circuit 1. The first oil passage port C21 is connected to the first chamber 411 of the first cylinder 401, and the second oil passage port C11 is connected to the first chamber 411 of the second cylinder 402. The first circuit assembly is connected between the first main oil port V1 and the second oil passage port C11, and the second circuit assembly is connected between the second main oil port V2 and the first oil passage port C21. The first circuit assembly includes a first balance valve 211 and a second balance valve 212 connected in parallel between the first main oil port V1 and the second oil passage port C11. The flow rate of the second balance valve 212 is greater than that of the first balance valve 211. The second circuit assembly includes a third balancing valve 213 and a fourth balancing valve 214 connected in parallel between the second main oil port V2 and the first oil outlet C21, wherein the flow rate of the fourth balancing valve 214 is greater than that of the third balancing valve 213.

[0026] The hydraulic control system for the slewing mechanism provided by the above-mentioned technical features uses a first balance valve 211 with a small flow rate and a second balance valve 212 with a large flow rate connected in parallel in the first circuit assembly, and a third balance valve 213 with a small flow rate and a fourth balance valve 214 with a large flow rate connected in parallel in the second circuit assembly. On the one hand, it can match the system output flow rate by combining balance valves of different specifications, broaden the flow rate adjustment range of the slewing mechanism, realize wide-range speed regulation, and adapt to the variable slewing speed requirements during tunneling. On the other hand, it can automatically form differentiated flow supply according to the load size. Under heavy load conditions, the large flow rate balance valve ensures sufficient slewing power, while under light load conditions, the small flow rate balance valve suppresses slewing impact, effectively reducing the shaking phenomenon during the slewing start-stop stage, improving the system's adaptability to various variable load conditions such as no-load, light-load, and heavy-load, alleviating the problem of system pressure and flow coupling interference, and ensuring the stable operation of the slewing mechanism of the mining tunneling equipment under complex tunneling conditions of high-frequency start-stop and wide-frequency speed regulation.

[0027] Preferably, the flow rates of the first balancing valve 211 and the third balancing valve 213 can both be less than or equal to 60 L / min (e.g., 40 L / min, 50 L / min, etc.), and the flow rates of the second balancing valve 212 and the fourth balancing valve 214 can both be greater than 60 L / min (e.g., 80 L / min, 100 L / min, etc.). In this way, on the one hand, the low-flow first balancing valve 211 and the third balancing valve 213 can be used to achieve precise fine-tuning at low speeds, meeting the needs of fine control of the slewing trajectory during tunneling operations. On the other hand, the high-flow second balancing valve 212 and the fourth balancing valve 214 ensure the oil supply under heavy-load and rapid slewing conditions. The balancing valves with large and small flow rates work together to widen the effective speed regulation range of the system, automatically match the corresponding flow path according to the load change, alleviate the system pressure-flow coupling interference, reduce the impact of slewing start-stop and braking vibration, improve the system's adaptability to alternating no-load, light-load and heavy-load mining tunneling conditions, and ensure the smooth operation of the slewing mechanism under wide-frequency speed regulation and high-frequency start-stop conditions.

[0028] Preferably, the first balancing valve 211 and the third balancing valve 213 have the same specifications.

[0029] Correspondingly, the second balancing valve 212 and the fourth balancing valve 214 mentioned above have the same specifications.

[0030] Preferably, such as Figure 1 and Figure 2As shown, the aforementioned balance brake valve assembly 21 may further include a first one-way throttle valve 215 and a second one-way throttle valve 216. The inlet end of the first one-way throttle valve 215 is connected to the first main oil port V1, and the outlet end of the first one-way throttle valve 215 is connected to the pilot port of the third balance valve 213. The inlet end of the second one-way throttle valve 216 is connected to the second main oil port V2, and the outlet end of the second one-way throttle valve 216 is connected to the pilot port of the first balance valve 211. In this way, on the one hand, the flow rate of the pilot control oil of the balance valve is regulated by relying on the throttling speed regulation characteristics of the one-way throttle valve, which slows down the opening and closing response speed of the balance valve and avoids the sudden change of oil circuit pressure caused by the instantaneous opening and closing of the balance valve. On the other hand, through the independently and correspondingly arranged pilot throttling control structure, the pilot regulation of the balance valves on both sides of the circuit is independent and does not interfere with each other, effectively weakening the impact and vibration during the reversing and starting and stopping process of the slewing mechanism, and improving the smoothness and continuity of the slewing action.

[0031] Preferably, such as Figure 2 As shown, the aforementioned balance brake valve assembly 21 may further include a first check valve 217 and a second check valve 218. The inlet end of the first check valve 217 is connected to the first main oil port V1, and the outlet end of the first check valve 217 is connected to the main oil supply ports of both the third balance valve 213 and the fourth balance valve 214. The pilot port of the second balance valve 212 is connected downstream of the first check valve 217. The inlet end of the second check valve 218 is connected to the second main oil port V2, and the outlet end of the second check valve 218 is connected to the main oil supply ports of both the first balance valve 211 and the second balance valve 212. The pilot port of the fourth balance valve 214 is connected downstream of the second check valve 218. Thus, on the one hand, the one-way conduction characteristic of the check valve is used to achieve one-way locking of the oil supply path, effectively preventing the malfunction of the rotary mechanism and load fluctuation caused by backflow of oil in the oil circuit, and improving the stability of the system oil supply. On the other hand, it realizes precise zoned oil supply between the main oil supply path and the pilot control path, ensuring that the main oil circuit supply of each group of balance valves and the pilot control oil circuit are coordinated and matched, thereby improving the control accuracy and load following performance of the rotary hydraulic system.

[0032] Preferably, the aforementioned balance brake valve assembly 21 may further include a damper 219, preferably, as shown in the example below. Figure 2 As shown, dampers 219 are provided both upstream and downstream of the connection point between the pilot port of the second balancing valve 212 and the downstream of the first check valve 217. Preferably, as shown... Figure 2As shown, dampers 219 are installed both upstream and downstream of the connection point between the pilot port of the fourth balancing valve 214 and the downstream connection point of the second check valve 218. In this way, on the one hand, the dampers 219 effectively attenuate the pressure fluctuations in the pilot oil circuit, smoothing out pilot oil pressure shocks and avoiding frequent small fluctuations in the balancing valve caused by sudden increases and decreases in pilot pressure. On the other hand, the multi-point damping 219 pressure stabilization structure further extends the opening and closing buffer time of the balancing valve, achieving flexible start and stop of the rotary mechanism, effectively suppressing rotary vibration and movement jerking problems under varying load conditions in mining tunneling, and significantly improving the operational stability of the equipment.

[0033] Based on the above technical features, the balanced brake valve assembly 21 allows the rotary mechanism to operate and stop smoothly under different flow requirements. Its main logic is as follows: 1. Direct action at low frequencies: Both the first balancing valve 211 and the third balancing valve 213 are inserts with a small flow range. When the first cylinder 401 and the second cylinder 402 perform low-frequency actions, i.e., when there is a small flow demand, the first balancing valve 211 and the second balancing valve 212 open first. Under suitable flow conditions, the first balancing valve 211 and the second balancing valve 212 can effectively lock the load, throttle and buffer the speed limit, prevent the first cylinder 401 and the second cylinder 402 from falling due to their own weight and from movement impact, and ensure stable load suspension and smooth and safe start-stop.

[0034] 2. Wide-frequency combined action: Both the second balancing valve 212 and the fourth balancing valve 214 are inserts with a large flow range. When the first cylinder 401 and the second cylinder 402 operate at high frequency, i.e., when there is a large flow demand, the first balancing valve 211 and the second balancing valve 212 are fully open, but the flow rate cannot meet the cylinder's operating requirements. During high-flow operation, the flow capacity of the first one-way throttle valve 215 and the second one-way throttle valve 216 only meets the flow requirements of the first balancing valve 211 and the second balancing valve 212 within a small flow range, causing pressure buildup at the pilot port and establishing a large pilot pressure.

[0035] 3. Stable switching between low and wide frequency ranges: During low-frequency startup, the first balance valve 211 and the second balance valve 212 respond rapidly. During high-frequency startup, a gradual pressure increase and flow restriction mechanism is adopted to prevent a sudden surge of hydraulic oil into the rotary cylinder when the handle is operated quickly, which would prevent the large-inertia rotary structure from being unable to adapt to pressure changes quickly. There is a gradual increase or decrease in pressure when switching between low and high frequencies, resulting in excellent operational adaptability and versatility.

[0036] In an embodiment, preferably, such as Figure 1 and Figure 3As shown, both the first buffer braking circuit 301 and the second buffer braking circuit 302 are safety circuits. Each safety circuit includes a pressure relief branch 31, a support / unloading port T2, and a first overflow valve 311, which is located in the pressure relief branch 31. The pressure relief branch 31 connects the support / unloading port T2 and the second chamber 412 of the first cylinder 401, or it connects the support / unloading port T2 and the second chamber 412 of the second cylinder 402. This allows for rapid pressure relief and stabilization via the overflow valve when the chamber pressure of the first cylinder 401 (or the second cylinder 402) is overloaded or when the load instantaneous impact exceeds the limit, preventing high pressure buildup in the oil circuit and component overload damage, thus achieving overload safety protection for the slewing mechanism. Furthermore, relying on an independent single-chamber pressure relief structure, it is specifically adapted to the braking buffer requirements of the slewing cylinder, effectively absorbing pressure shocks generated by slewing start / stop and load fluctuations, and improving the system's safety redundancy and buffer braking performance under complex tunneling conditions.

[0037] Preferably, such as Figure 1 and Figure 2 As shown, the aforementioned start-stop control circuit 2 may further include a second overflow valve 221, a third overflow valve 231, a first unloading circuit 22, a second unloading circuit 23, and a main unloading port T1. The first unloading circuit 22 connects to the first buffer brake circuit 301 and the main unloading port T1. The second unloading circuit 23 connects to the second buffer brake circuit 302 and the main unloading port T1. The second overflow valve 221 is located in the first unloading circuit 22, and the third overflow valve 231 is located in the second unloading circuit 23. This provides two sets of buffer brake circuits with independent and controllable unloading pathways, allowing for precise adjustment of the unloading rate and pressure based on the independent operating conditions of the two rotating cylinders. This achieves independent buffer braking for both rotating actions, preventing abnormal loads on one side from affecting overall rotating stability. Furthermore, the graded overflow pressure relief structure further broadens the system's pressure regulation range, adapting to various operating conditions such as no-load, heavy-load, and impact loads in mining tunneling, thus improving the system's overall anti-interference capability.

[0038] Furthermore, such as Figure 1 and Figure 3As shown, the aforementioned safety circuit may further include an explosion-proof circuit 32 and an explosion-proof valve 321, with the explosion-proof valve 321 disposed within the explosion-proof circuit 32. Taking the aforementioned safety circuit as a first buffer braking circuit 301 as an example, the explosion-proof circuit 32 connects the second chamber 412 of the first hydraulic cylinder 401 and the first unloading circuit 22. Correspondingly, if the aforementioned safety circuit is a second buffer braking circuit 302, the explosion-proof circuit 32 connects the second chamber 412 of the second hydraulic cylinder 402 and the second unloading circuit 23. In this way, the explosion-proof circuit 32 and the aforementioned pressure relief branch 31 cooperate to form a two-stage buffer pressure relief system. The first relief valve 311 directly installed on the cylinder serves as the first-stage pressure relief protection structure, while the second relief valve 221 and the third relief valve 231 added inside the control valve group serve as the second-stage pressure relief protection structure. The first relief valve 311 on the cylinder side achieves rapid pressure relief and stabilization for normal overload and small pressure impact, completing basic buffer protection. In extreme abnormal conditions such as pipeline rupture and severe load impact, the second pressure relief channel can be opened through the second relief valve 221 and the third relief valve 231 inside the valve group, forming a double pressure relief protection barrier. This effectively avoids the limitations of single-stage pressure relief structure protection and prevents system pressure runaway, pipeline rupture and overall instability under extreme conditions. At the same time, the explosion-proof protection is integrated with the graded buffer braking and overload pressure stabilization functions to achieve multi-stage safety protection for the rotary mechanism, adapting to the complex operating scenarios of high impact and high load risk in hard rock tunneling in mines.

[0039] Optionally, such as Figure 2 As shown, the start-stop control circuit 2 may be provided with a first brake control port C1 and a second brake control port C2. The explosion-proof circuit 32 of the first buffer brake circuit 301 is connected to the first unloading circuit 22 via the first brake port. The explosion-proof circuit 32 of the second buffer brake circuit 302 is connected to the second unloading circuit 23 via the second brake port.

[0040] Preferably, not shown in the figure, the hydraulic control system of the slewing mechanism may further include a low-pressure oil source, such as... Figure 1 and Figure 3As shown, the aforementioned safety circuit may further include a pressure-stabilizing branch 33 and a third check valve 331. The third check valve 331 is located in the pressure-stabilizing branch 33, and its outlet is positioned near the low-pressure oil source. Taking the aforementioned safety circuit as the first buffer braking circuit 301 as an example, the pressure-stabilizing branch 33 connects the low-pressure oil source and the second chamber 412 of the first cylinder 401. Correspondingly, if the above-mentioned safety circuit is the second buffer braking circuit 302, the pressure stabilizing branch 33 is connected to the low-pressure oil source and the second chamber 412 of the second cylinder 402. In this way, on the one hand, when the cylinder is subjected to external impact or equipment vibration and a negative pressure suction state is generated, the oil source interface 332 of the pressure stabilizing branch 33 (i.e., the interface used to connect with the low-pressure oil source) cooperates with the low-pressure oil source to continuously replenish oil and stabilize the pressure, effectively avoiding the problem of motion vibration and starting impact caused by cylinder suction, and ensuring smooth start and stop of the rotary mechanism. On the other hand, relying on the third one-way valve 331 to lock the backflow of oil in the pressure stabilizing branch 33, the oil replenishment circuit is guaranteed to provide stable oil supply in one direction, continuously maintain the stable pressure of the cylinder chamber, and effectively improve the operating stability and control accuracy of the system under variable load and frequent start and stop conditions.

[0041] Based on the safety loop provided by the above technical features, the rotary mechanism can be fully protected and monitored in real time under different flow requirements. Its main protection logic is: 1. Protection against accidental fall: Explosion-proof design prevents the first cylinder 401 (or the second cylinder 402) from falling accidentally in the event of pipeline damage or valve core failure, ensuring that the cylinder is stably locked in a stable position. 2. Protection against reverse impact: The first relief valve 311 automatically opens to relieve pressure when the first cylinder 401 is subjected to a negative load impact, limiting the maximum pressure of the first cylinder 401, protecting it from high pressure damage and stabilizing the system working pressure. The buffer protection function of the first relief valve 311 is different from that of the second relief valve 221 and the third relief valve 231 in the balance brake valve group 21, but it plays a composite protection role. The selection and setting of the first relief valve 311 is more extensive, targeting only the instantaneous reverse impact of the cylinder during hard rock cutting; the overflow protection of the balance brake valve group 21 also additionally targets the negative load impact caused by the cylinder swing due to the weight of the rotary mechanism during wide-frequency, high-flow, and rapid operation.

[0042] Third, to prevent cavitation during high-frequency switching, an external oil supply line is provided to the first cylinder 401 (or the second cylinder 402) via the third one-way valve 331. When the first cylinder 401 (or the second cylinder 402) suddenly starts or stops under high flow conditions, cavitation is prevented due to hysteresis of the valve core opening and closing, thus protecting the safety of the first cylinder 401 (or the second cylinder 402).

[0043] Preferably, the main oil supply reversing circuit 1 may include a load-sensitive multi-way valve. In this way, on the one hand, the system oil supply flow and pressure can be adaptively matched in real time according to the changes in the slewing load. When the load is large, the oil supply will be automatically increased, and when the load is small, the flow will be precisely throttled and the pressure will be stabilized. This effectively reduces the system pressure and flow coupling interference, reduces throttling losses and useless power consumption, and improves the system's energy efficiency. On the other hand, the load-sensitive control characteristics can perfectly adapt to the complex working conditions of wide-frequency speed regulation, variable load, and high-frequency start and stop in mining tunneling, and greatly improve the speed regulation accuracy and load adaptive capability of the slewing mechanism.

[0044] like Figure 1 As shown in the figure, an example including a set of load-sensitive multi-way valves is presented, but it is not limited to this. The number of load-sensitive multi-way valves can be adaptively adjusted according to actual load requirements.

[0045] The second aspect of this application also provides a tunneling equipment, including a rotary table 5 and a hydraulic control system for the rotary mechanism as described in any of the above embodiments, thus possessing all the beneficial technical effects of the hydraulic control system for the rotary mechanism, which will not be repeated here.

[0046] Optionally, the aforementioned tunneling equipment may be a horizontal shaft tunneling machine, a vertical shaft tunneling machine, a roller cutter crusher tunneling machine, a disc vibratory crusher tunneling machine, etc.

[0047] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of this application, and are not intended to limit them. Although this application 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 therein. Such 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 this application.

Claims

1. A hydraulic control system for a rotary mechanism, characterized in that, The hydraulic control system of the rotary mechanism is used to control the rotary table. It includes a main oil supply reversing circuit, a start-stop control circuit, a first oil cylinder, a second oil cylinder, a first buffer brake circuit, and a second buffer brake circuit. Both the first and second hydraulic cylinders are rotary hydraulic cylinders. Each rotary hydraulic cylinder includes a cylinder body and a piston. The piston divides the cylinder body into a first chamber and a second chamber. The pistons of the first and second hydraulic cylinders are respectively connected to the two ends of the rotary table to drive the rotary table to perform a rotary action. The first buffer braking circuit is connected to the second chamber of the first cylinder and the second buffer braking circuit is connected to the second chamber of the second cylinder; The start-stop control circuit includes a balance brake valve assembly, which includes a first main oil port, a second main oil port, a first circuit assembly, a second circuit assembly, a first oil passage port, and a second oil passage port. The first main oil port and the second main oil port are respectively connected to the main oil supply reversing circuit. The first oil passage port is connected to the first chamber of the first cylinder, and the second oil passage port is connected to the first chamber of the second cylinder. The first circuit assembly is connected between the first main oil port and the second oil passage port, and the second circuit assembly is connected between the second main oil port and the first oil passage port. The first circuit assembly includes a first balancing valve and a second balancing valve connected in parallel between the first main oil port and the second oil outlet, wherein the flow rate of the second balancing valve is greater than that of the first balancing valve. The second circuit assembly includes a third balance valve and a fourth balance valve connected in parallel between the second main oil port and the first oil outlet, wherein the flow rate of the fourth balance valve is greater than that of the third balance valve.

2. The hydraulic control system for the rotary mechanism according to claim 1, characterized in that, The balance brake valve assembly also includes a first one-way throttle valve and a second one-way throttle valve. The oil inlet of the first one-way throttle valve is connected to the first main oil port, and the oil outlet of the first one-way throttle valve is connected to the pilot port of the third balance valve. The oil inlet of the second one-way throttle valve is connected to the second main oil port, and the oil outlet of the second one-way throttle valve is connected to the pilot port of the first balance valve.

3. The hydraulic control system for the rotary mechanism according to claim 1, characterized in that, The balance brake valve assembly also includes a first check valve and a second check valve. The inlet end of the first check valve is connected to the first main oil port, and the outlet end of the first check valve is connected to the main oil supply ports of both the third balance valve and the fourth balance valve. The pilot port of the second balancing valve is connected downstream of the first check valve; The inlet end of the second check valve is connected to the second main oil port, and the outlet end of the second check valve is connected to the main oil supply ports of both the first balance valve and the second balance valve. The pilot port of the fourth balancing valve is connected downstream of the second check valve.

4. The hydraulic control system for the rotary mechanism according to claim 3, characterized in that, The balance brake valve assembly also includes damping. The damping is provided both upstream and downstream of the connection point between the pilot port of the second balancing valve and the downstream of the first check valve; And / or, the damping is provided both upstream and downstream of the connection point where the pilot port of the fourth balancing valve is connected to the downstream of the second one-way valve.

5. The hydraulic control system for the slewing mechanism according to any one of claims 1 to 4, characterized in that, Both the first buffer braking circuit and the second buffer braking circuit are safety circuits; The safety circuit includes a pressure relief branch, an oil discharge port, and a first overflow valve, wherein the first overflow valve is disposed in the pressure relief branch; The pressure relief branch connects the unloading port and the second chamber of the first cylinder, or the pressure relief branch connects the unloading port and the second chamber of the second cylinder.

6. The hydraulic control system for the rotary mechanism according to claim 5, characterized in that, The start / stop control circuit also includes a second relief valve, a third relief valve, a first unloading circuit, a second unloading circuit, and a main unloading port. The first unloading circuit is connected to the first buffer braking circuit and the main unloading port; The second unloading circuit is connected to the second buffer braking circuit and the main unloading port; The second overflow valve is located in the first oil unloading circuit, and the third overflow valve is located in the second oil unloading circuit.

7. The hydraulic control system for the rotary mechanism according to claim 6, characterized in that, The safety circuit also includes an explosion-proof circuit and an explosion-proof valve. The explosion-proof valve is disposed in the explosion-proof circuit. The explosion-proof circuit is connected to the second chamber of the first oil cylinder and the first oil unloading circuit, or the explosion-proof circuit is connected to the second chamber of the second oil cylinder and the second oil unloading circuit.

8. The hydraulic control system for the rotary mechanism according to claim 5, characterized in that, It also includes a low-pressure oil source. The safety circuit also includes a pressure stabilizing branch and a third check valve. The third check valve is located in the pressure stabilizing branch, and the outlet end of the third check valve is located on the side close to the low-pressure oil source. The pressure stabilizing branch is connected to the low-pressure oil source and the second chamber of the first oil cylinder, or the pressure stabilizing branch is connected to the low-pressure oil source and the second chamber of the second oil cylinder.

9. The hydraulic control system for the rotary mechanism according to claim 1, characterized in that, The main oil supply reversing circuit includes at least one set of load-sensitive multi-way valves.

10. A tunneling equipment, characterized in that, It includes the rotary table and the hydraulic control system for the rotary mechanism as described in any one of claims 1 to 9.

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