Hydraulic quick-release structure for monorail crane brake oil cylinder

Abstract

The present application relates to the technical fields of hydraulic components, in particular to a hydraulic quick-release structure for a monorail crane brake cylinder. The hydraulic quick-release structure for the monorail crane brake cylinder comprises an outer cylinder and an inner cylinder connected with each other, and further comprises an outer piston slidably connected between the outer cylinder and the inner cylinder. The inner side of the outer cylinder is provided with a driving oil cavity corresponding to the right side of the outer piston and an intermediate oil cavity corresponding to the left side of the outer piston. The bottom of the driving oil cavity is connected with an oil outlet pipeline. The outer piston is fixedly provided with a first spiral impeller at a position corresponding to the driving oil cavity. A rotating drum is rotatably installed between the outer cylinder and the inner cylinder through a bearing. The rotating drum is provided with a torsion spring at the rotating connection with the inner cylinder. An energy storage cavity is arranged between the rotating drum and the outer cylinder. The present application has the beneficial effect that the hydraulic quick-release function is integrated in the brake cylinder body, the external independent valve group scheme is abandoned, the external pipeline and the connection nodes are reduced, and the system space layout is simplified.

Description

Technical Field

[0001] This invention relates to the field of hydraulic component technology, specifically to a hydraulic quick-release structure for a monorail crane brake cylinder. Background Technology

[0002] To meet the needs of emergency and rapid braking, the existing monorail braking system generally adopts the principle of "spring braking and hydraulic release". However, when emergency braking is implemented, the pressure oil in the brake cylinder needs to flow back to the oil tank through a long pipeline, which poses a safety hazard of braking delay. To address this issue, existing technologies, such as patent CN106762922B, propose an external hydraulic quick-release valve solution. While this accelerates oil discharge by adding an independent valve block and a large-diameter quick-release channel, it essentially involves connecting a complex external functional module in series or parallel within the existing system. This results in a complex system structure, difficult spatial layout, and high manufacturing and maintenance costs. Furthermore, the introduction of additional connection points and potential failure points increases the overall leakage risk and reliability concerns. Therefore, the most pressing technical challenge is to eliminate the need for an externally attached complex valve assembly structure while ensuring rapid pressure relief braking performance. Instead, a highly integrated and unified design can be used to internalize the quick-release function within the braking actuator itself, thereby simplifying the system architecture, reducing the number of parts, lowering manufacturing costs and failure rates, and improving the overall reliability and ease of maintenance of the system. Based on this, the present invention provides a hydraulic quick-release structure for a monorail brake cylinder to solve the problems mentioned in the background art. Summary of the Invention

[0003] This invention addresses the technical problems existing in the prior art by providing a hydraulic quick-release structure for the brake cylinder of a monorail crane. This solves the problems of complex system structure, high cost, and additional failure points caused by the non-integrated design of the prior art.

[0004] The technical solution of this invention to solve the above-mentioned technical problems is as follows: A hydraulic quick-release structure for a monorail crane brake cylinder, comprising an outer cylinder and an inner cylinder connected to each other, and further comprising: An outer piston is slidably connected between an outer cylinder and an inner cylinder. The inner side of the outer cylinder has a drive oil chamber on the right side of the corresponding outer piston and an intermediate oil chamber on the left side of the corresponding outer piston. The bottom of the drive oil chamber is connected to an oil outlet pipe. A first spiral impeller is fixedly installed on the outer piston at the position corresponding to the drive oil chamber. The rotary drum is rotatably mounted between the outer cylinder and the inner cylinder via bearings. A torsion spring is provided at the rotatable connection between the rotary drum and the inner cylinder. An energy storage chamber is provided between the rotary drum and the outer cylinder. Energy storage blades are arrayed on the rotary drum at the positions corresponding to the energy storage chamber. An oil inlet pipe is connected to the bottom of the energy storage chamber, and an oil guide pipe is connected to the top of the energy storage chamber. The other end of the oil guide pipe is connected to the drive oil chamber. A gear is installed at the tail of the rotary drum. An electromagnetic actuator is fixedly mounted on an outer cylinder, and its output end is equipped with a toothed head that connects to a gear. An inner piston is slidably connected inside an inner cylinder. A piston rod is fixedly installed on the inner piston. Both the outer piston and the piston rod are linked with a rotating cylinder. Inside the inner cylinder, a balance air chamber is provided on the right side of the inner piston, and a driven oil chamber is provided on the left side of the inner piston. Multiple inlet check valves and multiple return check valves are installed on the inner cylinder between the intermediate oil chamber and the driven oil chamber, with the number of return check valves being greater than the number of inlet check valves. A second spiral impeller is installed on the inner piston at the position corresponding to the driven oil chamber. Energy storage springs are installed in both the intermediate oil chamber and the balance air chamber.

[0005] Based on the above technical solution, the present invention can be further improved as follows.

[0006] As a preferred embodiment of the present invention, both the oil outlet pipeline and the oil inlet pipeline are equipped with solenoid valves, and both the oil outlet pipeline and the oil inlet pipeline are provided with flange mounting faces at their bottom ends.

[0007] As a preferred embodiment of the present invention, a pump cylinder is fixedly installed on both the outer piston and the inner piston. The pump cylinder on the outer piston is connected to the first spiral impeller, and the pump cylinder on the inner piston is connected to the second spiral impeller.

[0008] As a preferred technical solution of the present invention, a spindle is fixedly installed at the axial position of the rotating drum, and a synchronization groove with a tail opening and sliding connection to the spindle is opened inside the piston rod. The cross-sections of the synchronization groove and the spindle are both regular polygons. A first sealing ring is fixedly installed on the outer periphery of the spindle, and the outer periphery of the first sealing ring is sealed and fitted with the synchronization groove.

[0009] As a preferred technical solution of the present invention, four synchronous slide rods are arrayed on the rotating drum. The axis of the synchronous slide rods is parallel to the axis of the outer cylinder. Guide holes are provided on the outer piston at the positions corresponding to the four synchronous slide rods. The four synchronous slide rods are slidably connected to the four guide holes respectively.

[0010] As a preferred embodiment of the present invention, a second sealing ring is fixedly installed on the outer peripheral surface of the outer piston, and a third sealing ring is fixedly installed on the inner wall surface. The outer peripheral surface of the second sealing ring is sealed and fitted with the inner wall surface of the outer cylinder, and the inner wall surface of the third sealing ring is sealed and fitted with the outer wall surface of the inner cylinder. A fourth sealing ring is fixedly installed on the inner wall of the inner cylinder, and the fourth sealing ring is sealed and fitted with the piston rod.

[0011] As a preferred embodiment of the present invention, the axes of the inlet check valve and the return check valve are both perpendicular to the axis of the inner cylinder.

[0012] As a preferred technical solution of the present invention, the inner cylinder is provided with four ventilation holes arranged in an array, all four ventilation holes being connected to the balance air chamber, the tail of the outer cylinder is fixedly installed with a first hinge seat, and the end of the piston rod is rotatably installed with a second hinge seat through a bearing.

[0013] As a preferred technical solution of the present invention, it further includes an oil return expansion assembly, which includes a balance cylinder. The other end of the balance cylinder is connected to the oil outlet pipeline. An oil port is provided at the connection between the balance cylinder and the oil outlet pipeline. The oil port is located between the flange mounting end face of the oil outlet pipeline and the solenoid valve. A balance piston is slidably connected inside the balance cylinder. A compensation air chamber is provided between the back of the balance piston and the balance cylinder. A pressure balance spring is installed inside the compensation air chamber. The tail end of the compensation air chamber is open.

[0014] The beneficial effects of this invention are: 1. This invention integrates the hydraulic quick discharge function into the brake cylinder body, abandoning the external independent valve group scheme, reducing external pipelines and connection nodes, simplifying the system space layout, reducing manufacturing costs and leakage risks, and improving the overall reliability and maintenance convenience of the device. At the same time, through the linkage of the rotating drum, double pistons and spiral impeller, combined with the coordinated energy release of torsion springs and energy storage springs, the oil is actively pumped to accelerate the return flow. With the help of a number of one-way valves with different numbers, the oil discharge rate is higher than the oil inlet rate, shortening the braking response time.

[0015] 2. This invention achieves the linkage transmission of rotation and linear motion through the spindle and synchronous slide bar. The transmission path is compact and highly integrated, eliminating the need for additional transmission components. The matching return oil expansion component can adaptively absorb the instantaneous return oil flow peak, buffer the hydraulic shock caused by energy release, optimize the smoothness of the fast discharge process, and better adapt to the working conditions of emergency braking of monorail cranes. Attached Figure Description

[0016] Figure 1 This is a schematic diagram of the overall structure of a hydraulic quick-release structure for a monorail crane brake cylinder according to the present invention; Figure 2 For the present invention Figure 1 A schematic diagram of the structure from an upward perspective; Figure 3 For the present invention Figure 2 A schematic diagram of the cross-sectional structure; Figure 4 For the present invention Figure 3 A magnified schematic diagram of the partial structure at point A in the middle; Figure 5 For the present invention Figure 3 A magnified schematic diagram of the local structure at point B; Figure 6 This is a schematic diagram of the structure of the compensation air chamber and oil outlet pipeline of the present invention; Figure 7 This is a schematic diagram of the structure of the gear and electromagnetic actuator of the present invention; Figure 8 This is a schematic diagram of the structure of the rotating drum and oil guide pipe of the present invention; Figure 9 This is a schematic diagram of the structure of the outer piston and the first helical impeller of the present invention; Figure 10 This is a schematic diagram of the structure of the outer piston of the present invention; Figure 11 This is a schematic diagram of the structure of the rotating drum of the present invention; Figure 12 This is a schematic diagram of the piston rod of the present invention; Figure 13 This is a cross-sectional structural diagram of the electromagnetic driver of the present invention.

[0017] The attached diagram lists the components represented by each number as follows: 1. Outer cylinder; 2. Inner cylinder; 3. Outer piston; 4. Rotary drum; 5. Electromagnetic actuator; 6. Solenoid valve; 7. Pump barrel; 101. First hinge seat; 201. Inner piston; 202. Piston rod; 203. Balance air chamber; 204. Driven oil chamber; 205. Inlet check valve; 206. Return check valve; 207. Second spiral impeller; 208. Energy storage spring; 209. Vent hole; 210. Second hinge 301. Drive oil chamber; 302. Intermediate oil chamber; 303. First spiral impeller; 304. Balance cylinder; 305. Balance piston; 306. Compensating air chamber; 307. Pressure balance spring; 308. Oil outlet pipe; 401. Torsion spring; 402. Accumulator blade; 403. Oil inlet pipe; 404. Oil guide pipe; 405. Spindle; 406. Gear; 407. Synchronous slide bar; 501. Tooth head. Detailed Implementation

[0018] The principles and features of the present invention are described below with reference to the accompanying drawings. The examples given are only for explaining the present invention and are not intended to limit the scope of the present invention.

[0019] The present invention provides the following preferred embodiments. like Figures 1-13 As shown, a hydraulic quick-release structure for a monorail crane brake cylinder includes an outer cylinder 1 and an inner cylinder 2 connected to each other. A first hinge seat 101 is fixedly installed at the tail of the outer cylinder 1. The structure also includes: The outer piston 3 is slidably connected between the outer cylinder 1 and the inner cylinder 2; A second sealing ring is fixedly installed on the outer peripheral surface of the outer piston 3, and a third sealing ring is fixedly installed on the inner wall surface. The outer peripheral surface of the second sealing ring is sealed and fitted with the inner wall surface of the outer cylinder 1, and the inner wall surface of the third sealing ring is sealed and fitted with the outer wall surface of the inner cylinder 2. The inner side of the outer cylinder 1 is provided with a drive oil chamber 301 on the right side of the corresponding outer piston 3 and an intermediate oil chamber 302 on the left side of the corresponding outer piston 3. The bottom of the drive oil chamber 301 is connected to an oil outlet pipe 308. The outer piston 3 is fixedly installed with a first spiral impeller 303 at the position corresponding to the drive oil chamber 301. Rotary drum 4 is rotatably mounted between outer cylinder 1 and inner cylinder 2 via bearings. A torsion spring 401 is provided at the rotatable connection between rotary drum 4 and inner cylinder 2. An energy storage chamber is provided between rotary drum 4 and outer cylinder 1. Energy storage blades 402 are arrayed on rotary drum 4 at positions corresponding to the energy storage chamber. An oil inlet pipe 403 is connected to the bottom of the energy storage chamber, and an oil guide pipe 404 is connected to the top. The other end of the oil guide pipe 404 is connected to the drive oil chamber 301. A spindle 405 is fixedly mounted at the axial position of rotary drum 4, and a gear 406 is mounted at the tail of rotary drum 4. The electromagnetic actuator 5 is fixedly mounted on the outer cylinder 1, and its output end is equipped with a tooth 501 that is connected to the gear 406. The electromagnetic actuator 5 includes a fixed electromagnet and a floating moving magnet. The tooth 501 is mounted on the moving magnet. A return spring is installed between the moving magnet and the outer cylinder 1. When the electromagnet is energized, it generates a repulsive force on the moving magnet. When the electromagnet is de-energized, the moving magnet automatically returns to its original position under the action of the return spring. The inner piston 201 is slidably connected inside the inner cylinder 2. The piston rod 202 is fixedly installed on the inner piston 201. The end of the piston rod 202 is rotatably installed with a second hinge seat 210 through a bearing. The inner wall of the inner cylinder 2 is fixedly installed with a fourth sealing ring, which is sealed and fitted with the piston rod 202. Both the outer piston 3 and the piston rod 202 are linked to the rotating cylinder 4; Specifically, the piston rod 202 has a timing groove with an open end and sliding connection to the spindle 405. The cross-sections of the timing groove and the spindle 405 are both regular polygons. A first sealing ring is fixedly installed on the outer periphery of the spindle 405, and the outer periphery of the first sealing ring is sealed and fitted with the timing groove.

[0020] Four synchronous slide rods 407 are arrayed on the rotating drum 4. The axis of the synchronous slide rods 407 is parallel to the axis of the outer cylinder 1. Guide holes are provided on the outer piston 3 at the positions corresponding to the four synchronous slide rods 407. The four synchronous slide rods 407 are slidably connected to the four guide holes respectively. The inner cylinder 2 has a balance air chamber 203 located on the right side of the inner piston 201 and a driven oil chamber 204 located on the left side of the inner piston 201. The inner cylinder 2 has four vent holes 209 arranged in an array, and all four vent holes 209 are connected to the balance air chamber 203. Multiple oil inlet check valves 205 and multiple oil return check valves 206 are installed on the inner cylinder 2 between the intermediate oil chamber 302 and the driven oil chamber 204, and the number of oil return check valves 206 is greater than the number of oil inlet check valves 205. In a preferred embodiment, the number of return oil check valves 206 is six, and the number of inlet oil check valves 205 is two; The flow area of ​​a single return check valve 206 is the same as that of a single inlet check valve 205; The axes of the inlet check valve 205 and the return check valve 206 are both perpendicular to the axis of the inner cylinder 2; Solenoid valves 6 are installed in both the oil outlet line 308 and the oil inlet line 403, and flange mounting faces are provided at the bottom of both the oil outlet line 308 and the oil inlet line 403. By setting the inlet check valve 205, the hydraulic oil in the intermediate oil chamber 302 can flow into the driven oil chamber 204 in one direction. By setting the return check valve 206, the hydraulic oil in the driven oil chamber 204 can flow back to the intermediate oil chamber 302 in one direction. A second spiral impeller 207 is installed on the inner piston 201 at the position corresponding to the driven oil chamber 204, and energy storage springs 208 are installed in both the intermediate oil chamber 302 and the balance air chamber 203. Pump cylinders 7 are fixedly installed on both the outer piston 3 and the inner piston 201. The pump cylinder 7 on the outer piston 3 is connected to the first spiral impeller 303, and the pump cylinder 7 on the inner piston 201 is connected to the second spiral impeller 207.

[0021] Both the first spiral impeller 303 and the second spiral impeller 207 are spiral blade structures, with their blades extending spirally along the axial direction. They are fixedly connected to the corresponding pistons through the pump barrel 7. When the piston and the spindle 405 rotate relative to each other, the spiral blades push the oil to flow axially in a directional manner. During operation, this structure is also equipped with an oil tank, on which a supply hydraulic pump and a return hydraulic pump are installed respectively. The oil outlet port of the supply hydraulic pump is connected to the oil inlet pipe 403 through the flange mounting end face, and the oil suction port of the return hydraulic pump is connected to the oil outlet pipe 308 through the flange mounting end face. When the piston rod 202 needs to be extended from the inner cylinder 2, the solenoid valve 6 in the oil outlet line 308 is closed, the solenoid valve 6 in the oil inlet line 403 is opened, the electromagnetic actuator 5 drives the tooth head 501 to fully reset, the gear 406 rotates freely, the oil supply hydraulic pump works, and then continuously supplies oil to the energy storage chamber. When the oil supply hydraulic pump supplies oil, the rotating drum 4 is driven by the energy storage blade 402, the torsion spring 401 is twisted by force and begins the first stage of energy storage, and the two energy storage springs 208 perform the second stage of energy storage. When the oil supply hydraulic pump is closed, the electromagnetic actuator 5 works and pushes the tooth head 501 out to brake the gear 406. When it is necessary to drive the piston rod 202 to return to the inner cylinder 2, that is, to achieve the rapid discharge of hydraulic oil in the driven oil chamber 204, the solenoid valve 6 on the oil inlet pipe 403 is closed and the solenoid valve 6 on the oil outlet pipe 308 is opened. After that, the return hydraulic pump works. When the return hydraulic pump works, the electromagnetic driver 5 drives the tooth head 501 to return to the original position, the gear 406 loses its brake, the torsion spring 401 and the energy storage spring 208 release energy at the same time, and the first spiral impeller 303 and the second spiral impeller 207 rotate to achieve the rapid discharge of hydraulic oil in the driven oil chamber 204 to the intermediate oil chamber 302 and the driving oil chamber 301. Meanwhile, due to the setting of the return oil check valve 206 and the inlet oil check valve 205, the oil inlet speed of the driven oil chamber 204 is lower than the oil outlet speed. It also includes a return oil expansion assembly, which includes a balance cylinder 304. The other end of the balance cylinder 304 is connected to the oil outlet pipeline 308. An oil port is provided at the connection between the balance cylinder 304 and the oil outlet pipeline 308. The oil port is located between the flange mounting end face of the oil outlet pipeline 308 and the solenoid valve 6. A balance piston 305 is slidably connected inside the balance cylinder 304. A compensation air chamber 306 is provided between the back of the balance piston 305 and the balance cylinder 304. A pressure balance spring 307 is installed inside the compensation air chamber 306. The tail end of the compensation air chamber 306 is open.

[0022] When the solenoid valve 6 of the oil outlet line 308 is opened and the system enters the rapid oil discharge stage, the oil in the drive oil chamber 301 and the driven oil chamber 204 converges into the oil outlet line 308 under the kinetic energy released by the torsion spring 401 and the energy storage spring 208. If the instantaneous return oil flow exceeds the fixed suction capacity of the return oil hydraulic pump, the pressure in the pipeline will increase instantaneously. At this time, the balance piston 305 in this component can compress the pressure balance spring 307 under the action of oil pressure and move towards the compensation air chamber 306 to temporarily expand the volume and absorb part of the flow and pressure fluctuations. After the instantaneous peak, the pressure balance spring 307 pushes the piston to reset, slowly discharging the temporarily stored oil. The above structure provides the system with a passive and adaptive pressure buffer and flow regulation mechanism, which helps to improve the hydraulic shock caused by the instantaneous release of energy, making the entire rapid oil discharge process smoother.

[0023] The specific steps for using this invention are as follows: Before operation, the first hinge seat 101 and the second hinge seat 210 are respectively used to hingely connect to one end of the left brake lever and the right brake lever in the monorail braking device. The other end of the brake lever is connected to the brake block, and the brake lever has a fixed fulcrum in the middle. Therefore, the brake cylinder transmits hydraulic thrust or spring braking force to the left and right brake levers through the first hinge seat 101 and the second hinge seat 210 at both ends, thereby driving the brake block to press or disengage from the guide rail, realizing the braking and release function of the monorail. When it is necessary to drive the piston rod 202 to extend from the inner cylinder 2 to perform the braking action, the solenoid valve 6 in the oil outlet pipe 308 is closed and the solenoid valve 6 on the oil inlet pipe 403 is opened, and at the same time the electromagnetic actuator 5 drives... Its tooth head 501 is fully reset to release the brake on the tail gear 406 of the rotating drum 4. At this time, the external oil supply hydraulic pump continuously pumps hydraulic oil into the energy storage chamber through the oil inlet pipe 403. The oil pushes the energy storage blades 402 arrayed on the rotating drum 4 to make the rotating drum 4 rotate against the resistance of the torsion spring 401, completing the first stage of mechanical torsion spring 401 energy storage. At the same time, the oil enters the drive oil chamber 301 through the guide oil pipe 404 at the top of the energy storage chamber and pushes the outer piston 3, which is slidably connected between the outer cylinder 1 and the inner cylinder 2, to move to the left. This process compresses the energy storage spring 208 located in the intermediate oil chamber 302 and the balance air chamber 203, completing the second stage of energy storage. At the same time, the inner piston 201 moves to the right, and the energy storage spring 208 in the balance air chamber 203 synchronously completes the compression and energy storage. When the piston rod 202 reaches the required stroke, the oil supply hydraulic pump stops working, the electromagnetic actuator 5 then moves and pushes out the tooth 501 to mesh with the gear 406, locking the entire transmission mechanism and putting the device into a pressure holding standby state. When the piston rod 202 needs to be quickly reset and retracted into the inner cylinder 2, the rapid oil discharge process is initiated. At this time, the solenoid valve 6 on the oil inlet pipe 403 is closed, the solenoid valve 6 on the oil outlet pipe 308 is opened, the external return hydraulic pump starts to suck, and at the same time, the electromagnetic actuator 5 drives the tooth head 501 to reset to release the gear 406. At the moment the brake is released, the mechanical potential energy stored in the torsion spring 401 and the energy storage spring 208 is released simultaneously, driving the rotating drum 4 to reverse at high speed and driving the outer piston 3 to move quickly to the right. During this process, the first spiral impeller 303 and the second spiral impeller 207 installed on the outer piston 3 and the inner piston 201 rotate at high speed, generating a strong pumping and pushing effect in the driving oil chamber 301 and the driven oil chamber 204. This action forces a large amount of hydraulic oil in the driven oil chamber 204 to flow back quickly to the intermediate oil chamber 302 at a higher speed than the inlet oil through a greater number of return oil check valves 206. This further acts on the hydraulic oil in the drive oil chamber 301 to be discharged quickly. Finally, the hydraulic oil flows into the opened outlet oil line 308 and is drawn away by the return oil hydraulic pump, achieving rapid discharge of hydraulic oil. To cope with the peak pressure in the pipeline caused by the instantaneous release of energy, the return oil expansion component installed on the outlet oil line 308 automatically starts working. When the instantaneous return oil flow exceeds the suction capacity of the return oil hydraulic pump, the oil pressure will push the balance piston 305 in the balance cylinder 304 to compress the pressure balance spring 307 on its back, temporarily expanding the volume to absorb the impact. After the peak, the pressure balance spring 307 pushes the balance piston 305 to reset, slowly discharging the temporarily stored oil, thereby ensuring that the entire rapid oil discharge process is stable and efficient.

[0024] The above are merely preferred embodiments of the present invention and are not intended to limit the present invention. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of the present invention should be included within the protection scope of the present invention.

Claims

1. A hydraulic quick-release structure for a monorail crane brake cylinder, comprising an outer cylinder (1) and an inner cylinder (2) connected to each other, characterized in that, Also includes: The outer piston (3) is slidably connected between the outer cylinder (1) and the inner cylinder (2). The inner side of the outer cylinder (1) is provided with a drive oil chamber (301) on the right side of the corresponding outer piston (3) and an intermediate oil chamber (302) on the left side of the corresponding outer piston (3). The bottom of the drive oil chamber (301) is connected to an oil outlet pipe (308). The outer piston (3) is fixedly installed with a first spiral impeller (303) at the position corresponding to the drive oil chamber (301). A rotating drum (4) is rotatably mounted between an outer cylinder (1) and an inner cylinder (2) via a bearing. A torsion spring (401) is provided at the rotatable connection between the rotating drum (4) and the inner cylinder (2). An energy storage chamber is provided between the rotating drum (4) and the outer cylinder (1). Energy storage blades (402) are arrayed on the rotating drum (4) at the positions corresponding to the energy storage chamber. An oil inlet pipe (403) is connected to the bottom of the energy storage chamber, and an oil guide pipe (404) is connected to the top. The other end of the oil guide pipe (404) is connected to the drive oil chamber (301). A gear (406) is installed at the tail of the rotating drum (4). The electromagnetic actuator (5) is fixedly installed on the outer cylinder (1), and its output end is equipped with a tooth (501) connected to the gear (406). The inner piston (201) is slidably connected inside the inner cylinder (2). The piston rod (202) is fixedly installed on the inner piston (201). The outer piston (3) and the piston rod (202) are both linked with the rotating drum (4). The inner cylinder (2) has a balance air chamber (203) on the right side of the inner piston (201) and a driven oil chamber (204) on the left side of the inner piston (201). Multiple oil inlet check valves (205) and multiple oil return check valves (206) are installed on the inner cylinder (2) between the intermediate oil chamber (302) and the driven oil chamber (204). The number of oil return check valves (206) is greater than the number of oil inlet check valves (205). The inner piston (201) has a second spiral impeller (207) installed on the position corresponding to the driven oil chamber (204). Energy storage springs (208) are installed in both the intermediate oil chamber (302) and the balance air chamber (203).

2. The hydraulic quick-release structure for a monorail crane brake cylinder according to claim 1, characterized in that, Solenoid valves (6) are installed in both the oil outlet pipeline (308) and the oil inlet pipeline (403), and flange mounting faces are provided at the bottom ends of both the oil outlet pipeline (308) and the oil inlet pipeline (403).

3. The hydraulic quick-release structure for a monorail crane brake cylinder according to claim 1, characterized in that, Pump cylinders (7) are fixedly installed on both the outer piston (3) and the inner piston (201). The pump cylinder (7) on the outer piston (3) is connected to the first spiral impeller (303), and the pump cylinder (7) on the inner piston (201) is connected to the second spiral impeller (207).

4. The hydraulic quick-release structure for a monorail crane brake cylinder according to claim 1, characterized in that, A spindle (405) is fixedly installed at the axial position of the rotating drum (4). The piston rod (202) has a timing groove with an open tail end that is slidably connected to the spindle (405). The cross-sections of the timing groove and the spindle (405) are both regular polygons. A first sealing ring is fixedly installed on the outer periphery of the spindle (405). The outer periphery of the first sealing ring is sealed and fitted with the timing groove.

5. The hydraulic quick-release structure for a monorail crane brake cylinder according to claim 1, characterized in that, Four synchronous slide rods (407) are arrayed on the rotating drum (4). The axis of the synchronous slide rod (407) is parallel to the axis of the outer cylinder (1). The outer piston (3) has guide holes at the positions corresponding to the four synchronous slide rods (407). The four synchronous slide rods (407) are slidably connected to the four guide holes respectively.

6. The hydraulic quick-release structure for a monorail crane brake cylinder according to claim 1, characterized in that, The outer piston (3) is fixedly installed with a second sealing ring on its outer circumferential surface and a third sealing ring on its inner wall surface. The outer circumferential surface of the second sealing ring is sealed and fitted with the inner wall surface of the outer cylinder (1). The inner wall surface of the third sealing ring is sealed and fitted with the outer wall surface of the inner cylinder (2). The inner wall of the inner cylinder (2) is fixedly installed with a fourth sealing ring. The fourth sealing ring is sealed and fitted with the piston rod (202).

7. The hydraulic quick-release structure for a monorail crane brake cylinder according to claim 1, characterized in that, The axes of the inlet check valve (205) and the return check valve (206) are both perpendicular to the axis of the inner cylinder (2).

8. The hydraulic quick-release structure for a monorail crane brake cylinder according to claim 1, characterized in that, The inner cylinder (2) has four air holes (209) arranged in an array. All four air holes (209) are connected to the balance air chamber (203). The tail of the outer cylinder (1) is fixedly installed with a first hinge seat (101). The end of the piston rod (202) is rotatably installed with a second hinge seat (210) through a bearing.

9. A hydraulic quick-release structure for a monorail crane brake cylinder according to claim 1, characterized in that, It also includes a return oil expansion assembly, which includes a balance cylinder (304). The other end of the balance cylinder (304) is connected to the oil outlet pipeline (308). An oil port is provided at the connection between the balance cylinder (304) and the oil outlet pipeline (308). The oil port is located between the flange mounting end face of the oil outlet pipeline (308) and the solenoid valve (6). A balance piston (305) is slidably connected inside the balance cylinder (304). A compensation air chamber (306) is provided between the back of the balance piston (305) and the balance cylinder (304). A pressure balance spring (307) is installed inside the compensation air chamber (306). The tail end of the compensation air chamber (306) is open.

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