A hydraulic system with multiple safety guarantees

Abstract

The utility model discloses a kind of hydraulic systems with multiple security guarantees, including hydraulic station and oil cylinder, the output end of oil cylinder is connected with load and can drive load lifting;Hydraulic station and oil cylinder between being equipped with the oil inlet pipe leading to the rod cavity of oil cylinder and the oil return pipe leading to the rodless cavity of oil cylinder, oil inlet pipe is equipped with in sequence for controlling the ascending valve group of oil cylinder lifting, main one-way valve, second three-way, second three-way another two interfaces are respectively equipped with the main path leading to the rod cavity of oil cylinder, and the branch path leading to oil return pipe, main path is equipped with in sequence for limiting the one-way flow valve group of main path maximum flow, for the quick cut-off valve group of main path under abnormal condition Quick cut-off;The rod cavity and rodless cavity of oil cylinder between being equipped with for overflow prevent overpressure and make the overflow slow down valve group of oil cylinder slow down, branch path is equipped with for making the quick down valve group of oil cylinder quick down.The utility model has multiple protection and efficient buffering, and has the advantages of certain energy-saving effect.

Description

Technical Field

[0001] This utility model relates to the field of hydraulic system technology, and in particular to a hydraulic system with multiple safety guarantees. Background Technology

[0002] In amusement rides that involve rapid vertical jumps, such as frog jumps, rotating towers, and drop towers, high-speed hydraulic cylinders are typically used to drive the cabins (riders) up and down rapidly via pulley systems. The hydraulic systems used in these rides have the following characteristics:

[0003] 1) The hydraulic cylinder stroke is relatively long, generally between 6 and 9 meters, and some even exceed 10 meters;

[0004] 2) The hydraulic cylinder operates at a high speed, generally exceeding 2 meters per second;

[0005] 3) Due to the large number of passengers and the large size of the skid and cabin, the mass of its moving parts is also very large;

[0006] 4) To achieve rapid lifting, a high-power hydraulic system is required;

[0007] 5) The flow rate of the high-speed cylinder circuit is large, especially the flow rate of the rodless chamber of the cylinder. Therefore, the hydraulic system needs to be equipped with large-diameter hydraulic lines and rotary joints.

[0008] These characteristics present multiple challenges to hydraulic systems:

[0009] 1) The transition from high-speed descent to rapid ascent in the cabin (passengers) involves enormous impact energy. The violent impact may cause equipment and its components to fail, or even pose a direct danger to the personal safety of passengers.

[0010] 2) Hydraulic systems are susceptible to unavoidable malfunctions such as hydraulic hose rupture, hydraulic valve malfunction, and overspeed. Rapidly descending cabins (passengers) may face the risk of uncontrolled descent. Although pneumatic-hydraulic shock absorbers are generally installed under the cabin, the short travel of the shock absorbers means that the impact on the cabin (passengers) is still significant, and overspeeding could lead to a safety accident.

[0011] 3) High-power hydraulic systems increase equipment costs and may cause the hydraulic system to overheat, thereby endangering system safety;

[0012] 4) During the high-speed descent of the cabin (passengers), the piston rod of the hydraulic cylinder extends rapidly, and the rodless chamber of the hydraulic cylinder needs to be replenished with a large flow of hydraulic oil. Therefore, a large-diameter pipe and rotary joint (rotary tower type) must be provided between the lower chamber and the oil tank to prevent the hydraulic cylinder from sucking in air and causing damage to the cylinder body.

[0013] The hydraulic systems of existing equipment use conventional designs, such as Figure 1As shown, this conventional hydraulic system mainly consists of a hydraulic power unit, valve assemblies mounted on the hydraulic power unit, an accumulator, cylinders and their valves and pipelines. The valve assemblies of the hydraulic power unit are equipped with solenoid valves controlling a three-position four-way electro-hydraulic directional valve and a hydraulically controlled check valve. The cylinders include hydraulically controlled check valves, one-way throttle valves, and relief valves. The valve assemblies, accumulator, and cylinders and their valves of the hydraulic power unit are connected via hydraulic hoses. The extension and retraction of the cylinder piston rod are controlled by the three-position four-way electro-hydraulic directional valve. When the cylinder piston rod extends, the solenoid valve must first open the hydraulically controlled check valve. The existing hydraulic system can meet the basic motion requirements of the equipment, but it cannot eliminate hydraulic shock and poses the following risks:

[0014] 1) Due to the long distance between the accumulator port and the working chamber port of the hydraulic cylinder installed on the hydraulic station, typically between 10 and 20 meters, the accumulator cannot effectively absorb the impact generated by the hydraulic cylinder in a timely manner. Prolonged reversing impacts can lead to the failure of equipment components, affecting the visitor experience and even causing safety accidents. Furthermore, because there is no accumulator between the hydraulic check valve and the hydraulic cylinder, when the hydraulic check valve suddenly closes due to an unexpected situation, a violent impact will be generated, posing a risk of damaging the equipment and endangering visitor safety.

[0015] 2) The distance between the hydraulic check valve and the control solenoid valve is too long, and the extension speed of the cylinder piston rod is extremely high, which causes the hydraulic check valve controlled by the hydraulic station valve group to fail to close in time, which may lead to loss of control of the cockpit.

[0016] 3) During high-speed descent, the flow rate in the hydraulic cylinder is very high. When this large flow of hydraulic oil passes through the three-position four-way electro-hydraulic directional valve, it may generate a significant pressure differential, causing distortion of the set speed of the one-way throttle valve. If the hydraulic hose connecting the hydraulic station valve assembly and the one-way throttle valve ruptures, the downstream pressure of the one-way throttle valve will suddenly disappear, leading to an increase in flow rate. If the descent speed of the cockpit exceeds the maximum permissible speed of the pneumatic-hydraulic damper, it may cause a safety accident.

[0017] Therefore, it is necessary to further improve and perfect the existing technology to overcome these shortcomings, and this utility model is made based on this situation. Utility Model Content

[0018] The purpose of this utility model is to overcome the shortcomings of the existing technology and provide a hydraulic system with multiple protections, efficient buffering, and a certain energy-saving effect.

[0019] This utility model is achieved through the following technical solution:

[0020] To solve the above-mentioned technical problems, this utility model provides a hydraulic system with multiple safety guarantees, including a hydraulic station and a cylinder. The output end of the cylinder is connected to a load and can drive the load to rise and fall. An oil inlet pipe leading to the rod chamber of the cylinder and a return oil pipe leading to the rodless chamber of the cylinder are provided between the hydraulic station and the cylinder. The oil inlet pipe is sequentially provided with a rising valve group for controlling the rising and falling of the cylinder, a main check valve, and a second three-way valve. The other two ports of the second three-way valve are respectively provided with a main line leading to the rod chamber of the cylinder and a branch line leading to the return oil pipe. The main line is sequentially provided with a one-way flow valve group for limiting the maximum flow of the main line and a quick-cut-off valve group for quickly cutting off the main line in abnormal situations. An overflow slow-down valve group for overflow prevention of overpressure and slow descent of the cylinder is provided between the rod chamber and the rodless chamber of the cylinder. The branch line is provided with a quick-down valve group for rapid descent of the cylinder.

[0021] To further address the technical problems to be solved by this utility model, this utility model provides a hydraulic system with multiple safety guarantees, wherein the oil inlet pipe is equipped with a first accumulator located between the main check valve and the second three-way valve.

[0022] To further address the technical problems to be solved by this utility model, this utility model provides a hydraulic system with multiple safety guarantees, wherein the rod chamber of the oil cylinder is connected to a second accumulator.

[0023] To further address the technical problems to be solved by this utility model, this utility model provides a hydraulic system with multiple safety guarantees, wherein the one-way flow valve group is a one-way flow valve or a one-way throttle valve.

[0024] To further address the technical problems to be solved by this utility model, this utility model provides a hydraulic system with multiple safety guarantees, wherein the quick-cut-off valve group includes a two-way bidirectional shut-off electro-hydraulic switch valve and a third accumulator, and an oil inlet check valve is provided between the third accumulator and the main line.

[0025] To further address the technical problems to be solved by this utility model, this utility model provides a hydraulic system with multiple safety guarantees, wherein the overflow slow-descent valve group includes an overpressure protection overflow valve, a slow-descent solenoid valve, and an emergency descent balance valve connected in parallel, and the emergency descent balance valve is connected to a manual pump for manually opening it.

[0026] To further address the technical problems addressed by this utility model, this utility model provides a hydraulic system with multiple safety guarantees. The quick-release valve group is a multi-stage electromagnetic relief valve group, including a two-way cartridge valve. The pilot control oil circuit of the two-way cartridge valve is equipped with one or more sets of combined valves and safety relief valves. The combined valves and safety relief valves are connected in parallel. The combined valves include a control solenoid valve and a pressure regulating relief valve connected in series.

[0027] To further address the technical problems to be solved by this utility model, this utility model provides a hydraulic system with multiple safety guarantees, wherein the rising valve group is a bidirectional shut-off hydraulic valve group with variable flow function.

[0028] To further address the technical problems to be solved by this utility model, this utility model provides a hydraulic system with multiple safety guarantees, wherein a gas-liquid buffer and a safety position detection switch are provided below the load.

[0029] To further address the technical problems to be solved by this utility model, this utility model provides a hydraulic system with multiple safety guarantees, wherein a pressure sensor is connected to the rod chamber of the oil cylinder.

[0030] Compared with the prior art, the present invention has the following advantages:

[0031] This invention ensures the safety and stability of the hydraulic system during load lifting and lowering through multiple safety mechanisms and a highly efficient buffer system. Specifically, it employs a series-connected multi-safety lowering module (including multiple accumulators in different positions, a one-way flow valve group, a fast-cut-off valve group, and an overflow slow-down valve group), a normal and emergency buffer system, and an independent safety circuit, greatly reducing the risk of runaway due to a single fault. Simultaneously, the system achieves efficient energy storage and release through the rational arrangement of valve groups and accumulators, not only improving work efficiency but also reducing energy consumption. This design enables the hydraulic system to maintain excellent performance under various operating conditions, providing a strong guarantee for the safe operation of the equipment and the user experience. Attached Figure Description

[0032] The specific embodiments of this utility model will be further described in detail below with reference to the accompanying drawings, wherein:

[0033] Figure 1 This is an existing hydraulic principle block diagram;

[0034] Figure 2 This is one of the hydraulic principle block diagrams of this utility model;

[0035] Figure 3 This is the second hydraulic principle block diagram of this utility model;

[0036] Figure 4 This is a block diagram of the hydraulic principle of a dual-cylinder system. Detailed Implementation

[0037] To enable those skilled in the art to better understand the technical solution of this utility model, the present utility model will be further described in detail below with reference to the accompanying drawings and specific embodiments.

[0038] like Figures 2 to 4 As shown, this embodiment relates to a hydraulic system with multiple safety features, which can efficiently and safely control the lifting and lowering operation of a load 3 (such as a cabin). The hydraulic system mainly consists of a hydraulic station 1, an ascending valve group V1, an inlet pipe HL1, a main check valve V2, a first accumulator AC1, a fast descending valve group V3, a return pipe RL0, a one-way flow valve group V4, a fast shut-off valve group V5, an overflow slow descending valve group V6, a second accumulator AC2, a pressure sensor PS1, a safety position detection switch 5, and several tees (including a main tee T0, a first tee T1, a second tee T2, a third tee T3, etc.), hydraulic steel pipes, hydraulic hoses, and other pipeline connectors. Through the reasonable arrangement of the valve group, accumulator, and their connecting pipes, a hydraulic system with multiple protections, high-efficiency buffering, and a certain energy-saving effect is formed.

[0039] In this embodiment, the output end of the hydraulic cylinder 2 is connected to the load 3 and can drive the load 3 to move up and down. A pulley system 31 is provided between the piston rod of the hydraulic cylinder 2 and the load 3 to amplify the stroke of the hydraulic cylinder. When the piston rod of the hydraulic cylinder 2 moves down, it drives the load 3 to rise; conversely, when the piston rod moves up, the load 3 will fall.

[0040] Preferred, such as Figure 2 As shown, a safety position detection switch 5, which is a limit switch, is installed below the load 3. When the load 3 descends to this safe position, the safety position detection switch 5 will be triggered. Upon receiving the signal, the control system will promptly de-energize the quick-cut-off valve group V5 to cut off the main oil circuit, thus addressing potential safety risks. This design effectively enhances the system's safety.

[0041] To monitor the working status of cylinder 2 in real time, the rod chamber (or upper chamber, working chamber) of cylinder 2 is connected to pressure sensor PS1 to detect the oil pressure in the chamber in real time. When the control system detects an abnormal oil pressure signal, it will also promptly de-energize the quick-cut-off valve group V5 to cut off the main oil circuit to handle potential safety risks.

[0042] The hydraulic station 1 and the cylinder 2 are connected by an inlet pipe HL1 leading to the rod chamber of the cylinder 2 and a return pipe RL0 leading to the rodless chamber (or lower chamber) of the cylinder 2. The inlet pipe HL1 is sequentially equipped with a riser valve group V1 for controlling the lifting and lowering of the cylinder 2, a main check valve V2, and a second three-way valve T2. Between the main check valve V2 and the second three-way valve T2, there is also a second pipeline HL2, a first three-way valve T1, and a third pipeline HL3. The first accumulator AC1 is connected to one of the ports of the first three-way valve T1. The other two ports of the second three-way valve T2 are respectively a main path leading to the rod chamber of the cylinder 2 and a branch path leading to the return pipe RL0. The main line is sequentially equipped with a one-way flow valve group V4 for limiting the maximum flow of the main line and a quick-cut-off valve group V5 for quickly cutting off the main line in abnormal situations; the rod chamber and rodless chamber of the cylinder 2 are equipped with an overflow slow-down valve group V6 for overflow prevention of overpressure and slow descent of the cylinder 2; the branch line is equipped with a quick-down valve group V3 for rapid descent of the cylinder 2.

[0043] The specific structure of each valve group is described below.

[0044] Specific structure of riser valve group V1:

[0045] The ascending valve assembly V1 preferably employs a bidirectional shut-off hydraulic valve (or valve assembly) with variable flow capability. The variable flow is used to achieve slow start, rapid operation, and slow stop during the ascending phase, thereby achieving a smooth ascent and reducing impact. The bidirectional shut-off function can prevent uncontrolled descent that may occur if the main check valve V2 fails.

[0046] The riser valve group V1 can be configured with different valve combinations, including valves of different diameters (such as slow valve V1.1 and fast valve V1.2 connected in parallel), proportional servo valves, or conventional directional valves with buffering function.

[0047] Specific structure of the quick-release valve assembly V3:

[0048] The quick-release valve assembly V3 is a combined multi-stage solenoid relief valve assembly, preferably composed of the following parts: a large-diameter two-way cartridge valve V3.0 and its control cover, one or more control solenoid valves V3.2 and pressure regulating relief valves V3.1 (i.e., combination valves), and a safety relief valve V3.3. The control solenoid valves V3.2 are responsible for controlling the opening and closing of the quick-release valve assembly V5; the pressure regulating relief valve V3.1 can adjust the valve assembly pressure within a small range, thereby changing the quick-release speed; the safety relief valve V3.3 is used to regulate the safety pressure of the valve assembly. Of course, a conventional multi-stage solenoid relief valve can also be used as the quick-release valve.

[0049] The combination valve and the safety relief valve V3.3 are configured in parallel. The combination valve includes a control solenoid valve V3.2 and a pressure regulating relief valve V3.1 connected in series.

[0050] Specific structure of the one-way flow valve assembly V4:

[0051] The one-way flow valve V4 can be installed at any position between the oil port of the hydraulic cylinder working chamber and the second three-way valve T2 or the quick-release valve assembly V3. The one-way flow valve V4 preferably uses a dedicated flow valve with self-adjustment function; this flow valve can have a built-in one-way valve or be used in combination with a separate one-way valve. Depending on the actual application requirements, users can choose a conventional one-way flow valve or a one-way throttle valve.

[0052] In extreme cases, if both the quick-shutdown valve assembly V5 and the quick-down valve assembly V3 fail, the one-way flow valve V4 ensures that the runaway load 3 (cabin) safely lands at the lower gas-liquid buffer 4 without exceeding the maximum design speed. Figure 2 As shown, a gas-liquid buffer 4 is located directly below the load 3. Through the gas-liquid buffer 4, the load 3 (cabin) will be smoothly lowered to the lowest point, minimizing safety risks and impact forces.

[0053] Specific structure of the V5 quick-shut-off valve assembly:

[0054] The quick-cut-off valve assembly V5 includes a two-way bidirectional electro-hydraulic shut-off valve V5.0 and a third accumulator AC3. An inlet check valve V5.1 is installed between the third accumulator AC3 and the main oil circuit. This quick-cut-off valve assembly V5 is connected to a low-position safety point and program detection system. When the load 3 (e.g., the cockpit) touches the safety position detection switch 5 or the program detects an abnormality, the system will immediately cut off the main oil circuit to prevent the load 3 (cockpit) from falling uncontrollably and causing a safety accident.

[0055] During the inspection and preparation phase, the quick-close valve assembly V5 is de-energized to effectively prevent uncontrolled ascent of load 3 (cabin) due to a malfunction in the rise valve assembly V1. Furthermore, the third accumulator AC3 is in standby mode to store high-pressure hydraulic oil, providing power backup when rapid closure of valve assembly V5 is required. Simultaneously, an inlet check valve V5.1 is installed between the cylinder working chamber and the third accumulator AC3 to prevent pressure leakage of the high-pressure hydraulic oil in the third accumulator AC3, thereby ensuring the safety and stability of the system.

[0056] Specific structure of the overflow slow-down valve assembly V6:

[0057] The overflow slow-descent valve assembly V6 mainly consists of an overpressure protection overflow valve V6.1, a slow-descent solenoid valve V6.2, and an emergency descent balancing valve V6.3. These three are connected in parallel to enhance system functionality. The emergency descent balancing valve V6.3 is connected to a manual pump HP1 for manual opening.

[0058] Specifically, the overpressure protection relief valve V6.1 is used for overpressure protection of the hydraulic cylinder, while the slow-descent solenoid valve V6.2 is used to control the slow start, stop, and slow descent during the high-speed descent phase. In emergency situations, the emergency descent balance valve V6.3 can be opened via the manual pump HP1 to achieve a smooth descent of load 3 (cabin). The overflow from the slow-descent relief valve assembly V6 and the hydraulic oil flowing out during the slow descent will flow back to the outlet of the fast-descent valve assembly V3 through the oil pipe RL2.

[0059] The following describes a more detailed pipe layout:

[0060] The main pipeline is divided into several sections: the fifth pipeline HL5, the sixth pipeline HL6, and the seventh pipeline HL7. A one-way flow valve assembly V4 is located between HL5 and HL6, and a quick-cut-off valve assembly V5 is located between HL6 and HL7. HL7 is connected to the rod chamber of the hydraulic cylinder 2. The branch pipeline is also divided into several sections: the fourth pipeline HL4 and the first outlet pipeline RL1. A quick-drain valve assembly V3 is located between the fourth pipeline HL4 and the first outlet pipeline RL1. A second outlet pipeline RL2 connects HL7 and RL1, and an overflow slow-drain valve assembly V6 is located on the second outlet pipeline RL2.

[0061] Furthermore, a first accumulator AC1 is installed on the oil inlet pipe HL1, located between the main check valve V2 and the second three-way valve T2. In this embodiment, the first accumulator AC1 is connected to the first three-way valve T1, and the first accumulator AC1 and the first three-way valve T1 are preferably rigidly connected to a steel pipe, but can also be connected to a hydraulic hose. Similarly, a second accumulator AC2 is connected to the rod chamber of the cylinder 2 to further improve the system performance.

[0062] Preferably, the quick-cut-off valve group V5, the one-way flow valve V4, and the quick-down valve group V3 are rigidly connected and installed on the cylinder body to form a series-connected multi-safety descent module, eliminating the risk of uncontrolled descent caused by a single valve group failure or a broken connecting hydraulic hose.

[0063] The first accumulator AC1, the quick-release valve group V3, the second accumulator AC2, and the overpressure protection relief valve V6.1 constitute a normal buffer system. The second accumulator AC2 and the overpressure protection relief valve V6.1 constitute an emergency buffer system after the main oil circuit is cut off. The oil ports of the second accumulator AC2 and the overpressure protection relief valve V6.1 are directly connected to the working chamber of the oil cylinder and are both installed on the end cover of the working chamber side of the oil cylinder or on a valve block fixed to the end cover. The first accumulator AC1 and the quick-release valve group V3 are preferably fixed to the cylinder body. The first three-way valve T1 and the second three-way valve T2 are preferably rigidly connected. Since there is double protection between the working chamber of the oil cylinder and the accumulator by the quick-release valve group V5 and the one-way flow valve V4, the first accumulator AC1 can also be installed on the frame near the oil cylinder if necessary. The first three-way valve T1 and the second three-way valve T2 are preferably connected by a hydraulic hose. The normal buffer system and the emergency buffer system constitute a buffer system in all working states. The buffer system installed at close range can eliminate the impact generated during high-speed reversal or sudden stop in a timely and efficient manner, protect the safety of equipment and tourists, reduce equipment failure, and improve the tourist experience.

[0064] The first accumulator AC1 is installed between the outlet of the main one-way valve V2 and the fast-down valve assembly V3 / one-way flow valve V4. The selection of the first accumulator AC1 takes into account both buffering and energy storage functions. When the fast-down valve assembly V3 is de-energized and enters the buffering stage, the first accumulator AC1 absorbs the impact energy generated by high-speed reversal and stores it in the form of high-pressure oil. After entering the rising stage, the high-pressure oil stored in the first accumulator AC1 quickly enters the working chamber of the cylinder from the one-way flow valve assembly V4 and the fast-cut-off valve assembly V5 to rapidly lift the load 3 (cabin), so that the three stages of high-speed descent-buffering-rapid rise of the load 3 (cabin) are smoothly connected. The pressure of the high-pressure oil stored in the first accumulator AC1 is greater than the system pressure of hydraulic station 1, which is used for the accelerated lifting stage of load 3 (cabin), which can reduce the installed power of the hydraulic system and achieve energy saving. The first accumulator AC1 preferably adopts a piston-type accumulator to prevent the risk of sudden rupture and leakage of the bladder-type accumulator, thus losing its buffering function.

[0065] Oil enters the working chamber of the hydraulic cylinder through the inlet pipe HL1, controlled by the rising valve assembly V1; oil exits through the first outlet pipe RL1, controlled by the quick-release valve assembly V3. When oil enters the working chamber, high-pressure oil flows from the rising valve assembly V1 through the inlet pipe HL1, the main check valve V2, (second pipe HL2), the first three-way valve T1, (third pipe HL3), the second three-way valve T2, (fifth pipe HL5), the one-way flow valve assembly V4, (sixth pipe HL6), the quick-release valve assembly V5, and (seventh pipe HL7) into the working chamber. When oil exits the working chamber, hydraulic oil enters the lower chamber of the hydraulic cylinder through (seventh pipe HL7), the quick-release valve assembly V5, (sixth pipe HL6), the one-way flow valve V4, (fifth pipe HL5), the second three-way valve T2, (fourth pipe HL4), the quick-release valve assembly V3, the first outlet pipe RL1, and the third three-way valve T3. The second tee T2 is the end point of the one-way oil inlet pipe HL1 and the starting point of the one-way oil outlet pipe RL1.

[0066] The inlet pipe HL1 is equipped with a hydraulic hose HL1.1 and a main check valve V2. The hydraulic hose HL1.1 prevents mechanical damage to the piping system caused by the swaying of the cylinder during lug mounting. The main check valve V2 eliminates the risk of uncontrolled descent caused by a rupture of the hydraulic hose HL1.1 or a failure of the riser valve assembly. The main check valve V2 also branches the cylinder circuit into an independent safety hydraulic circuit (detailed below) starting from the main check valve V2, improving system safety.

[0067] One end of the first oil outlet line RL1 is connected to the oil outlet of the quick-descent valve assembly V3, and the other end is connected to the third tee T3, which communicates with the oil port PT1 in the lower chamber of the cylinder. The other end of the third tee T3 is connected to the return oil line RL0. During the high-speed descent phase, the hydraulic oil in the working chamber flows through the oil outlet of the quick-descent valve assembly V3, through the first oil outlet line RL1 and the third tee T3, and all enters the lower chamber (rodless chamber) of the cylinder. The insufficient portion is drawn from the oil tank of the hydraulic station through the return oil line RL0, reducing the amount of oil replenished through the return oil line RL0, preventing malfunctions caused by insufficient oil replenishment in the lower chamber, and reducing the diameter of the return oil line RL0 and the valves (and rotary joints) on it, thus saving costs.

[0068] The working process of the hydraulic system of this utility model

[0069] The quick-shutdown valve assembly V5 adopts a normally closed design. Under normal operating conditions of the hydraulic system, the quick-shutdown valve assembly V5 is energized, and the main oil circuit remains connected at all times. This design ensures system safety in the event of various abnormalities such as load 3 reaching the safe position, abnormal oil pressure detection, and temporary power failure.

[0070] 1. Load increase process

[0071] When the load 3 (e.g., the cabin) begins to rise, the high-pressure oil in the hydraulic station 1 first flows through the riser valve group V1, then through the main tee T0 (located on the inlet pipe HL1), and quickly flows into the inlet pipe HL1. This process, with the help of the hydraulic hose (HL1.1), ensures that the high-pressure oil can be smoothly transmitted to the main check valve V2. After passing through the main check valve V2, the hydraulic oil flows sequentially through the second pipeline HL2, the first tee T1, the third pipeline HL3, and the second tee T2. At this time, the hydraulic oil enters the fifth pipeline HL5, and the flow rate is regulated by the one-way flow valve group V4. Immediately afterwards, the oil flows through the sixth pipeline HL6, and finally reaches the rapid shut-off valve group V5, entering the working chamber (upper chamber) of the cylinder. With the input of hydraulic oil, the piston rod of the cylinder begins to retract, and with the help of the pulley group 31, the load 3 is driven to rise rapidly to the predetermined height.

[0072] 2. Load reduction process

[0073] As load 3 (cabin) begins its descent, the hydraulic oil in the cylinder's working chamber is discharged outward through the quick-closing valve assembly V5, flowing sequentially through the sixth line HL6, the one-way flow valve V4, the fifth line HL5, and the second three-way valve T2, before flowing through the fourth line HL4 to the quick-descent valve assembly V3. Through the quick-descent valve assembly V3, the hydraulic oil then flows into the first outlet line RL1, and finally enters the lower chamber of the cylinder through the third three-way valve T3. During this process, the weight of load 3 causes the cylinder piston rod to extend outward, and the load moves at high speed during its descent.

[0074] 3. The function of accumulators

[0075] When the quick-release valve assembly V3 is de-energized, the hydraulic oil between the cylinder working chamber and the quick-release valve assembly V3 begins to enter the first accumulator AC1 and compress the internal nitrogen. During this process, the hydraulic oil pressure in the cylinder working chamber and the first accumulator AC1 gradually increases, and the extension speed of the cylinder piston rod gradually decreases until it finally stops. Subsequently, the high-pressure oil in the first accumulator AC1 works together with the hydraulic oil from the main check valve V2 to cause the piston rod to retract again, quickly driving the load 3 (cabin) to rise. This process demonstrates the system's smoothness and continuity during the load's up-and-down movement, ensuring that the load can smoothly decelerate and smoothly transition to the rising phase.

[0076] 4. Security Guarantee Mechanism

[0077] During operation, if load 3 (cabin) becomes uncontrollable and triggers the low-position safety switch (safety position detection switch 5), or if the program detects other abnormalities requiring rapid disconnection of the main oil circuit, the system will immediately de-energize the rapid shut-off valve group V5 to cut off the main oil circuit, ensuring the safety of the entire system. This safety mechanism effectively prevents load runaway due to faults, providing strong protection for system operation.

[0078] 5. Buffer Coordination Operation

[0079] During rapid ascent and descent during startup and shutdown, the system employs a combined fast and slow buffering procedure. This process is achieved by first activating the slow valve V1.1, then switching to the fast valve V1.2, and finally adjusting back to the slow valve V1.1. This operating strategy effectively reduces the impact force during load increases and decreases, ensuring the safety of equipment and personnel, and improving operational stability.

[0080] 6. Emergency Operations During Power Outages

[0081] In the event of a sudden power outage, operators can use the manual pump HP1 to open the emergency descent balance valve V6.3, actively connecting the hydraulic system. This design allows the system to slowly lower Load 3 (cabin) to the ground, preventing accidental injury or equipment damage caused by a sudden power outage. This emergency response mechanism further enhances the system's safety, ensuring the safety of personnel and equipment in various emergency situations.

[0082] Through the above steps, this hydraulic system demonstrates excellent safety and reliability, enabling it to safely and efficiently complete load lifting and lowering operations while ensuring stability and safety under various working conditions.

[0083] In addition, such as Figure 4 As shown, the flexibility of this hydraulic circuit allows it to be configured into a multi-actuator system or a single-actuator multi-safety-circuit system via T-junction combinations. In specific applications, the system can be configured into a dual-cylinder system or a single-cylinder dual-safety-circuit system by setting the main T0, depending on requirements. This design not only enhances the safety factor of the equipment but also effectively reduces the potential risks caused by a single failure, achieving a more reliable operating mode.

[0084] exist Figure 4 In the illustrated dual-cylinder system, the two cylinders can work together through a flexible hydraulic connection. The dual-cylinder system has two identical but independent hydraulic circuits (divided into two symmetrical hydraulic circuits at the main tee T0; the two circuits share only the hydraulic power unit, the riser valve group V1, and the manual pump). Each hydraulic circuit drives its own cylinder. The main check valve V2 on each hydraulic circuit serves to allow the two cylinders to operate independently, providing double protection.

[0085] In the design of a single-cylinder dual-safety-circuit system (not shown in the figure), the system has two identical but independent hydraulic circuits (sharing only the hydraulic station, the lifting valve group V1, and the manual pump). Both of these hydraulic circuits have relatively low flow rates. These two low-flow hydraulic circuits drive the same cylinder. The advantages of using two low-flow hydraulic circuits instead of a single high-flow circuit are: 1. In extreme cases, if both the quick-cutoff valve group V5 and the quick-down valve group V3 fail, the low-flow-rate check valve V4 can ensure that the runaway load 3 (cabin) safely descends to the lower pneumatic-hydraulic buffer at no more than 1 / 2 of the maximum design speed, improving safety; 2. Single or dual circuits can be flexibly selected to operate simultaneously, meeting the requirements for safe operation of the equipment in multiple states.

[0086] It is worth noting that, according to the design concept of this utility model, the specific configuration of the hydraulic circuit can be flexibly adjusted according to the needs of actual applications. This flexibility allows engineers to select suitable types of hydraulic components and assembly sequences based on different working environments and load conditions, and even add or remove individual components to maximize system performance and ensure system economy. This adjustability enables this hydraulic circuit to be widely used in various scenarios requiring high-speed or high-inertia load hydraulic systems. Whether in high-speed or high-inertia load hydraulic systems with cylinder lifting or in high-speed or high-inertia load systems driven by hydraulic motors, it exhibits excellent adaptability, ensuring the safety and reliability of the equipment.

[0087] Obviously, the above embodiments of this utility model are merely examples for clearly illustrating the present utility model, and are not intended to limit the implementation of the present utility model. Those skilled in the art can make other variations or modifications based on the above description. It is neither necessary nor possible to exhaustively list all possible implementations here. Any modifications, equivalent substitutions, and improvements made within the spirit and principles of this utility model should be included within the protection scope of the claims of this utility model.

Claims

1. A hydraulic system with multiple safety guarantees, characterized in that: The system includes a hydraulic station (1) and a cylinder (2). The output end of the cylinder (2) is connected to a load (3) and can drive the load (3) to rise and fall. Between the hydraulic station (1) and the cylinder (2), there is an oil inlet pipe (HL1) leading to the rod chamber of the cylinder (2) and an oil return pipe (RL0) leading to the rodless chamber of the cylinder (2). The oil inlet pipe (HL1) is sequentially equipped with a riser valve group (V1), a main check valve (V2), and a second three-way valve (T2) for controlling the rise and fall of the cylinder (2). The second three-way valve (T2) has two other valves. The interface is provided with a main path leading to the rod chamber of the cylinder (2) and a branch path leading to the return oil pipe (RL0). The main path is provided with a one-way flow valve group (V4) for limiting the maximum flow of the main path and a quick-cut-off valve group (V5) for quickly cutting off the main path in abnormal situations. The rod chamber and rodless chamber of the cylinder (2) are provided with an overflow slow-down valve group (V6) for overflow prevention of overpressure and slow descent of the cylinder (2). The branch path is provided with a quick-down valve group (V3) for rapid descent of the cylinder (2).

2. A hydraulic system with multiple safety guarantees according to claim 1, characterized in that: The oil inlet pipe (HL1) is equipped with a first accumulator (AC1) located between the main check valve (V2) and the second three-way valve (T2).

3. A hydraulic system with multiple safety guarantees according to claim 1, characterized in that: The rod chamber of the hydraulic cylinder (2) is connected to a second accumulator (AC2).

4. A hydraulic system with multiple safety guarantees according to claim 1, characterized in that: The one-way flow valve assembly (V4) is a one-way flow valve or a one-way throttle valve.

5. A hydraulic system with multiple safety guarantees according to claim 1, characterized in that: The quick-cut-off valve assembly (V5) includes a two-way bidirectional shut-off electro-hydraulic switch valve (V5.0) and a third accumulator (AC3), and an oil inlet check valve (V5.1) is provided between the third accumulator (AC3) and the main line.

6. A hydraulic system with multiple safety guarantees according to claim 1, characterized in that: The overflow slow-down valve assembly (V6) includes an overpressure protection overflow valve (V6.1), a slow-down solenoid valve (V6.2), and an emergency landing balance valve (V6.3) connected in parallel. The emergency landing balance valve (V6.3) is connected to a manual pump (HP1) for manually opening it.

7. A hydraulic system with multiple safety guarantees according to claim 1, characterized in that: The quick-release valve assembly (V3) is a multi-stage electromagnetic relief valve assembly, and includes a two-way cartridge valve (V3.0). The pilot control oil circuit of the two-way cartridge valve (V3.0) is provided with one or more sets of combination valves and safety relief valves (V3.3). The combination valves and safety relief valves (V3.3) are connected in parallel. The combination valves include a control solenoid valve (V3.2) and a pressure regulating relief valve (V3.1) connected in series.

8. A hydraulic system with multiple safety guarantees according to claim 1, characterized in that: The riser valve assembly (V1) is a bidirectional shut-off hydraulic valve assembly with variable flow function.

9. A hydraulic system with multiple safety guarantees according to claim 1, characterized in that: Below the load (3) is a gas-liquid buffer (4) and a safety position detection switch (5).

10. A hydraulic system with multiple safety guarantees according to claim 1, characterized in that: The rod chamber of the hydraulic cylinder (2) is connected to a pressure sensor (PS1).

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