Double flywheel transmission system for a screw press

Abstract

The application relates to the field of screw presses, in particular to a double-flywheel transmission system of a screw press, which comprises a main screw rod, a first flywheel horizontally inserted at the top end of the main screw rod, a first driving element arranged on the screw press and used for driving the first flywheel to rotate, and the double-flywheel transmission system further comprises a second flywheel, which is inserted into the main screw rod and horizontally arranged below the first flywheel, is independent of the first flywheel and has a smaller cross-section diameter than the first flywheel, a second driving element arranged in the screw press and used for driving the second flywheel to rotate, a bearing group sleeved between the top end of the main screw rod and the first flywheel and used for independent rotation of the first flywheel and the main screw rod, and a clutch arranged at the end of the top end of the main screw rod and used for separation and combination of the first flywheel and the main screw rod. The application has the effects of weakening the influence of screw rod speed sudden drop on the power grid and prolonging the service life of the screw rod.

Description

Technical Field

[0001] This application relates to the field of screw presses, and more particularly to a dual flywheel drive system for a screw press. Background Technology

[0002] A screw press is a forging equipment that falls between a forging hammer and a hot forging press. It applies a large amount of pressure to complete processes such as compression, extrusion, forming, and cold forging of metal blocks. It has the advantages of high efficiency, stability, and flexibility, and is widely used in the field of metal parts forging.

[0003] The main stamping part of the screw press consists of a flywheel, a screw with threads at the bottom, and a nut with matching threads. The nut is fastened to the top of the forging block and forms a screw drive pair with the screw. When the external transmission mechanism drives the flywheel and screw to rotate, the screw motion is converted into the vertical reciprocating linear motion of the forging block along the guide rail of the machine body.

[0004] If a die and a metal block to be processed are installed below the forging block, when the external transmission mechanism drives the flywheel to rotate at an accelerated speed, energy is transferred to the flywheel. When the upper die of the slider contacts the forging, the accelerated rotation of the flywheel accumulates a large amount of energy. The screw press uses the energy accumulated in the flywheel in advance to perform die forging, so that the forging obtains the required deformation. The die forging deformation process is the process of the flywheel continuing to release energy, and the rotation speed decreases sharply until it stops rotating.

[0005] Most existing screw presses use asynchronous servo motors for their transmission components, with the transmission mechanism consisting of a flywheel and belt. The asynchronous servo motor drives the screw through the belt and pulleys. A common drawback of traditional screw presses is that when the screw moves the forging block downwards to contact the metal block, the flywheel's large energy storage causes a sudden drop in the forging block's speed, simultaneously generating a large torque on the screw and producing tangential shearing force. Furthermore, the latter half of the forging cycle involves a lifting process, where the asynchronous servo motor drives the flywheel to reverse in a very short time. This makes the motor susceptible to damage, reduces its lifespan, and generates a large electrical surge, impacting the power grid and causing power fluctuations in the application workshop.

[0006] In response to the aforementioned technologies, structural improvements can be made to the transmission system of existing screw presses. When the forging block forges the metal block, the impact of the sudden drop in screw speed on the power grid and the shearing damage to the screw can be reduced, while the service life of the asynchronous servo motor can be improved. Summary of the Invention

[0007] To mitigate the impact of sudden screw speed drops on the power grid and improve screw lifespan, this application provides a dual flywheel drive system for a screw press.

[0008] The dual flywheel drive system for a screw press provided in this application adopts the following technical solution: A dual flywheel drive system for a screw press includes a main screw, a first flywheel horizontally inserted into the top of the main screw, a first drive component on the screw press that drives the first flywheel to rotate, and further includes; The second flywheel is inserted into the main screw and horizontally positioned below the first flywheel. It is independent of the first flywheel and has a smaller cross-sectional diameter than the first flywheel. The screw press is equipped with a second driving component for driving the second flywheel to rotate. The bearing assembly is sleeved between the top of the main screw and the first flywheel, and is used for the independent rotation of the first flywheel and the main screw; The clutch, located at the top end of the main screw, is used for the separation and engagement of the first flywheel and the main screw.

[0009] By adopting the above technical solution, the clutch engages the first flywheel with the main screw. The first driving component drives the main screw to rotate through the first flywheel, and the second driving component drives the second flywheel to rotate independently of the first flywheel. Taking a single forging cycle as an example, a forging block is threadedly connected to the bottom end of the main screw. The first driving component drives the first flywheel to rotate. At this time, the clutch is engaged, and the first flywheel drives the main screw to rotate. Simultaneously, the second driving component drives the second flywheel to rotate at a speed synchronized with the first flywheel, thus driving the main screw to rotate. The torques transmitted to the main screw by both are superimposed. The forging block moves downward through the guide inside the screw press. Before the metal block installed at the bottom of the screw press collides with the forging block, the clutch separates the first flywheel from the main screw, and the first driving component stops operating. The bearing assembly allows the first flywheel to maintain its original speed independently of the main screw by utilizing inertia to the maximum extent. Then, the first flywheel remains separated from the main screw. The second driving component stops operating simultaneously before the forging block collides with the metal block. The speed of the main screw drops sharply when the forging block collides with the metal block, and then... The second drive component drives the second flywheel to directly reverse. Due to the smaller diameter and thickness of the second flywheel, its inertia is smaller, and the power peak caused by direct reversal is within the grid's tolerance range. During the main screw's reversal, the clutch keeps the first flywheel separated from the main screw. After being raised to a certain height, the forging block descends again, and the main screw's reversal is directly achieved by the second drive component driving the second flywheel. When the main screw descends again, it rotates in the same direction as the first flywheel, which remains rotating due to inertia. The clutch engages the main screw with the first flywheel, and the first drive component starts again, causing the main screw to be simultaneously driven by both the first and second drive components, accumulating a large amount of energy during the brief downward movement. In summary, the difference between this scheme and the traditional scheme is that a smaller, less inertial second flywheel, which cannot impact the grid's safe peak value, is used as the main screw reversal device, while the larger, more inertial first sub-wheel acts as a booster to push the main screw downward, providing sufficient energy to the forging block. In the above scheme, it is recommended to use asynchronous servo motors for both the first and second drive components.

[0010] Optional, also includes; The brake arc plate is hinged to the inner wall of the screw press and is used to reduce the speed of the second flywheel. Correspondingly, the inner wall of the screw press is provided with a drive component to drive the brake arc plate to rotate.

[0011] By adopting the above technical solution, the brake arc plate assists the second flywheel in decelerating during the reversal of the main screw, thereby reducing the energy consumption of the second drive component. The working process is as follows: while the forging block at the bottom of the main screw forges the metal block, the drive component drives the brake arc plate to brake the main screw. Correspondingly, due to the setting of the brake arc plate, the second drive component can stop operating before the brake arc plate brakes. The main screw remains in a powerless state and rotates by inertia. The brake arc plate reduces the speed of the main screw in a very short time. After the forging block forges the metal block, the brake arc plate cancels the braking of the main screw. The second drive component drives the second flywheel to reverse, and the forging block rises.

[0012] Optionally, the first flywheel, the second flywheel, and the main screw are in clearance fit, and the first flywheel has multiple oil injection channels with interconnected clearances inside.

[0013] By adopting the above technical solution, the clearance fit can provide a certain degree of flexibility. Due to the violent collision of the forging block with the metal block, the collision brings a huge torque force to the main screw and also gives the main screw a vertical upward recoil force. In actual application, the collision process is not ideal and will inevitably generate a radial component force, causing the main screw to deviate radially. The space provided by the clearance fit can give the main screw a certain amount of room to accommodate the collision deviation. In addition, the oil injection channel connects the gap between the main screw and the first flywheel and the second flywheel, and injects oil into it to reduce the friction between the main screw and the two flywheels.

[0014] Optionally, the bearing assembly includes; One ball bearing is installed on the top side and one on the bottom side near the first flywheel, and the two ball bearings are parallel to each other; Support rings, two of different diameters, are provided between the two ball bearings to support them. The two support rings correspond to the inner and outer rings of the ball bearings, respectively, and an oil injection channel connects the part between the two support rings.

[0015] By adopting the above technical solution, the support ring supports the two ball bearings to maintain a certain distance. Under the support of the support ring, the two ball bearings are close to the two end walls of the first flywheel and are symmetrically arranged along the central part of the support ring to ensure the structural stability of the rotational connection of the first flywheel. An oil injection channel connects the part between the support rings, enters the interior of the two ball bearings from the part between the support rings, lubricates the cylindrical bearings, and enters the space between the support ring and the two ball bearings, and between the support ring and the main screw through the gap.

[0016] Optionally, the second flywheel bottom side near the main screw has multiple disc spring grooves, and the multiple disc spring grooves are opened on the same circumference; Each of the aforementioned disc spring slots is equipped with a shock-absorbing disc spring.

[0017] By adopting the above technical solution, the first flywheel and the second flywheel are inserted into the main screw. When the forging block moves down and collides with the metal block, the metal block gives the main screw a vertically upward recoil force, which is transmitted through the main screw to the first flywheel and the second flywheel at the top of the main screw. Over time, this will cause damage to the internal transmission mechanism, deformation of the first flywheel, the second flywheel, and the bearing assembly between them. Therefore, a spring component is set below the second flywheel, that is, a disc spring groove is opened and a disc spring is installed inside the disc spring groove. Multiple disc springs are opened along the axial direction of the second flywheel to evenly buffer the impact force from the transmission component below the second flywheel and improve the impact resistance of the transmission component. The main reason for using disc springs in the above solution is that disc springs have the advantages of small size and large load, and can withstand large loads with small deformation.

[0018] Optionally, a tapered roller bearing is fitted onto the portion of the main screw below the second flywheel, with the rollers of the tapered roller bearing positioned close to the groove of the disc spring to support the shock-absorbing disc spring.

[0019] By adopting the above technical solution, based on the setting of disc springs to buffer the impact force of collisions, tapered roller bearings are installed near the slot. On the one hand, this prevents the shock-absorbing disc springs from falling and provides support. On the other hand, since other transmission components are inserted into the part of the main screw below the second flywheel, bearings need to be set between the other transmission components and the second flywheel to ensure the normal rotation of the second flywheel. However, there are no shock-absorbing disc springs to buffer the impact force below the second flywheel. Therefore, tapered roller bearings that can withstand large axial forces are set. In addition, the above solution uses tapered roller bearings mainly because tapered roller bearings have strong adaptability. That is, they can work in high-speed operation and low-speed heavy-load operation, and can adapt to the situation of sudden speed changes in a short period of time when the second flywheel switches between forward and reverse rotation.

[0020] Optional, also includes; The flange ring is fixed to the part of the main screw below the second flywheel. The cross-sectional diameter of the flange ring is larger than that of the main screw. The two ends of the flange ring are arc-shaped. Correspondingly, the part of the screw press with the corresponding flange ring is provided with a pressure-bearing groove adapted to the flange ring.

[0021] By adopting the above technical solution, the flange ring, as the pressure-bearing and fixing component of the transmission mechanism, relies on the cooperation between the flange ring and the pressure-bearing groove to achieve the stability of the main screw. The weight of the first flywheel, the second flywheel, and other transmission components installed at the top of the main screw is supported by the flange ring and the pressure-bearing groove. The flange ring is set in a gyroscope shape, with the part near the main screw protruding. When the forging block collides with the metal block, the main screw vibrates and shifts. The middle part is set in an arc shape to allow the main screw to automatically reset after vibration and shift, ensuring the positive direction of force transmission. In addition, the flange ring part of the inner wall of the pressure-bearing groove is curved to fit the main screw, that is, the curved surface of the inner wall of the pressure-bearing groove is fitted with the curved surface of the flange ring, increasing the fitting area and increasing the effectiveness of support.

[0022] Optionally, the inner wall of the pressure-bearing groove and the end face of the flange ring are in clearance fit, and the clearance between the main screw and the first flywheel and the second flywheel is connected.

[0023] By adopting the above technical solution, the clearance fit between the inner wall of the pressure-bearing groove and the surface of the flange ring also achieves the yielding effect. That is, as the forging block collides and contacts the metal block, the pressure-bearing groove also collides with the flange ring. The yielding effect of the clearance fit can reduce the collision damage to a certain extent. In addition, the gap connecting the main screw and the first flywheel and the second flywheel allows the lubricating oil injected through the oil injection channel to slide into the pressure-bearing groove, lubricating the gap between the pressure-bearing groove and the flange ring, while reducing the axial impact effect of the flange ring towards the pressure-bearing groove. Furthermore, due to the rotation of the main screw, the flange ring rotates together in the pressure-bearing groove. The entry of lubricating oil can reduce the friction between the surface of the flange ring and the pressure-bearing groove, thereby reducing friction loss.

[0024] In summary, this application includes at least one of the following beneficial technical effects: 1. The traditional large flywheel and the added small flywheel form a dual-flywheel traditional system. The dual-flywheel system changes the traditional single-flywheel drive structure. The large flywheel, which has greater inertia and higher operating energy consumption, is used as an auxiliary drive component in the downward movement process, while the small flywheel, which has less inertia and lower operating energy consumption, is used as a steering and reversing mechanism. When the small flywheel operates in reverse, the impact on the power grid caused by the reversal of the small flywheel drive component is within a safe range. Under this structure, when the main screw rotates and drives the forging block to move downward, the large flywheel and the small flywheel drive simultaneously, accumulating impact energy. When the forging block forges the metal block, the large flywheel and the small flywheel stop driving simultaneously. After the forging block is completed, the drive component of the small flywheel drives the small flywheel to directly reverse and move the main screw upward. During the upward movement process, the large flywheel remains in a disengaged state until the small flywheel reverses again. This optimizes the transmission structure on the traditional screw press and reduces the impact on the power grid caused by the flywheel reversal. 2. The brake pads can further protect the second drive component. When the forging block forges the metal block, the brake pads brake the second flywheel, helping to reduce the speed of the second flywheel and reduce the speed difference before and after the second drive component is driven again. This reduces the energy consumption of the second drive component when it reverses and extends the service life of the second drive component. 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 made in the embodiments of this application to highlight the internal structure.

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

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

[0029] Figure 5 This is a structural schematic diagram made to highlight the disc spring in the embodiments of this application.

[0030] Figure 6 yes Figure 2 Enlarged view of part B.

[0031] Explanation of reference numerals in the attached drawings: 1. Screw press; 11. First asynchronous servo motor; 12. Second asynchronous servo motor; 13. Clutch; 14. Pressure groove; 2. Main screw; 21. Forging block; 22. Bushing; 23. First flywheel; 24. Second flywheel; 25. Bearing assembly; 251. Ball bearing; 252. Support ring; 26. Brake pad; 261. Drive cylinder; 27. Oil injection channel; 28. Disc spring groove; 281. Disc spring; 282. Tapered roller bearing; 29. ​​Flange ring. Detailed Implementation

[0032] The following is in conjunction with the appendix Figure 1-6 This application will be described in further detail.

[0033] This application discloses a dual flywheel drive system for a screw press. (Refer to...) Figure 1A dual flywheel drive system for a screw press includes a main screw 2 vertically disposed inside the screw press 1. The main screw 2 has threads only at its bottom, and a forging block 21 is threaded to the threaded portion of the main screw 2. The forging block 21 is guided and restricted by the bottom support column of the screw press 1 and slides vertically with the rotation of the main screw 2. The rotation of the main screw 2 drives the forging block 21 to move downward, forging a metal block installed in the forging zone of the screw press 1. After forging is completed, the main screw 2 reverses to drive the forging block 21 to move upward, completing a single forging cycle. Thus, the above steps are repeated to perform multiple forging cycles, completing the impact forging of the metal block.

[0034] Reference Figure 1 and Figure 2 A bushing 22 is inserted into the top of the main screw 2. The inner diameter of the bushing 22 is slightly larger than that of the main screw 2, so that the bushing 22 and the top of the main screw 2 are in clearance fit. A first flywheel 23 is rotatably connected to the outer wall of the bushing 22. The first flywheel 23 is horizontally arranged and coaxial with the bushing 22 and the main screw 2. A first asynchronous servo motor 11 for driving the first flywheel 23 to rotate is arranged at the same height as the surface of the first flywheel 23 in the screw press 1. The first asynchronous servo motor 11 can drive the first flywheel 23 by means of gear set or belt drive. In this embodiment, belt drive is adopted.

[0035] Reference Figure 2 and Figure 3 In this embodiment, a bearing assembly 25 is provided between the first flywheel 23 and the bushing 22. The bearing assembly 25 includes two parallel ball bearings 251 and two support rings 252 between the two ball bearings 251. The two cylindrical bearings are respectively positioned near the top and bottom surfaces of the first flywheel 23. The two support rings 252 have different diameters. One support ring 252 is fitted onto the bushing 22 and is used to support the inner ring of the ball bearing 251, while the other support ring 252 is used to support the outer ring of the ball bearing 251. Due to the rotational connection between the first flywheel 23 and the bushing 22, when they rotate independently, the bearing assembly 25 is needed to reduce friction and friction loss. Based on this, the two ball bearings 251 are respectively positioned near the two end surfaces of the first flywheel 23 to share the contact pressure of the first flywheel 23, ensuring the smooth operation of the first flywheel 23.

[0036] Reference Figure 1 and Figure 2 A clutch 13 is provided at the top end of the main screw 2. The clutch 13 covers the part from the top end of the main screw 2 to the first flywheel 23 near the main screw 2. It is used for the engagement and disengagement of the first flywheel 23 and the main screw 2. In this embodiment, the separator adopts a common friction clutch 13. The principle of the friction clutch 13 will not be described in detail.

[0037] Reference Figure 2A second flywheel 24 is horizontally arranged below the first flywheel 23, with a through hole in the center of the second flywheel 24 adapted to the main screw 2. When the main screw 2 is inserted into the through hole of the second flywheel 24, the two are in clearance fit, and the clearance between the main screw 2 and the second flywheel 24 is connected to the clearance between the main screw 2 and the bushing 22. In this embodiment, the thickness and diameter of the second flywheel 24 are smaller than the thickness and diameter of the first flywheel 23. The top side of the second flywheel 24 abuts against the bottom side of the first flywheel 23. A ball bearing 251 is installed on the top side of the second flywheel 24 for relative rotation between the first flywheel 23 and the second flywheel 24. A second asynchronous servo motor 12 is arranged at the same height as the horizontal wheel surface of the screw press 1 and the second flywheel 24. The second asynchronous servo motor 12 drives the second flywheel 24 to rotate via a belt.

[0038] Therefore, taking a single forging cycle as an example, the operation process of this embodiment is described in detail below; When the clutch 13 is engaged with the main screw 2 and the first flywheel 23, the first asynchronous servo motor 11 drives the first flywheel 23 to rotate, and the second asynchronous servo motor 12 drives the second flywheel 24 to rotate. The first flywheel 23 and the second flywheel 24 synchronously drive the main screw 2 to rotate. The forging block 21 at the bottom of the main screw 2 moves downward. Before the forging block 21 collides with the metal block, the clutch 13 separates the first flywheel 23 from the main screw 2. The first asynchronous servo motor 11 stops operating, and the first flywheel 23 remains separated from the main screw 2.

[0039] Before the forging block 21 collides with the metal block, the second asynchronous servo motor 12 stops operating simultaneously with the first asynchronous servo motor 11. Both motors remain idle, and the output shaft is driven to rotate by the inertial force of the first flywheel 23 and the second flywheel 24. The speed of the main screw 2 drops sharply when the forging block 21 collides with the metal block. After the forging block 21 completes a single forging, the second asynchronous servo motor 12 drives the second flywheel 24 to directly reverse, causing the forging block 21 to rise again. During the process of the main screw 2 reversing and causing the forging block 21 to rise, the first flywheel 23 maintains almost the original speed and rotates in the original direction due to the presence of the bearing assembly 25.

[0040] When the forging block 21 is raised to a preset height, the second asynchronous servo motor 12 drives the main screw 2 to reverse again. When the main screw 2 descends again, it rotates in the same direction as the first flywheel 23, which is still idling. The clutch 13 engages the main screw 2 with the first flywheel 23, and the first asynchronous servo motor 11 starts again, so that the main screw 2 is driven by the first asynchronous servo motor 11 and the second asynchronous servo motor 12 simultaneously, until the forging block 21 collides with the metal block again.

[0041] It should be noted that, for the sake of simplifying the accompanying drawings, the first flywheel 23 and the second flywheel 24 are both directly driven by belts in this embodiment. However, in actual applications, belt drive pulleys need to be installed below both the first flywheel 23 and the second flywheel 24.

[0042] Reference Figure 2 and Figure 4 Based on the above operation process, in this embodiment, two brake arc plates 26 are provided on the outside of the side wall of the second flywheel 24. Each brake arc plate 26 is semi-circular and is sleeved on the side wall of the second flywheel 24. Inside the screw press 1, a drive cylinder 261 is horizontally provided at one end corresponding to each brake arc plate 26. The cylinder body of the drive cylinder 261 is hinged to the inner wall of the screw press 1, and the piston rod end of the drive cylinder 261 is fixedly connected to the opposite side of the brake arc plate 26. The end of each brake arc plate 26 away from the drive cylinder 261 is hinged to the inner wall of the screw press 1, so as to realize that the piston rod of the drive cylinder 261 extends or retracts, and the two brake arc plates 26 can rotate towards or away from each other at a certain angle.

[0043] Two drive cylinders 261 extend their piston rods towards each other, and two brake pads 26 rotate towards each other around the hinge point, gripping the second flywheel 24 from both sides of its diameter to brake it. The two drive cylinders 261 retract their piston rods, and the two brake pads 26 rotate in opposite directions around the hinge point to release the second flywheel 24 and cancel the braking of it.

[0044] In this embodiment, the braking arc plate 26 can reduce the rotational speed of the second flywheel 24 by contact friction in a short time, thereby reducing the operational burden on the second asynchronous servo motor 12. Simultaneously with the forging block 21 moving downwards to impact the metal block, the drive cylinder 261 extends its piston rod, relying on the clamping force of the braking arc plate 26 to brake the second flywheel 24. After forging is completed, the second asynchronous servo motor 12 reverses direction. Braked by the braking arc plate 26, the rotational speed of the second flywheel 24 decreases, reducing the speed difference before and after the second asynchronous servo motor 12 reverses, thus saving power and further reducing peak energy consumption, protecting the normal power supply of other electrical components in the same power grid.

[0045] The same end of each brake disc 26 is hinged to the inner wall of the screw press 1, so that each brake disc 26 can rotate freely around the hinge point. Reference Figure 2The first flywheel 23 has two oil injection channels 27 inside. The oil injection ports of the two oil injection channels 27 are located near the top edge of the first flywheel 23 to facilitate oil injection by relevant technicians. The oil outlet port of one oil injection channel 27 is located near the support ring 252. Multiple oil inlet holes are equally spaced along the axial direction on the side wall of the support ring 252 for injecting lubricating oil into the oil injection channel 27. The lubricating oil enters the part between the two support rings 252 to lubricate the two ball bearings 251. The oil outlet port of the other oil injection channel 27 passes through the bushing 22 and connects the gap between the bushing 22 and the main screw 2 for lubrication between the main screw 2 and the bushing 22, and between the main screw 2 and the second flywheel 24.

[0046] Reference Figure 1 and Figure 2 In this embodiment, the bottom side of the first flywheel 23 is provided with multiple cavities. Therefore, in order to facilitate the opening of the oil injection channel 27, the oil injection channel 27 is connected to the cavity in the part where no cavity is opened, and a hose is installed in the cavity to connect the oil injection channel 27 opened in the cavity, thus saving the cost and time of opening the oil injection channel 27.

[0047] Reference Figure 3 and Figure 5 The second flywheel 24 has a disc spring groove 28 inside. Multiple disc spring grooves 28 are equally spaced along the circumference of the second flywheel 24. The multiple disc spring grooves 28 are located in the part of the second flywheel 24 near the main screw 2. Multiple disc springs 281 are stacked in each disc spring groove 28. Adjacent disc springs 281 in the same disc spring groove 28 are installed in opposite directions. The disc springs 281 near the groove opening of the disc spring groove 28 protrude from the surface of the disc spring groove 28. A tapered roller bearing 282 is inserted into the bottom side of the second flywheel 24. The diameter of the tapered roller bearing 282 is the same as the diameter of the distribution circle of the multiple disc spring grooves 28, so that the tapered roller bearing 282 is used to close the groove opening of the disc spring groove 28 and support the multiple disc springs 281 installed in the disc spring groove 28.

[0048] In this embodiment, the disc spring 281 is used to buffer the reverse force generated along the main screw 2 when the forging block 21 forges the metal block. The disc spring 281 is set on the bottom side of the second flywheel 24, that is, the bottom side of the flywheel drive system, to avoid hard and violent impact damage to the transmission structure composed of the first flywheel 23 and the second flywheel 24.

[0049] Reference Figure 2 and Figure 6A flange ring 29 is fixedly connected to the part of the main screw 2 below the second flywheel 24. The flange ring 29 can be regarded as part of the main screw 2 and is an integral part of the main screw 2. The diameter of the ring surface of the flange ring 29 is larger than the interface diameter of the main screw 2. The side surface of the main screw 2 and the side surface of the flange ring 29 are joined in an arc shape, making the flange ring 29 approximately gyroscope-shaped. Correspondingly, a pressure-bearing groove 14 adapted to the diameter of the flange ring 29 is opened in the part of the screw press 1 corresponding to the flange ring 29, and the inner wall of the pressure-bearing groove 14 is a curved surface that fits the flange ring 29.

[0050] In this embodiment, the flange ring 29 serves as the main pressure-bearing component in the transmission system, bearing the installation weight of the first flywheel 23 and the second flywheel 24. The entire main screw 2 is positioned by the contact between the bottom wall of the pressure-bearing groove 14 and the flange ring 29. Taking advantage of the prominent structure of the flange ring 29, a pressure-bearing groove 14 is provided to fit the ring wall portion of the flange ring 29. After the main screw 2 is displaced by collision and vibration, the curved surface of the flange ring 29 and the pressure-bearing groove 14 can automatically reset the main screw 2 after the collision displacement.

[0051] Reference Figure 1 and Figure 2 In this embodiment, considering that the flange ring 29 rotates synchronously with the main screw 2, the flange ring 29 and the inner wall of the pressure bearing groove 14 are set to a clearance fit. Furthermore, the gap between the flange ring 29 and the inner wall of the pressure bearing groove 14 is connected to the gap between the main screw 2 and the second flywheel 24, so that the lubricating oil injected through the oil injection channel 27 flows into the pressure bearing groove 14.

[0052] The implementation principle of the dual flywheel transmission system of a screw press according to the present application is as follows: In this embodiment, an additional smaller flywheel is added on the basis of a single flywheel. The large flywheel in the traditional scheme is used as the main driving flywheel, and the newly added small flywheel is used as the reversing flywheel. The first asynchronous servo motor 11 and the second asynchronous servo motor 12 are used to drive the large and small flywheels respectively to drive the main screw 2 to rotate and reverse.

[0053] The main operating process is as follows: when the main screw 2 rotates and drives the forging block 21 to move downward, the first asynchronous servo motor 11 and the second asynchronous servo motor 12 operate synchronously, driving the main screw 2 to rotate through the first flywheel 23 and the second flywheel 24. The main screw 2 simultaneously receives the superposition of the driving forces of the first flywheel 23 and the second flywheel 24, accumulating huge energy during the downward movement of the forging block 21, so that the forging block 21 can violently forge the metal block.

[0054] Before the forging block 21 moves down to abut the metal block, the clutch 13 separates the first flywheel 23 from the first asynchronous servo motor 11. Through the setting of the bearing assembly 25, the first flywheel 23 can maintain rotation at the original speed for a short time, while the second asynchronous servo motor 12 stops driving, so that the second flywheel 24 follows the main screw 2 to keep spinning. Relying on inertia, it keeps the metal block moving down for a very short time and violently collides with the metal block to complete a single forging.

[0055] While the forging block 21 forges the metal block, the drive cylinder 261 extends its piston rod to drive the brake pad 26 to engage with the second flywheel 24. Thus, when the forging block 21 contacts the metal block, in conjunction with the braking of the brake pad 26, the speed of the main screw 2 drops to zero in a short time without being driven by the second asynchronous servo motor 12.

[0056] However, due to the sudden stop of the forging block 21, and the fact that the main screw 2 was still running at a high speed before the sudden stop, when the main screw 2 was braked by the metal block and the brake pad 26, the rod itself instantly generated a huge reverse shear force along the tangential direction and a recoil force along the axial direction. The disc spring 281 and the tapered roller bearing 282 in this embodiment were buffered when the recoil force was transmitted to the bottom end face of the second flywheel 24, thus protecting the second flywheel 24 and the transmission drive assembly above the second flywheel 24.

[0057] In this embodiment, to prevent the main screw 2 from shifting when subjected to recoil force, the pressure groove 14 and the relatively protruding flange ring 29 that is adapted to the pressure groove 14 are used to position the screw through structural positioning, thus preventing axial displacement. Furthermore, the protruding curved surface in the center can quickly return to the correct position when subjected to impact.

[0058] After the forging block 21 forges the metal block, the second asynchronous servo motor 12 directly drives the second flywheel 24 to reverse. The first flywheel 23 and the main screw 2 remain separated when the second flywheel 24 reverses. When the forging block 21 rises to a certain height, the second asynchronous servo motor 12 pulls the second flywheel 24 to reverse again, and the forging block 21 descends, entering the next forging cycle.

[0059] In this embodiment, a small-sized and low-inertia second flywheel 24 is used as a reversing mechanism. When the second asynchronous servo motor 12 drives the second flywheel 24 to reverse directly, the electric surge is low. Therefore, the peak instantaneous power consumption is still within a safe range, protecting the power grid while improving the electrical safety in the factory workshop.

[0060] As the main screw 2 rotates and drives the forging block 21 to descend, the clutch 13 re-engages the first flywheel 23 with the main screw 2, and the first asynchronous servo motor 11 and the second asynchronous servo motor 12 operate simultaneously, so that the main screw 2, driven by the first flywheel 23 and the second flywheel 24, repeats multiple forging cycles according to the above steps to complete the die forging process of the metal block.

[0061] 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 double flywheel drive system for a screw press, comprising a main screw (2), a first flywheel (23) horizontally inserted into the top end of the main screw (2), and a first driving member for driving the first flywheel (23) to rotate on the screw press (1), characterized in that: Also includes; The second flywheel (24) is inserted into the main screw (2) and horizontally positioned below the first flywheel (23). It is independent of the first flywheel (23) and has a smaller cross-sectional diameter than the first flywheel (23). The screw press (1) is equipped with a second driving component for driving the second flywheel (24) to rotate. The bottom side of the second flywheel (24) near the main screw (2) is provided with multiple disc spring grooves (28), which are located on the same circumference. Each disc spring groove (28) is provided with a shock-absorbing disc spring (281). The main screw (2) is located at... The portion below the second flywheel (24) is fitted with a tapered roller bearing (282). The rollers of the tapered roller bearing (282) are positioned close to the groove of the disc spring groove (28) to support the shock-absorbing disc spring (281). The flange ring (29) is fixed to the portion of the main screw (2) corresponding to the portion below the second flywheel (24). The cross-sectional diameter of the flange ring (29) is larger than that of the main screw (2). The two ends of the flange ring (29) are arc-shaped. Correspondingly, the portion of the screw press (1) corresponding to the flange ring (29) is provided with a pressure-bearing groove (14) adapted to the flange ring (29). The bearing assembly (25) is sleeved between the top of the main screw (2) and the first flywheel (23) for independent rotation of the first flywheel (23) and the main screw (2); The clutch (13) is located at the top end of the main screw (2) and is used for the separation and engagement of the first flywheel (23) and the main screw (2).

2. The double flywheel transmission system of a screw press according to claim 1, characterized in that: Also includes; Braking arc plate (26) is hinged to the inner wall of screw press (1) and is used to reduce the speed of second flywheel (24). Correspondingly, the inner wall of screw press (1) is provided with a driving component to drive the braking arc plate (26) to rotate.

3. The double flywheel transmission system of a screw press according to claim 1, characterized in that: The first flywheel (23), the second flywheel (24) and the main screw (2) are in clearance fit. The first flywheel (23) has multiple oil injection channels (27) with interconnected clearances inside.

4. The double flywheel transmission system of a screw press according to claim 1, characterized in that: The bearing assembly (25) includes; One ball bearing (251) is provided on the top side and one on the bottom side near the first flywheel (23), and the two ball bearings (251) are parallel to each other; Support rings (252) of different diameters are provided between the two ball bearings (251) to support the two ball bearings (251). The two support rings (252) correspond to the inner ring and outer ring of the ball bearings (251) respectively. One of the oil injection channels (27) connects the part between the two support rings (252).

5. The double flywheel transmission system of a screw press according to claim 1, characterized in that: The inner wall of the pressure-bearing groove (14) is in clearance fit with the end face of the flange ring (29), and it connects the gap between the main screw (2) and the first flywheel (23) and the second flywheel (24).

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