Three-flywheel transmission system applied to screw press

Abstract

The application relates to the field of screw press transmission technology, in particular to a three-flywheel transmission system applied to a screw press, which comprises a driving flywheel and a reverse flywheel horizontally arranged at the top of a main screw rod, the wheel surface size diameter of the reverse flywheel is smaller than that of the driving flywheel, corresponding driving elements for the reverse flywheel and the driving flywheel are arranged on the screw press, and the three-flywheel transmission system further comprises a brake flywheel arranged at the middle part of the main screw rod, the wheel surface size diameter of the brake flywheel is smaller than that of the reverse flywheel, and corresponding driving elements for driving the brake flywheel are arranged on the screw press; a buffer mechanism is arranged below the brake flywheel and used for buffering forging impact recoil force; and a supporting mechanism is arranged below the buffer mechanism and used for supporting the weight of the transmission system. The application has the effects of reducing the torque damage to the main screw rod of the screw press and maintaining the stable operation of workshop equipment.

Description

Technical Field

[0001] This application relates to the field of screw press transmission technology, and in particular to a three-flywheel transmission system applied to a screw press. Background Technology

[0002] A screw press is a common forging equipment in the metal processing industry. Its main principle is the screw drive of a lead screw. The screw structure and internal limiting mechanism of the press generate torque for the slide block to move up and down during forming. A flywheel accelerates the rotation, transferring energy to the slide block, which then violently impacts the forging workpiece, causing it to achieve the desired deformation. Traditional screw presses are driven by an asynchronous servo motor that pulls the main screw via belt drive. The rotation of the main screw further drives the slide block.

[0003] As is well known, the aforementioned transmission method of the screw press has significant drawbacks. Under inertia, as the motor drives the main screw to rotate and the slide moves downward, the slide accumulates a large amount of energy. This energy is released at the moment of impact with the forging, but the violent collision will be transmitted through the main screw to the upper drive and transmission components, resulting in a huge recoil force and impact transmission between internal structures. Furthermore, and more importantly, when the slide impacts the forging, the main screw, which is rotating at high speed, suddenly slows to a standstill. The inertial effect of the torque will bring a huge circumferential shear force to the main screw. Each forging involves multiple impacts, significantly affecting the structural strength of the main screw. As the main transmission structure of the screw press, the main screw is like the "keel," and damage to the main screw is irreparable. Most importantly, the instantaneous power generated by the violent reverse rotation of the flywheel driven by the output shaft of the asynchronous servo motor will exceed the safety limits of the power grid, causing a "trip" phenomenon, resulting in a power outage in the workshop and affecting the use of other machines.

[0004] To maintain the stable operation of workshop equipment, there is a dual flywheel drive technology for a screw press. This technology involves setting up large and small flywheels, with the large flywheel acting as the driving component and the small flywheel as the reversing component. When the slide moves down, both flywheels operate simultaneously, driving the main screw to rotate and accumulating a large amount of energy in a short time. After forging, the slide moves up, and under the drive of the clutch, the large flywheel cancels its drive on the main screw, the small flywheel directly reverses, and the large flywheel remains separated from the main screw until the slide moves down again.

[0005] The above process uses a small flywheel with low inertia and driving energy consumption as a reversing flywheel, and a traditional large flywheel as the driving flywheel. In this way, the energy consumption generated at the moment of reversal of the small flywheel cannot exceed the power grid's safety limit, ensuring the stable operation of other equipment in the workshop. However, the above dual flywheel drive still does not get rid of the driving method of the motor driving the flywheel to reverse directly. The shearing and destructive force of the inertial torque is not alleviated. Therefore, from the perspective of the main screw's service life, the dual flywheel drive system is not an effective solution.

[0006] In response to the aforementioned technologies, from a transmission perspective, an upgrade is made to the dual flywheel transmission system, which reduces the impact of the screw press on the power grid while enhancing the torque destructive force on the main screw. Summary of the Invention

[0007] In order to reduce the torque destructive force on the main screw of the screw press and maintain the stable operation of workshop equipment, this application provides a three-flywheel transmission system for screw presses.

[0008] The technical solution provided in this application for a three-flywheel drive system applied to a screw press is as follows: A three-flywheel transmission system for a screw press includes a drive flywheel and a counter-rotating flywheel horizontally arranged on the top of the main screw, wherein the wheel diameter of the counter-rotating flywheel is smaller than that of the main screw, and the screw press is provided with corresponding drive components for the counter-rotating flywheel and the drive flywheel, characterized in that: it further includes; A brake flywheel is located in the middle part of the main screw, and its wheel diameter is smaller than that of the reverse flywheel. Correspondingly, the screw press is equipped with a drive component for driving the brake flywheel. A buffer mechanism, located below the brake flywheel, is used to buffer the forging impact recoil force; The support mechanism, located below the buffer mechanism, is used to support the weight of the transmission system.

[0009] By adopting the above technical solution, a three-flywheel transmission system is set up with a braking flywheel. Further improvements are made to the improved dual-flywheel transmission system by adding a braking flywheel to the traditional drive flywheel and counter-rotating flywheel. This brake flywheel is used to reduce the main screw speed briefly before the slider forging impact, providing a buffer period for the sudden change in circumferential shear force without affecting the impact effect, thus reducing the inertial shear destructive force on the main screw. The main operation process is as follows: during the slider's descent, the drive flywheel, counter-rotating flywheel, and braking flywheel simultaneously engage the main screw, meaning all three flywheels drive the slider simultaneously. During the slider's descent, a huge amount of energy accumulates... Energy is used to forge the workpiece. Before the slide block strikes the workpiece, the clutch of the screw press separates the drive flywheel from the main screw, causing the drive flywheel, which has the greatest inertia and consumes the most energy in reverse rotation, to idle and remain in this idle state. Next, the drive component of the reverse flywheel stops operating, and the reverse flywheel relies on and rotates synchronously with the main screw. The brake flywheel remains connected, and the drive component operates to keep the brake flywheel at the same speed as the main screw. At this time, the main screw is driven only by the brake flywheel. In the 0.75 seconds before the slide block strikes the workpiece, the drive component drives the brake flywheel to maintain its rotational direction and reduce its speed. During this brief period, the brake flywheel... The braking force provides a counteracting force to the main screw, offsetting the upward momentum of the main screw due to the energy accumulation before braking. During the slide block forging of the workpiece, the reduction in the forging effect caused by the braking deceleration of the brake flywheel is negligible. After the slide block forging, the drive mechanism of the reverse flywheel restarts, working together with the brake flywheel to directly pull the main screw in reverse. The braking deceleration of the main screw by the brake flywheel effectively reduces the maintenance of inertia and the acceleration difference at the moment of reversal, thereby reducing the circumferential shear force exerted on the main screw by the torque shear force. Before the slide block's upward movement ends, the brake flywheel is also required, and the brake flywheel precedes... The reverse flywheel acts on the main screw, while the braking flywheel decelerates in the same direction. By reducing the speed difference between the front and rear of the main screw through short-term deceleration, the reverse flywheel and the braking flywheel simultaneously drive the main screw to reverse, causing the slide block to descend. During the descent of the slide block, the clutch engages the main screw with the drive flywheel, and the three flywheels work together during the descent of the slide block. The above scheme is that before the reverse flywheel acts, that is, before the slide block forges the workpiece, the braking flywheel prevents the accumulation of inertia in a short period of time, reducing the circumferential acceleration of the main screw to a negative value, and completing the forging after it becomes negative, thereby reducing the impact of inertial torque force.

[0010] Optionally, the support structure includes; The flange disc is a horizontally set part that passes through the bottom side of the main screw brake flywheel. Its disc diameter is larger than the cross-sectional diameter of the main screw. The corresponding part inside the screw press has a flange disc groove that fits the surface of the flange disc. The flange disk and the flange disk groove are clearance fit; The flange disk has its two ends near the center bent.

[0011] By adopting the above technical solution, the main screw is positioned and the upper drive flywheel, reverse flywheel, and brake flywheel are supported by the structure of the flange disc and flange disc groove. The flange disc can serve as a protruding part in the middle of the main screw, and the corresponding groove inside the screw press body is recessed to position the main screw during operation. It should be noted that in actual applications, the flange disc and flange disc groove should be clearance-fitted with a clearance width of 0.3-0.5mm to provide a certain degree of slack in the transmission structure. This is necessary when the main screw rotates at high speed or when the slide block strikes the forging. When the main screw is subjected to a recoil force, it vibrates at a high frequency. Due to the rigid connection between the transmission components, the amplitude of the main screw and its accessories is relatively small. Therefore, a gap that does not affect the transmission of the structure is set to accommodate the vibration of the flange disk following the main screw. In addition, in the above scheme, the flange disk is bent into an arc surface, making the flange disk as a whole gyroscope. The corresponding part of the flange disk groove fits into the center part of the flange disk. The gyroscope shape of the flange disk can use the structural constraint of the flange disk groove to limit the vibration of the flange disk to a certain area. After vibration, it is easy for the flange disk to drive the main screw to reset, so that the vibration of the main screw has a reset effect.

[0012] Optional, also includes; A copper washer ring is disposed between the bottom wall of the inner groove of the flange disk and the bottom side surface of the flange disk, and abuts against the edge of the flange disk. The copper washer ring has a gap with the portion of the flange disk near the bottom of the flange disk groove.

[0013] By adopting the above technical solution, a copper washer ring is installed at the bottom of the flange disk groove as a direct structural component contacting the flange disk. Correspondingly, the bottom side of the flange disk groove is horizontally positioned to support the copper washer ring, and the top side of the copper washer ring is inclined and bent to fit the curved portion of the bottom end face of the flange disk. A gap is created in the portion of the copper washer ring near the main screw, separating the inner ring wall portion and the top side portion of the copper washer ring from the curved portion of the flange disk, reducing the contact surface without vertical support, thereby reducing relative rotational friction. Since the supporting force of the portion of the copper washer ring near the inner ring wall on the flange disk in the vertical plane is relatively small, if not... Setting a gap increases friction more than it increases the supporting force, meaning the beneficial effect is insufficient. The above-mentioned flange disk uses copper material mainly because copper washers have the following advantages: copper surface smoothness ensures that the sliding friction between the main screw and the copper washer is kept within a small range during main screw rotation, minimizing friction loss. Secondly, copper has a high cost-performance ratio, achieving high strength at a relatively low price and maintaining surface smoothness for a long time. In addition, copper is a green metal that does not pollute the environment and can be reused repeatedly.

[0014] Optional, also includes; The oil injection channel penetrates the groove wall of the flange disk and connects the gap between the flange disk groove and the flange disk. Accordingly, the screw press has a sealed oil reservoir on the bottom side of the flange groove for holding lubricating oil.

[0015] By adopting the above technical solution, during the maintenance of the screw press, relevant technicians can inject oil into the flange groove through the oil injection channel. The lubricating oil flows into the flange groove from the gap between the inner wall of the flange groove and the surface of the flange. When the screw press is running, the lubricating oil can greatly reduce the friction loss between the surface of the flange and the inner wall of the flange groove, and improve the service life of the main screw. In addition, the lubricating oil can fill the gap between the inner wall of the flange groove and the surface of the flange. When the main screw vibrates, it reduces the collision between the flange and the flange groove to a certain extent, playing a buffering role. The flange vibrates with the vibration of the main screw, and the lubricating oil flows into the oil tank through the gap generated by the vibration and accumulates in the oil tank. Technicians can recycle the lubricating oil by opening the oil tank periodically.

[0016] Optionally, the buffer mechanism includes; A gas spring is vertically arranged between the brake flywheel and the flange plate groove, and multiple gas springs are evenly distributed along the circumference of the main screw. The bottom end of the gas spring passes through the top wall of the flange plate groove and connects to the flange plate, and the top end abuts against the bottom side of the brake flywheel.

[0017] By adopting the above technical solution, the gas spring, as one of the main buffer chambers, is mainly used to buffer the vertical upward recoil force generated along the main screw when the slider forges the forging. In the above solution, the gas spring is set between the brake flywheel and the flange plate groove, and the bottom end extends into the flange plate groove to abut against the continuously vibrating flange plate. The hard impact force is transmitted from the flange plate to the gas spring, and the impact force is buffered by the high-pressure air source in the compressed air chamber, thereby achieving initial protection for the drive flywheel, reverse flywheel and brake flywheel at the top of the main screw.

[0018] Optionally, the buffer mechanism further includes; Disc springs are disposed on the bottom side of the brake flywheel. Multiple disc springs are stacked coaxially into a group. Multiple groups of disc springs are distributed at equal intervals along the circumferential direction of the bottom side of the brake flywheel. A disc spring groove is provided on the bottom side of the brake flywheel corresponding to each group of disc springs. The top of the gas spring is positioned to correspond to the slot of the disc spring.

[0019] By adopting the above technical solution, after adding a smaller brake flywheel to the bottom of the traditional reversing flywheel, the pressure-bearing capacity of the brake flywheel needs to be considered. After the gas spring initially buffers the huge impact force, it still causes structural damage to the smaller brake flywheel. Therefore, multiple disc spring slots are vertically opened at the bottom of the brake flywheel, and the multiple disc spring slots are evenly distributed around the bottom side of the brake flywheel. This allows the force transmitted from the gas spring to compress the stacked disc springs in the disc spring slots, and the compressibility of the disc springs further buffers the impact force. Therefore, when installing the gas spring, the gas spring must correspond one-to-one with the disc spring slot, and the end of the gas spring must correspond to the opening of the disc spring slot, so that the distribution circumference of the top of the vertically set multiple gas springs coincides with the distribution circumference of the disc spring slot. It should be noted that the disc springs are stacked in such a way that adjacent disc springs are arranged in opposite directions. The middle part of the disc spring slot is provided with a through rod to insert all the disc springs in the same disc spring slot, keeping all the disc springs coaxial.

[0020] Optionally, the buffer structure further includes; A tapered roller bearing is disposed between the groove of the disc spring and the top of the gas spring, and is used to transmit axial force along the main screw.

[0021] By adopting the above technical solution, a tapered roller bearing is selected as the force transmission element between the gas spring and the disc spring. The tapered roller bearing has strong axial load-bearing capacity and axial impact resistance, and can withstand huge axial loads. With the bottom of the gas spring fixed, the top end transmits the compressive force to the disc spring by abutting against the bearing ring of the tapered roller bearing. While bearing huge axial loads, it ensures the relative rotation of the brake flywheel and the gas spring. Therefore, in the above solution, the tapered rollers of the tapered roller bearing should be set to fit the circumferential surface of the disc spring groove to ensure positive force transmission.

[0022] Optional, also includes; A ball bearing is disposed between the brake flywheel and the counter-rotating flywheel for their relative rotation.

[0023] By adopting the above technical solution, the ball bearing is mainly used for the relative rotation between the brake flywheel and the reverse flywheel. In addition to the brake flywheel and the reverse flywheel, ball bearings are also provided between the brake flywheel and the drive flywheel. Considering that there is a period of asynchronous rotation between the contact surfaces of the brake flywheel and the reverse flywheel, ball bearings are provided to reduce the relative friction between the brake flywheel and the reverse flywheel.

[0024] In summary, this application includes at least the following beneficial technical effects: 1. Without threatening the operation of other workshop equipment within the power grid, the service life of the main screw is increased from the perspective of reducing the shearing destructive force on the main screw. This is mainly reflected in setting the brake flywheel to decelerate the main screw in the same direction for 0.75 seconds before the slider forges the forging, which counteracts the speed maintenance trend caused by the rotational inertia of the main screw and the speed increase trend caused by the continuous drive of the brake flywheel, reducing the acceleration difference before and after reversal, thereby achieving the reversal torque difference of the main screw. 2. By setting the flange disc and flange disc groove to be structurally positioned, the main screw has the ability to reset after vibration. Then, the smoothness of the copper washer ring is used to reduce the relative rotational friction with the flange disc from the material. Finally, lubricating oil is added to further buffer the relative vibration of the flange disc. Attached Figure Description

[0025] Figure 1 This is a schematic diagram of the overall structure of an embodiment of this application.

[0026] Figure 2 This is a cross-sectional view taken in the embodiments of this application to highlight the internal structure of the screw press.

[0027] Figure 3 yes Figure 2 Enlarged view of part A.

[0028] Figure 4 This is a structural schematic diagram made to highlight the disc spring in the embodiments of this application.

[0029] Explanation of reference numerals in the attached drawings: 1. Screw press; 11. Main screw; 111. Flange disc; 112. Flange disc groove; 113. Copper washer ring; 114. Oil injection channel; 115. Gas spring; 116. Disc spring groove; 117. Disc spring leaf; 118. Ball bearing; 12. First asynchronous servo motor; 13. Second asynchronous servo motor; 14. Third asynchronous servo motor; 15. Clutch; 2. Drive flywheel; 3. Reverse flywheel; 4. Brake flywheel; 5. Tapered roller bearing. Detailed Implementation

[0030] The following is in conjunction with the appendix Figure 1-4 This application will be described in further detail.

[0031] This application discloses a three-flywheel drive system applied to a screw press. (Refer to...) Figure 1 and Figure 2 A three-flywheel transmission system applied to a screw press 1 includes a main screw 11 as the main structure of the transmission system. The main screw 11 is vertically arranged. The top of the screw press 1 is provided with an active component for driving the main screw 11 to rotate. The rotation of the main screw 11 drives the slide block to move down to forge the forging.

[0032] Reference Figure 2The main screw 11 has a drive flywheel 2, a reverse flywheel 3, and a brake flywheel 4 horizontally arranged at its top end. The drive flywheel 2, reverse flywheel 3, and brake flywheel 4 are sequentially mounted on the main screw 11 from top to bottom. The diameter and thickness of the drive flywheel 2 are greater than those of the reverse flywheel 3, and the diameter and thickness of the reverse flywheel 3 are greater than those of the brake flywheel 4. The screw press 1 is equipped with asynchronous servo motors for the corresponding drive flywheel 2, reverse flywheel 3, and brake flywheel 4. For easy distinction, the motor used to drive the drive flywheel 2 is the first asynchronous servo motor 12, the motor used to drive the reverse flywheel 3 is the second asynchronous servo motor 13, and the motor used to drive the brake flywheel 4 is the third asynchronous servo motor 14.

[0033] Reference Figure 2 In this embodiment, the drive flywheel 2 has a large mass and a high influence of inertial torque. The load brought by the drive flywheel 2 is large when the main screw 11 rotates and stops, which will also increase the tangential destructive force on the main screw 11. Therefore, it is considered to separate the drive flywheel 2 from the main screw 11 in time when the main screw 11 switches states, so as to eliminate the obstruction of the drive flywheel 2 to the main screw 11. Therefore, the screw press 1 is provided with a clutch 15 at the top of the main screw 11 for engaging the drive flywheel 2 with the main screw 11.

[0034] Therefore, the operation process of the three flywheels in this embodiment will be explained. Taking the single forging process of the slider as an example, during the descent of the slider, the drive flywheel 2, the reverse flywheel 3, and the brake flywheel 4 simultaneously engage the main screw 11. The first asynchronous servo motor 12, the second asynchronous servo motor 13, and the third asynchronous servo motor 14 maintain synchronous speed and acceleration, that is, the three flywheels drive the slider simultaneously. The slider accumulates a huge amount of energy during the descent to forge the workpiece. Before the slider forges, the first asynchronous servo motor 12 stops driving the drive flywheel 2, and the clutch 15 of the screw press 1 connects the drive flywheel 2 with the main screw. 11. Separation allows the drive flywheel 2, which has the greatest inertia and highest energy consumption during reversal, to enter the idle turntable and remain in this state. Next, the second asynchronous servo motor 13 stops operating, and the reversing flywheel 3 rotates synchronously with the main screw 11, relying on the main screw 11. The brake flywheel 4 remains connected, and the third asynchronous servo motor 14 continues operating, keeping the brake flywheel 4 at the same speed as the main screw 11. At this time, the main screw 11 is driven at its original speed solely by the brake flywheel 4. Just before the slider strikes the forging, the third asynchronous servo motor 14 drives the brake flywheel 4 to maintain its rotational direction but reduce its speed briefly. During the period, the brake flywheel 4 exerts a reverse restraining force on the main screw 11, which cancels out the upward momentum of the main screw 11 due to the energy accumulation before braking. When the slider forges the workpiece, the reduction in the slider forging effect caused by the braking deceleration of the brake flywheel 4 is negligible. After the slider forging, the second asynchronous servo motor 13 drives the reverse flywheel 3 to operate again, working in conjunction with the brake flywheel 4 to directly pull the main screw 11 in reverse. The braking deceleration of the main screw 11 by the brake flywheel 4 can effectively reduce the maintenance of inertia and reduce the acceleration difference at the moment of reversal, thereby reducing the torque shear force on the main screw. The circumferential shear force of 11; before the slider rises, it also needs to rely on the brake flywheel 4; the brake flywheel 4 acts on the main screw 11 before the reverse flywheel 3. The brake flywheel 4 still uses the same direction deceleration method to brake, relying on the deceleration in a short period of time to reduce the front and rear speed difference of the main screw 11. Then the reverse flywheel 3 and the brake flywheel 4 drive the main screw 11 to reverse, and the slider descends; during the slider descent, the first asynchronous servo motor 12 restarts, and the clutch 15 engages the main screw 11 with the drive flywheel 2, connecting the rotational driving force of the drive flywheel 2 to the rotational driving force of the main screw 11.

[0035] Reference Figure 2 According to the above operation process, in order to ensure the rotation of the drive flywheel 2, the reverse flywheel 3 and the brake flywheel 4 and reduce the rotational friction between the three, ball bearings 118 are provided between the drive flywheel 2 and the reverse flywheel 3 and between the reverse flywheel 3 and the brake flywheel 4 in this embodiment.

[0036] Reference Figure 2 and Figure 3In this embodiment, a support structure is also provided to support the weight of the three flywheels and their accessories. This support structure includes a flange disk 111 mounted on the main screw 11. The flange disk 111 is positioned below the brake flywheel 4. The flange disk 111 can be considered as an integral part of the main screw 11 and is a protruding portion of the main screw 11. The diameter of the two end faces of the flange disk 111 is larger than the cross-sectional diameter of the main body of the main screw 11. Furthermore, the edges of the two end faces of the flange disk 111 are connected to the sidewalls of the main screw 11 in an arc shape, making the flange disk 111 as a whole... The screw press 1 is shaped like a top. The flange plate 111 on the corresponding main screw 11 inside the screw press 1 has a flange plate groove 112. The inner top wall of the flange plate groove 112 is curved to fit the top wall of the flange plate 111. The inner top wall of the flange plate groove 112 has a through hole adapted to the main screw 11. The inner bottom wall of the flange plate groove 112 is horizontally set and also has a through hole for passing through and adapted to the main screw 11. A copper washer ring 113 is set on the inner bottom wall of the flange plate groove 112. The top wall of the copper washer ring 113 is used to support the bottom end face of the flange plate 111.

[0037] In this embodiment, the flange groove 112 serves a positioning function. Since the main screw 11 maintains a small-amplitude high-frequency vibration during rotation, it would shift if not restricted. Therefore, the curved fit between the flange groove 112 and the flange 111 provides the main screw 11 with a certain vibration reset capability. Considering the vibration impact of the main screw 11, a gap is opened between the flange groove 112 and the flange 111 in this embodiment, and the two are set as a clearance fit. In practical applications, the gap should be 0.3-0.5mm. In this embodiment, the bottom wall of the flange groove 112 serves as the main load-bearing structure of the transmission system on the main screw 11. A copper washer ring 113 is set as the direct contact component of the main screw 11. The wear resistance and smoothness of copper are utilized to minimize the rotational friction between the flange 111 and the flange groove 112.

[0038] Reference Figure 3 In this embodiment, considering that the portion of the flange disk 111 near the main screw 11 is bent in the vertical direction, if it abuts against this portion, the vertical component of the supporting force is less effective than the frictional effect brought about by increasing the contact surface. Therefore, in order to reduce rotational friction, the inner ring diameter of the copper washer ring 113 and the through hole diameter on the bottom side of the flange disk groove 112 are set to be larger than the corresponding cross-sectional diameter of the main screw 11 to leave a predetermined gap. At the same time, the portion of the top side of the copper washer ring 113 near the main screw 11 is inclined away from the flange disk 111 to increase the reserved gap, reduce the bending contact surface with weak support effect, and maintain a small frictional value when the main screw 11 rotates.

[0039] Reference Figure 2In this embodiment, in order to further reduce friction loss, an oil injection channel 114 is provided inside the screw press 1 to connect with the inside of the flange plate groove 112. Relevant technicians inject lubricating oil into the oil injection channel 114. The lubricating oil flows into the flange plate groove 112 and into the gap between the flange plate groove 112 and the flange plate 111. When the main screw 11 rotates, that is, when the flange plate 111 rotates relative to the flange plate groove 112, the lubrication of the lubricating oil reduces the friction between the flange plate 111 and the copper washer ring 113, and between the side wall of the flange plate 111 and the inner wall of the flange plate groove 112, and to a certain extent weakens the vibration and collision that occur in the flange plate groove 112.

[0040] Reference Figure 2 According to the above design, in this embodiment, the oil injection channel 114 is installed inside the screw press 1, with one end extending outside the screw press 1 and the other end extending through the side wall of the flange groove 112 into the flange groove 112. It should be noted that in practical applications, the end of the oil injection channel 114 extending out of the screw press 1 must be closed when not injecting oil.

[0041] Reference Figure 2 Because the huge impact force generated when the slider forges the forging is transmitted upward along the main screw 11, it is easy to damage the flywheel transmission system at the top of the main screw 11. Therefore, in this embodiment, multiple gas springs 115 are vertically arranged below the brake flywheel 4 at the bottom of the transmission flywheel. The multiple gas springs 115 are evenly distributed along the circumference of the main screw 11. The bottom end of the gas spring 115 extends through the top wall of the flange groove 112 and into the interior of the flange groove 112. The top end of the gas spring 115 is connected to the top end of the brake flywheel 4. The main purpose of the above solution is to buffer the axial recoil force transmitted along the main screw 11 at the gas spring 115, thus protecting the transmission system at the top of the main screw 11. In order to improve the transmission performance, a copper pad is also provided between the top wall of the flange groove 112 and the flange 111. The bottom end of the gas spring 115 abuts against the copper pad. The copper pad vibrates with the flange 111 when the flange 111 rotates, and then transmits the vibration to the gas spring 115 to buffer the huge impact force.

[0042] Reference Figure 2 and Figure 4Because the brake flywheel 4 has a small diameter, the huge impact force after being buffered by the gas spring 115 can still structurally impact the brake flywheel 4, weakening the connection between the belt and the brake flywheel 4. Therefore, multiple disc spring grooves 116 are vertically opened on the bottom end face of the brake flywheel 4. Each disc spring groove 116 is evenly distributed along the circumference of the brake flywheel 4. Multiple disc spring plates 117 are arranged inside each disc spring groove 116. Every two adjacent disc spring plates 117 are installed in opposite directions in the vertical direction to improve the compressive elasticity of the multiple disc spring plates 117. It should be noted that in this embodiment, the circumferential distribution circle of the multiple disc spring grooves 116 coincides with the circumferential distribution circle formed by the tops of the multiple gas springs 115. That is, it is necessary to ensure that the gas springs 115 can transmit the impact force to the disc spring grooves 116. Considering the rotation of the brake flywheel 4, in this embodiment, a tapered roller bearing 5 is installed on the bottom end face of the brake flywheel 4. The diameter of the tapered roller bearing 5 is the same as the diameter of the distribution circle of the disc spring grooves 116, so that the tapered roller is fixed between the disc spring 117 and the gas spring 115.

[0043] The implementation principle of a three-flywheel transmission system applied to a screw press 1 in this application embodiment is as follows: This embodiment further improves upon the improved dual-flywheel transmission system by adding a braking flywheel 4 to the traditional drive flywheel 2 and reverse flywheel 3 to reduce the speed of the main screw 11 for a short period of time before the slide block forging. Without affecting the impact effect, it provides a buffer period for the sudden change in circumferential shear force, thereby reducing the shearing destructive force of inertia on the main screw 11.

[0044] During the descent of the slider, the drive flywheel 2, the reverse flywheel 3, and the brake flywheel 4 simultaneously engage the main screw 11. The first asynchronous servo motor 12, the second asynchronous servo motor 13, and the third asynchronous servo motor 14 maintain synchronous speed and acceleration, meaning that the three flywheels drive the slider simultaneously. The slider accumulates a massive amount of energy during its descent to forge the workpiece. Before the forging, the first asynchronous servo motor 12 stops driving the drive flywheel 2, and the clutch 15 of the screw press 1 separates the drive flywheel 2 from the main screw 11, allowing the drive flywheel 2, which has the greatest inertia and consumes the most energy in reverse rotation, to enter the air. The rotary table remains in this state. Next, the second asynchronous servo motor 13 stops operating, and the reverse flywheel 3 rotates synchronously with the main screw 11, relying on the main screw 11. The brake flywheel 4 remains connected, and the third asynchronous servo motor 14 remains operational, keeping the brake flywheel 4 at a synchronized speed with the main screw 11. At this time, the main screw 11 is driven at its original speed solely by the brake flywheel 4. Just before the slider strikes the forging, the third asynchronous servo motor 14 drives the brake flywheel 4 to maintain its rotational direction but reduce its speed. During a brief period, the brake flywheel 4 provides the main screw 11 with a... The reverse restraining force cancels out the upward trend of the main screw 11 before braking due to the energy accumulation. When the slider forges the workpiece, the reduction in the slider forging effect caused by the braking deceleration of the brake flywheel 4 is negligible. After the slider forges, the second asynchronous servo motor 13 drives the reverse flywheel 3 to operate again. Working in coordination with the brake flywheel 4, the reverse flywheel 3 directly pulls the main screw 11 in reverse. The braking deceleration of the main screw 11 by the brake flywheel 4 can effectively reduce the maintenance of the inertial effect and reduce the acceleration difference at the moment of reversal, thereby reducing the circumferential shear force brought to the main screw 11 by the torque shear force. Before the slider rises, it also needs to rely on the brake flywheel 4. The brake flywheel 4 acts on the main screw 11 before the reverse flywheel 3. The brake flywheel 4 still uses the same direction deceleration method to brake, relying on the deceleration in a short period of time to reduce the front and rear speed difference of the main screw 11. Then the reverse flywheel 3 and the brake flywheel 4 drive the main screw 11 to reverse, and the slider descends. During the slider descent, the first asynchronous servo motor 12 restarts, and the clutch 15 engages the main screw 11 with the drive flywheel 2, connecting the rotational driving force of the drive flywheel 2 to the rotational driving force of the main screw 11.

[0045] The above are all preferred embodiments of this application and are not intended to limit the scope of protection of this application. Therefore, all equivalent changes made in accordance with the structure, shape and principle of this application should be covered within the scope of protection of this application.

Claims

1. A three-flywheel drive system for a screw press, comprising a drive flywheel (2) and a counter-rotating flywheel (3) horizontally disposed on the top of a main screw (11), wherein the diameter of the counter-rotating flywheel (3) is smaller than the diameter of the drive flywheel (2), and the screw press (1) is provided with corresponding drive components for the counter-rotating flywheel (3) and the drive flywheel (2), characterized in that: It also includes a brake flywheel (4), which is located in the middle part of the main screw (11). Its wheel diameter is smaller than that of the reverse flywheel (3). Correspondingly, the screw press (1) is provided with a drive component for driving the brake flywheel (4). A buffer mechanism is located below the brake flywheel (4) to buffer the forging impact force; a support mechanism is located below the buffer mechanism to support the weight of the transmission system. The support mechanism includes: a flange disc (111), which is horizontally arranged and passes through the bottom side of the brake flywheel (4) of the main screw (11), and its disc diameter is larger than the cross-sectional diameter of the main screw (11). A flange disc groove (112) is opened in the corresponding part inside the screw press (1) to fit the surface of the flange disc (111); the flange disc (111) and the flange disc groove (112) are clearance fit; the two ends of the flange disc (111) are bent near the center. The buffer mechanism includes: a gas spring (115), which is vertically arranged between the brake flywheel (4) and the flange disk groove (112), and multiple gas springs are evenly distributed along the circumference of the main screw (11). The bottom end of the gas spring penetrates the top wall of the flange disk groove (112) and connects to the flange disk (111), and the top end abuts against the bottom side of the brake flywheel (4). The buffer mechanism further includes: disc springs (117), which are disposed on the bottom side of the brake flywheel (4). Multiple disc springs (117) are coaxially stacked into a group. The multiple groups of disc springs (117) are distributed at equal intervals along the circumferential direction of the bottom side of the brake flywheel (4). A disc spring groove (116) is provided on the bottom side of the brake flywheel (4) corresponding to each group of disc springs (117). The top of the gas spring (115) is provided corresponding to the groove opening of the disc spring groove (116). The brake flywheel decelerates the main screw in the same direction before the slider strikes the forging, so as to counteract the speed maintenance trend caused by the rotational inertia of the main screw and the speed increase trend caused by the continuous drive of the brake flywheel.

2. The three-flywheel transmission system for a screw press according to claim 1, characterized in that: It also includes a copper washer ring (113), which is disposed between the bottom wall of the inner wall of the flange disk groove (112) and the bottom side of the flange disk (111), and abuts against the edge of the flange disk (111); the copper washer ring (113) and the part of the bottom side of the flange disk groove (112) near the flange disk (111) are provided with a gap.

3. The three-flywheel transmission system for a screw press according to claim 2, characterized in that: It also includes: an oil injection channel (114) that penetrates the wall of the flange plate groove (112) and connects the gap between the flange plate groove (112) and the flange plate (111); correspondingly, the screw press (1) has a sealed oil tank on the bottom side of the flange plate groove (112) for holding lubricating oil.

4. The three-flywheel transmission system for a screw press according to claim 1, characterized in that: The buffer mechanism further includes a tapered roller bearing (5), which is disposed between the groove of the disc spring (116) and the top of the gas spring (115) for transmitting axial force along the main screw (11).

5. A three-flywheel transmission system for a screw press according to claim 1, characterized in that: It also includes a ball bearing (118) disposed between the brake flywheel (4) and the reverse flywheel (3) for relative rotation between the two.

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