Press flywheel system and lubricating method thereof

Abstract

The invention relates to a press flywheel system and a lubricating method thereof, and belongs to the field of press equipment.The technical scheme is that the press flywheel system comprises a power shaft, the power shaft is provided with a flywheel assembly and a brake assembly, the flywheel assembly comprises a supporting sleeve, the power shaft is rotatably installed in an inner hole of the supporting sleeve, and the brake assembly is arranged in the supporting sleeve; a flywheel is mounted on the periphery of the power shaft through two bearings; the brake assembly comprises a clutch sleeve, and the right end face of the clutch sleeve is concentrically and fixedly connected with the left end face of the flywheel. The clutch sleeve is connected with an oil inlet pipeline, a lubricating hole channel is formed in the supporting sleeve, one end of the lubricating hole channel is communicated with the right end of the gap between the supporting sleeve and the flywheel, and the other end of the lubricating hole channel is connected with a first oil return pipeline. According to the system, the bearing clearance of the flywheel assembly is opened and communicated with the inner cavity of the clutch sleeve, hydraulic oil of the clutch forcibly enters the bearing clearance of the flywheel in an oil drainage mode, the hydraulic oil serves as lubricating oil, and the oil flow at the flywheel is greatly increased.

Description

Technical Field

[0001] This invention relates to the field of press equipment, and in particular to a press flywheel system and its lubrication method. Background Technology

[0002] The flywheel is a core component of a press. Its primary function is to store and release rotational inertia to balance energy fluctuations during press operation, ensuring stable and efficient equipment operation. During the stamping process, a large amount of energy is consumed instantaneously. The flywheel stores excess energy from the motor as kinetic energy during non-stamping phases and releases it rapidly during stamping, compensating for insufficient instantaneous motor output power and preventing motor damage due to sudden load increases. The clutch connects the flywheel to the power shaft and controls the transmission and disconnection of power. When the press needs to perform a stamping action, the clutch engages, transferring the kinetic energy stored in the flywheel to the power shaft, driving the slide to complete the stamping. When stamping is finished or the equipment needs adjustment, the clutch disengages, cutting off power transmission and preventing the flywheel's inertia from continuously driving the actuator.

[0003] Currently, flywheels generally use conventional intermittent thin oil lubrication. This lubrication method uses thin oil as the lubricating medium and delivers lubricating oil intermittently to the bearing part of the flywheel support sleeve through a specific oil supply system. This forms an oil film to reduce internal friction and wear of the bearing. At the same time, the flow of lubricating oil carries away some of the heat generated during operation, maintaining the normal operating temperature of the bearing and ensuring the stable operation of the flywheel and the entire press system.

[0004] As industrial production demands higher efficiency, the operating cycle of presses is constantly accelerating. The shortcomings of traditional intermittent thin oil lubrication are becoming increasingly apparent, and it can no longer meet the needs of high-cycle presses. The flow rate of intermittent thin oil lubrication is generally 1L / min. However, when the speed of the press's power shaft exceeds 350rpm, the heat generated by bearing friction cannot be carried away by the lubricating oil in time, causing the bearing temperature to rise sharply. This leads to the equipment malfunctioning and severely limits the increase in the press's operating speed. Summary of the Invention

[0005] This invention addresses the problem that current press flywheel lubrication methods cannot meet the heat dissipation requirements of high-speed operation by providing a press flywheel system with high-flow-rate heat dissipation.

[0006] To solve the above problems, the technical solution adopted by the present invention is as follows: a press flywheel system, including a power shaft, on which a flywheel assembly and a braking assembly are provided. The braking assembly is located on the left side of the flywheel assembly. The flywheel assembly includes a support sleeve. The power shaft is rotatably installed in the inner hole of the support sleeve. A flywheel is mounted on the outer periphery of the support sleeve through two bearings, and an oil passage gap is formed between the flywheel and the support sleeve. The braking assembly includes a clutch sleeve. The right end face of the clutch sleeve is concentrically fixedly connected to the left end face of the flywheel. The inner cavity of the clutch sleeve communicates with the left end of the oil passage gap. The clutch sleeve is connected to an oil inlet pipe. A lubrication channel is provided in the support sleeve. One end of the lubrication channel communicates with the right end of the oil passage gap, and the other end of the lubrication channel is connected to a return oil pipe. The return oil pipe and the oil inlet pipe are connected to a pump station oil tank. This system integrates the flywheel assembly and the braking assembly, opens the oil passage gap of the flywheel assembly and connects it to the inner cavity of the clutch sleeve, and constructs the hydraulic drive of the clutch and the lubrication of the flywheel into an integrated lubrication system. The hydraulic oil of the clutch is forced into the oil passage gap between the bearings by the oil discharge method. Using hydraulic oil as lubricant, the oil flow at the flywheel is greatly increased, and uninterrupted lubrication is achieved. At the same time, this system integrates the flywheel assembly and the braking assembly, which significantly reduces the size of the equipment.

[0007] As a preferred implementation of a press flywheel system, an inner spacer and an outer spacer are provided between the two bearings. The inner spacer is fitted around the outer circumference of the support sleeve, and its two ends abut against the inner rings of the two bearings, respectively. The outer spacer is disposed on the inner wall of the flywheel, and its two ends abut against the outer rings of the two bearings, respectively. A certain distance is maintained between the outer surface of the inner spacer and the inner surface of the outer spacer. The cooperation between the inner and outer spacers precisely positions the relative positions of the two bearings, preventing axial movement during operation, ensuring the coaxiality and stability of the flywheel, and improving the stamping accuracy of the press. Simultaneously, the reserved gap between the two spacers forms a dedicated oil channel, allowing hydraulic oil to flow more smoothly between the two bearings, ensuring sufficient lubrication for each bearing, further optimizing heat dissipation, and preventing bearing damage caused by localized lubrication dead zones.

[0008] As a preferred implementation of a press flywheel system, the left end of the oil passage gap is provided with an outer bearing retaining ring and an inner bearing retaining ring. The outer bearing retaining ring is fixedly connected to the left end face of the flywheel and abuts against the outer ring of the bearing located on the left side. The inner bearing retaining ring is fixedly connected to the left end of the outer circumferential surface of the support sleeve and abuts against the inner ring of the bearing located on the left side. An oil inlet gap is formed between the inner edge of the outer bearing retaining ring and the outer edge of the inner bearing retaining ring. The outer and inner bearing retaining rings can provide double axial fixation for the left bearing, preventing displacement of the bearing during high-speed operation and ensuring the assembly stability of the bearing, flywheel, and support sleeve. The gap reserved between them provides a precise inflow channel for hydraulic oil in the clutch sleeve, ensuring that the hydraulic oil can enter the oil passage gap in a directional manner. This avoids oil waste and lubrication failure caused by oil circuit blockage. At the same time, it eliminates the need for an additional skeleton seal, reducing maintenance costs caused by seal wear and avoiding the problem of traditional sealing structures hindering oil flow.

[0009] As a preferred implementation of a press flywheel system, an inner shaft sealing plate is provided at the right end of the oil passage gap. The inner edge of the inner shaft sealing plate is fixedly connected to the outer circumferential surface of the support sleeve, and the outer edge of the inner shaft sealing plate is fitted against the right end face of the flywheel. An outer shaft sealing plate is also installed on the right end face of the flywheel, and the outer shaft sealing plate is pressed against the right outer circumference of the inner shaft sealing plate. A rotary sealing ring is provided between the outer shaft sealing plate and the inner shaft sealing plate. The sealing structure composed of the inner shaft sealing plate, the outer shaft sealing plate, and the rotary sealing ring can effectively prevent hydraulic oil in the oil passage gap from leaking from the right end of the flywheel, avoiding insufficient lubrication and environmental pollution caused by oil loss. At the same time, it prevents external impurities from entering the oil passage gap and protects the bearing from wear. In addition, the rotary sealing ring is suitable for high-speed operation of the flywheel, has stable sealing performance, does not require frequent replacement, reduces equipment maintenance frequency and cost, and ensures long-term efficient operation of the lubrication system.

[0010] As a preferred implementation of a press flywheel system, the lubrication channel is U-shaped, with its two ends located on either side of the inner shaft seal plate. The U-shaped lubrication channel allows for unidirectional circulation of hydraulic oil within the oil passage gap. One end receives oil flowing from the bearing, while the other end guides the oil to the return oil pipe, preventing oil stagnation inside the support sleeve and ensuring unobstructed oil flow. Simultaneously, the two ends of the channel, located on either side of the inner shaft seal plate, can cooperate with the sealing structure, both preventing oil leakage and quickly discharging hot oil through the channel, further improving heat dissipation efficiency and ensuring stable bearing temperature at high speeds.

[0011] As a preferred implementation of a press flywheel system, the support sleeve is further provided with an oil drain channel. The left end of the oil drain channel is located on the left end face of the support sleeve, and the right end is located on the right side of the outer circumference of the support sleeve. The right end of the oil drain channel is connected to a second oil return pipe, which is connected to the pump station oil tank. The auxiliary oil return system composed of the oil drain channel and the second oil return pipe can divert excess hydraulic oil in the clutch sleeve, preventing excessively high oil pressure in the system due to the oil inlet volume exceeding the oil return volume of the first oil return pipe, thus preventing oil circuit blockage or seal damage. At the same time, the auxiliary oil return can further accelerate the oil circulation speed, improve heat dissipation efficiency, and ensure that the bearing temperature is always within a safe range. In addition, excess oil flows back to the pump station oil tank through a dedicated channel, avoiding oil waste and reducing the user's oil replenishment costs.

[0012] As a preferred implementation of a press flywheel system, a pressure relief valve is also provided at the right end of the oil drain channel, which is connected to the interior of the oil drain channel. The pressure relief valve can automatically adjust its opening state according to the oil pressure in the system. When the oil pressure exceeds a preset value, the pressure relief valve opens to quickly divert excess oil, preventing damage to the clutch, bearings, and seals due to excessive oil pressure and ensuring the safety of system operation. When the oil pressure returns to normal, the pressure relief valve closes, ensuring that the oil preferentially flows through the return oil pipe to provide lubrication to the bearings, avoiding insufficient lubrication due to excessive oil diversion. This achieves the dual functions of pressure protection and lubrication guarantee, improving the stability and reliability of system operation.

[0013] As a preferred implementation of a press flywheel system, the braking assembly further includes a clutch body, which comprises a rotating side and a fixed side. The rotating side rotates synchronously with the power shaft, and the fixed side is coaxially and fixedly connected to the support sleeve. An oil inlet channel is provided on the left side of the power shaft. The right end of the oil inlet channel is located on the outer circumferential surface of the power shaft and within the inner cavity of the clutch sleeve. The left end of the oil inlet channel is located on the left end face of the power shaft and is equipped with a rotary joint. The oil inlet pipe is connected to the rotary joint. The oil inlet channel inside the power shaft, in conjunction with the rotary joint, enables stable oil supply when the power shaft rotates at high speed. Simultaneously, the oil inlet channel directly delivers oil to the inner cavity of the clutch sleeve, shortening the oil path distance, reducing oil pressure loss, and improving lubrication and drive efficiency.

[0014] On the other hand, the present invention also provides a lubrication method for a press flywheel system, comprising the following steps: S1. The pump station oil tank supplies oil through the oil inlet pipe and the power axial clutch sleeve to lubricate the braking components; S2. Hydraulic oil flows through the inlet gap, through the bearing on the left, into the oil passage gap, and then through the bearing on the right, thus lubricating the two bearings and the flywheel. S3. The hydraulic oil passes through the lubrication channel and enters the return oil pipeline 1 under the obstruction of the inner shaft seal pressure plate and the outer shaft seal pressure plate, and flows back to the pump station oil tank.

[0015] When the amount of oil injected into the clutch sleeve exceeds the amount of oil returned through the first return oil pipe, the pressure relief valve opens, and the excess oil enters the second return oil pipe through the drain hole and flows back to the pump station oil tank.

[0016] This lubrication method achieves synchronization between power input and lubrication. Step S1 provides drive hydraulic oil to the clutch while simultaneously reserving oil for subsequent lubrication, eliminating the need to start the lubrication system and simplifying the operation process. Step S2, through a directional oil circuit design, ensures that the hydraulic oil fully covers both bearings, avoiding lubrication dead zones and improving lubrication uniformity. Step S3, in conjunction with the pressure relief valve, prevents oil leakage through a sealing structure and diverts excess oil through dual return channels, ensuring smooth oil flow and stable system pressure. The overall method has clear logic, a high degree of automation, and can adapt to the high-cycle operation requirements of presses, while reducing manual intervention costs and minimizing equipment failures caused by operational errors.

[0017] As can be seen from the above technical solutions, the beneficial effects of this invention are as follows: By integrating the flywheel assembly and braking assembly, and using the clutch hydraulic oil as the flywheel bearing lubricant, this system achieves the integration of hydraulic drive and lubrication, significantly increasing the oil flow at the flywheel and achieving uninterrupted lubrication. This effectively solves the problem of insufficient lubrication in traditional intermittent systems, allowing the power shaft speed to adapt to the high-frequency operation of the press. Simultaneously, the integrated design significantly reduces the equipment size, the number of parts, and system complexity, lowering manufacturing costs. The cooperation between the inner and outer spacers precisely positions the bearing, ensuring the coaxiality of the flywheel and stamping accuracy, while also forming a dedicated oil channel to ensure uniform lubrication and optimized heat dissipation. The outer and inner bearing retaining rings, while fixing the bearing and preventing high-speed displacement, reserve an oil inlet gap for the directional flow of hydraulic oil, eliminating the need for a skeleton seal to reduce maintenance costs and oil passage obstruction. The sealing structure composed of the inner shaft seal plate, the outer shaft seal plate, and the rotary seal ring prevents oil leakage and impurity intrusion, adapting to high-speed operation. Reduced maintenance frequency; U-shaped lubrication channels enable unidirectional oil circulation, preventing oil stagnation and improving heat dissipation efficiency with a sealing structure, ensuring stable bearing performance at high temperatures; an auxiliary oil return system composed of drain channels and return pipes diverts excess oil to prevent excessive system oil pressure and oil waste, further accelerating oil circulation and heat dissipation; the pressure relief valve automatically adjusts according to oil pressure, achieving dual functions of pressure protection and lubrication assurance, improving system safety and reliability; the internal oil inlet channel of the power shaft, in conjunction with the rotary joint, ensures stable oil supply under high-speed operation, shortening the oil path distance to reduce pressure loss and improve efficiency; the corresponding lubrication method achieves synchronization of power input and lubrication, simplifying the operation process; the directional oil path design avoids lubrication dead zones; the dual return oil channels, in conjunction with the pressure relief valve, ensure smooth oil flow and stable pressure; high degree of automation reduces manual intervention costs and operational error risks; it also solves the problem of cross-contamination between clutch hydraulic oil and bearing lubricating oil in traditional structures, reducing user oil change costs and extending the service life of components and oil. Attached Figure Description

[0018] To more clearly illustrate the technical solution of this patent, the drawings used in the description will be briefly introduced below. Obviously, the drawings described below are only some embodiments of this patent. For those skilled in the art, other drawings can be obtained from these drawings without creative effort.

[0019] Figure 1 This is a schematic diagram of the structure of Embodiment 1 of the present invention.

[0020] Figure 2 for Figure 1 Enlarged view of point A in the middle.

[0021] Figure 3 This is a schematic diagram of the support sleeve in Embodiment 1 of the present invention.

[0022] Explanation of main figure symbols 01. Flywheel assembly, 02. Brake assembly, 03. Oil passage clearance, 04. Oil inlet clearance, 1. Support sleeve, 2. Inner shaft seal plate, 3. Rotary seal ring, 4. Outer shaft seal plate, 5. Flywheel, 6. Outer spacer, 7. Inner spacer, 8. Bearing, 9. Outer bearing retaining ring, 10. Inner bearing retaining ring, 11. Clutch body, 112. Rotating side, 111. Fixed side, 12. Clutch sleeve, 13. Rotary joint, 14. Power shaft, 15. Oil inlet pipe, 16. Oil return pipe one, 17. Oil return pipe two, 18. Pump station oil tank, 19. Lubrication channel, 20. Oil drain channel, 21. Pressure relief valve, 22. Oil inlet channel. Detailed Implementation

[0023] To make the objectives, features, and advantages of this patent more apparent and understandable, the technical solutions of this patent will be clearly and completely described below with reference to the accompanying drawings of the specific embodiments. Obviously, the embodiments described below are only some embodiments of this patent, and not all embodiments. Based on the embodiments of this patent, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of this patent.

[0024] Example 1 like Figure 1-3 As shown, a press flywheel system includes a power shaft 14, on which a flywheel assembly 01 and a braking assembly 02 are mounted. The braking assembly 02 is integrated on the left side of the flywheel assembly 01. The integrated layout significantly reduces the size of the equipment. At the same time, the hydraulic drive of the clutch and the flywheel lubrication are integrated into a whole system, eliminating the need for an additional independent lubrication device and reducing system complexity and manufacturing costs.

[0025] The flywheel assembly 01 includes the support sleeve 1. The power shaft 14 is rotatably installed in the inner hole of the support sleeve 1. The flywheel 5 is mounted on the outer periphery of the power shaft 14 via two bearings 8. The two bearings 8 create an oil passage gap 03 between the flywheel 5 and the support sleeve 1, which allows for uninterrupted lubrication via hydraulic oil discharge through a clutch. This significantly increases the oil flow rate to efficiently remove heat, increasing the power shaft speed from 350 rpm to 450 rpm, meeting the high-cycle operation requirements of the press. Specifically... The inner spacer 7 and the outer spacer 6 are provided between the two bearings 8. The inner spacer 7 is fitted around the outer periphery of the support sleeve 1, and its two ends abut against the inner rings of the two bearings 8, respectively. The outer spacer 6 is disposed on the inner wall of the flywheel 5, and its two ends abut against the outer rings of the two bearings 8, respectively. This design can accurately position the bearings, prevent axial movement, ensure the coaxiality and stamping accuracy of the flywheel, and also form a dedicated oil channel through the certain distance between the two spacers, ensuring that each bearing receives adequate lubrication. Sufficient lubrication and optimized heat dissipation are achieved. The left end of the oil passage gap is equipped with an outer bearing retaining ring 9 and an inner bearing retaining ring 10. The outer bearing retaining ring 9 is fixedly connected to the left end face of the flywheel 5 and abuts against the outer ring of the left-side bearing 8. The inner bearing retaining ring 10 is fixedly connected to the left end of the outer circumferential surface of the support sleeve 1 and abuts against the inner ring of the left-side bearing 8. This double-fixed bearing design prevents high-speed displacement, while the gap between the two forms an oil inlet gap, providing a precise inflow channel for hydraulic oil, avoiding oil waste and blockage, and eliminating the need for additional... An external skeleton seal is provided to reduce maintenance costs; the right end of the oil passage gap 03 is provided with the inner shaft seal pressure plate 2, whose inner diameter is fixedly connected to the outer circumferential surface of the support sleeve 1 and whose outer edge is attached to the right end face of the flywheel 5. The right end face of the flywheel 5 is also equipped with the outer shaft seal pressure plate 4, which is pressed against the outer right side of the inner shaft seal pressure plate 2 and the rotating seal ring 3 is provided between the two. This sealing structure can effectively prevent oil leakage and impurity intrusion, is suitable for high-speed operation conditions and has stable sealing, reduces maintenance frequency, and ensures long-term efficient operation of the lubrication system.

[0026] The braking assembly includes the clutch sleeve 12, whose right end face is concentrically fixedly connected to the left end face of the flywheel 5, and whose inner cavity is connected to the left end of the oil passage gap 03; the clutch sleeve 12 is connected to the oil inlet pipe 15, and the support sleeve 1 is provided with the U-shaped lubrication channel 19, whose two ends are respectively located on both sides of the inner shaft seal plate 2, one end is connected to the right end of the oil passage gap 03, and the other end is connected to the return oil pipe 16, which can realize the one-way circulation of oil, avoid stagnation, and cooperate with the sealing structure to quickly discharge hot oil, ensuring the high temperature stability of the bearing. The return oil pipe 16 and the oil inlet pipe 15 are connected to the pump station oil tank 18.

[0027] The support sleeve 1 is also provided with the oil drain channel 20, with its left end located on the left end face of the support sleeve 1 and its right end located on the right side of the outer circumference of the support sleeve 1 and connected to the return oil pipe 2 17. It can divert excess hydraulic oil, avoid excessive system oil pressure and oil waste, and accelerate circulation and heat dissipation. The return oil pipe 2 17 is connected to the pump station oil tank 18. The right end of the oil drain channel 20 is also provided with the pressure relief valve 21 that leads into it. It can automatically adjust the opening state according to the oil pressure, realize the dual functions of pressure protection and lubrication guarantee, and improve the safety and reliability of system operation. The braking assembly 02 also includes the clutch body 11, which includes a rotating side 112 and a fixed side 111. The rotating side 112 rotates synchronously with the power shaft 14, and the fixed side 111 is coaxially and fixedly connected to the support sleeve 1. The power shaft 14 has an oil inlet channel 22 on its left side, with its right end located in the inner cavity of the clutch sleeve 12 and its left end opened on the left end face of the power shaft 14 and equipped with the rotary joint 13. The oil inlet pipe 15 is connected to it, which can stably supply oil when the power shaft rotates at high speed, avoid pipe entanglement and wear, shorten the oil circuit distance to reduce pressure loss, and improve lubrication and driving efficiency.

[0028] Example 2 A lubrication method for a press flywheel system includes the following steps: S1. The pump station oil tank 18 supplies oil to the clutch sleeve 12 through the oil inlet pipe 15 and the power shaft 14 to lubricate the brake assembly 02, and at the same time reserve oil source for subsequent flywheel lubrication, without the need to start the lubrication system, thus simplifying the operation process; S2. Hydraulic oil flows through the inlet gap 04, passes through the left bearing 8, enters the oil passage gap 03 between the outer sleeve 6 and the inner sleeve 7, and then flows through the right bearing 8. The directional oil passage design achieves comprehensive lubrication of the two bearings 8 and the flywheel 5, avoids lubrication dead zones, and improves lubrication uniformity. S3. Hydraulic oil, blocked by the inner shaft seal plate 2 and the outer shaft seal plate 4, passes through the lubrication channel 19 and enters the return oil pipeline 16, flowing back to the pump station oil tank 18; when the oil injection volume of the clutch sleeve 12 exceeds the oil return volume of the return oil pipeline 16, the pressure relief valve 21 opens, and the excess oil enters the return oil pipeline 17 through the drain channel 20, flowing back to the pump station oil tank 18.

[0029] This design, through the cooperation of dual return oil channels and pressure relief valve, ensures smooth oil circuit and stable system pressure. The overall method has a high degree of automation, is suitable for high-speed operation of presses, and reduces the cost of manual intervention and the risk of operational errors.

[0030] As can be seen from the above embodiments, the advantages of this invention are as follows: By integrating the flywheel assembly and braking assembly, and using the clutch hydraulic oil as the flywheel bearing lubricant, this system achieves the integration of hydraulic drive and lubrication, significantly increasing the oil flow at the flywheel and achieving uninterrupted lubrication. This effectively solves the problem of insufficient lubricating oil in traditional intermittent systems, allowing the power shaft speed to adapt to the high-frequency operation of the press. Simultaneously, the integrated design significantly reduces the equipment size, the number of parts, and system complexity, lowering manufacturing costs. The cooperation between the inner and outer spacers precisely positions the bearing, ensuring the coaxiality of the flywheel and stamping accuracy, while also forming a dedicated oil channel to ensure uniform lubrication and optimized heat dissipation. The outer and inner bearing retaining rings, while fixing the bearing and preventing high-speed displacement, provide a clearance for the directional flow of hydraulic oil, eliminating the need for a skeleton seal and reducing maintenance costs and oil passage obstruction. The sealing structure composed of the inner shaft seal plate, outer shaft seal plate, and rotary seal ring prevents oil leakage and impurity intrusion, adapting to high-speed operation and reducing maintenance frequency. The U-shaped lubrication channel enables unidirectional oil circulation. The ring design prevents oil stagnation and, in conjunction with a sealing structure, improves heat dissipation efficiency, ensuring stable bearing operation at high temperatures. An auxiliary oil return system, consisting of a drain channel and a return pipe, diverts excess oil to prevent excessive system oil pressure and waste, further accelerating oil circulation and heat dissipation. The pressure relief valve automatically adjusts according to oil pressure, providing both pressure protection and lubrication assurance, enhancing system safety and reliability. The separate design of the rotating and fixed sides of the clutch body allows for flexible connection between the power shaft and flywheel, reducing power loss. The internal oil inlet channel of the power shaft, in conjunction with the rotary joint, ensures stable oil supply at high speeds, shortening the oil path distance to reduce pressure loss and improve efficiency. Corresponding lubrication methods synchronize power input and lubrication, simplifying operation. A directional oil path design avoids lubrication dead zones, and the dual return channels, combined with the pressure relief valve, ensure smooth oil flow and stable pressure. This highly automated system reduces manual intervention costs and the risk of operational errors, while also solving the problem of cross-contamination between clutch hydraulic oil and bearing lubricating oil in traditional structures, reducing user oil change costs and extending the service life of components and oil.

[0031] The above description of the disclosed embodiments enables those skilled in the art to implement or use this patent. Various modifications to these embodiments will be readily apparent to those skilled in the art, and the general principles defined herein may be implemented in other embodiments without departing from the spirit or scope of this patent. Therefore, this patent is not to be limited to the embodiments shown herein, but is to be accorded the widest scope consistent with the principles and novel features disclosed herein.

Claims

1. A press flywheel system, comprising a power shaft (14), wherein a flywheel assembly (01) and a braking assembly (02) are disposed on the power shaft (14), the braking assembly (02) being disposed on the left side of the flywheel assembly (01), characterized in that, The flywheel assembly (01) includes a support sleeve (1), the power shaft (14) is rotatably mounted in the inner hole of the support sleeve (1), and a flywheel (5) is mounted on the outer periphery of the support sleeve (1) via two bearings (8), forming an oil passage gap (03) between the flywheel (5) and the support sleeve (1); the braking assembly (02) includes a clutch sleeve (12), the right end face of the clutch sleeve (12) is concentrically fixedly connected to the left end face of the flywheel (5), and the... The inner cavity of the clutch sleeve (12) is connected to the left end of the oil passage gap (03); the clutch sleeve (12) is connected to an oil inlet pipe (15); the support sleeve (1) is provided with a lubrication channel (19); one end of the lubrication channel (19) is connected to the right end of the oil passage gap (03); the other end of the lubrication channel (19) is connected to a return oil pipe (16); the return oil pipe (16) and the oil inlet pipe (15) are connected to a pump station oil tank (18).

2. The press flywheel system according to claim 1, characterized in that, An inner spacer (7) and an outer spacer (6) are provided between the two bearings (8). The inner spacer (7) is fitted on the outer periphery of the support sleeve (1). The two ends of the inner spacer (7) abut against the inner rings of the two bearings (8) respectively. The outer spacer (6) is set on the inner wall of the flywheel (5). The two ends of the outer spacer (6) abut against the outer rings of the two bearings (8) respectively. The outer surface of the inner spacer (7) and the inner surface of the outer spacer (6) are spaced a certain distance apart.

3. The press flywheel system according to claim 2, characterized in that, The left end of the oil passage gap (03) is provided with an outer bearing retaining ring (9) and an inner bearing retaining ring (10). The outer bearing retaining ring (9) is fixedly connected to the left end face of the flywheel (5). The outer bearing retaining ring (9) abuts against the outer ring of the bearing (8) located on the left side. The inner bearing retaining ring (10) is fixedly connected to the left end of the outer peripheral surface of the support sleeve (1). The inner bearing retaining ring (10) abuts against the inner ring of the bearing (8) located on the left side. An oil inlet gap (04) is formed between the inner edge of the outer bearing retaining ring (9) and the outer edge of the inner bearing retaining ring (10).

4. The press flywheel system according to claim 3, characterized in that, An inner shaft sealing plate (2) is provided at the right end of the oil passage gap (03). The inner edge of the inner shaft sealing plate (2) is fixedly connected to the outer circumferential surface of the support sleeve (1). The outer edge of the inner shaft sealing plate (2) is attached to the right end face of the flywheel (5). An outer shaft sealing plate (4) is also installed on the right end face of the flywheel (5). The outer shaft sealing plate (4) is pressed against the right outer circumference of the inner shaft sealing plate (2). A rotary sealing ring (3) is provided between the outer shaft sealing plate (4) and the inner shaft sealing plate (2).

5. The press flywheel system according to claim 4, characterized in that, The lubrication channel (19) is U-shaped, and the two ends of the lubrication channel (19) are located on both sides of the inner shaft sealing plate (2).

6. The press flywheel system according to claim 1, characterized in that, The support sleeve (1) is also provided with an oil drain channel (20). The left end of the oil drain channel (20) is opened on the left end face of the support sleeve (1), and the right end of the oil drain channel (20) is opened on the right side of the outer peripheral surface of the support sleeve (1). The right end of the oil drain channel (20) is connected to a return oil pipe two (17), and the return oil pipe two (17) is connected to the pump station oil tank (18).

7. The press flywheel system according to claim 6, characterized in that, The right end of the oil drain channel (20) is also provided with a pressure relief valve (21), which is connected to the inside of the oil drain channel (20).

8. The press flywheel system according to claim 1, characterized in that, The braking assembly (02) also includes a clutch body (11), which includes a rotating side (112) and a fixed side (111). The rotating side (112) rotates synchronously with the power shaft (14), and the fixed side (111) is coaxially fixedly connected to the support sleeve (1). The left side of the inside of the power shaft (14) is also provided with an oil inlet channel (22). The right end of the oil inlet channel (22) is opened on the outer circumferential surface of the power shaft (14) and is located in the inner cavity of the clutch sleeve (12). The left end of the oil inlet channel (22) is opened on the left end face of the power shaft (14) and is equipped with a rotary joint (13). The oil inlet pipe (15) is connected to the rotary joint (13).

9. A lubrication method for a press flywheel system, characterized in that, Includes the following steps: S1. The pump station oil tank (18) supplies oil to the clutch sleeve (12) through the oil inlet pipe (15) and the power shaft (14) to achieve lubrication of the brake assembly (02); S2. The hydraulic oil flows through the inlet gap (04), through the bearing (8) on the left, into the oil passage gap (03), and then through the bearing (8) on the right, thus achieving lubrication of the two bearings (8) and the flywheel (5); S3. The hydraulic oil passes through the lubrication channel (19) and enters the return oil pipeline (16) under the obstruction of the inner shaft seal plate (2) and the outer shaft seal plate (4), and flows back to the pump station oil tank (18).

10. The lubrication method for the press flywheel system according to claim 9, characterized in that, When the amount of oil injected into the clutch sleeve (12) exceeds the amount of oil returned through the first return oil pipe (16), the pressure relief valve (21) opens, and the excess oil enters the second return oil pipe (17) through the drain hole (20) and flows back to the pump station oil tank (18).

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