Cage system for hydraulic machine

Abstract

A lower cage plate fixedly mounted on a bottom plate and an upper cage plate right above the lower cage plate are fixedly connected through a plurality of cage bolts to form a cage-shaped structure, and a cylinder body mounting opening and a cylinder bottom mounting opening which are coaxially opposite to each other are formed in the upper cage plate and the lower cage plate respectively; the cylinder bottom of an oil hydraulic cylinder contained in the cage-shaped structure can be inserted into the cylinder bottom installation opening and is fixed to the bottom plate, a cylinder body of the oil hydraulic cylinder can be fixedly inserted into the cylinder body installation opening, and a plunger of the oil hydraulic cylinder can stretch out of the cage-shaped structure through the cylinder body installation opening and is connected with an upper beam of a pressing machine of the hydraulic machine in a self-alignment mode. The upper guide body and the lower guide body are fixedly installed on the left side and the right side of the upper cage plate and the left side and the right side of the lower cage plate respectively, and the upper guide face of the upper guide body and the upper guide face of the lower guide body can vertically slide and guide along guide plates on a left stand column and a right stand column of the hydraulic machine respectively. And the height and the weight of the hydraulic machine are reduced, and the unbalance loading resistance is high.

Description

Technical Field

[0001] This invention relates to the field of hydraulic press technology, and more particularly to a cage system for a hydraulic press. Background Technology

[0003] During the forging process of a hydraulic press, the hydraulic system generates tens of thousands of tons of pressure, which is transmitted to the forging through the plunger-moving crossbeam-pad-die. However, this causes uneven pressure distribution on the die, which changes constantly during the pressing process, causing the moving crossbeam to sway left and right, and back and forth—due to the swaying torque. The above analysis shows that transmitting pressure and resisting eccentric loads are the main functions of the moving crossbeam.

[0004] For nearly a century, the engineering community has designed rigid, stacked plate assemblies and thick-plate welding and casting "high beams" (a type of beam defined by mechanics) to ensure the pressure transmission and anti-eccentricity capabilities of the movable crossbeam. In the era of multi-cylinder forging hydraulic presses, the weight of the movable crossbeam could reach thousands of tons, even close to ten thousand tons. Since 1984, heavy-duty hydraulic cylinders have undergone significant technological improvements and structural optimizations, greatly increasing the tonnage of a single hydraulic cylinder. This ended the era where the movable crossbeam combined the output of multiple hydraulic cylinders to form a combined force. Even after forging hydraulic presses entered the single-cylinder era, the weight of the movable crossbeam could still reach hundreds of tons, close to a thousand tons, remaining a massive structure. The working master cylinder is mounted on its upper surface and connected to the piston or cylinder body of the master cylinder. See [link to documentation]. Figure 1 .

[0005] For decades, the engineering community has used a traditional concept in the design of movable beams: utilizing a "high beam" with strong mechanical resistance to bending and shear to transmit pressure and resist eccentricity. This requires significantly increasing the angular stiffness of the high beam to resist the combined effects of strong compression, bending, and shear forces. This is mainly reflected in the thickness of the upper and lower cover plates of the high beam, which must be sufficiently thick. For shear resistance, the web of the high beam must also be sufficiently thick; otherwise, it will not withstand the shear force. During operation, if the forging is small, the movable beam bends downwards, the upper cover plate bears the combined tension and compression, the lower cover plate bears the combined compression and compression, and the neutral layer bears enormous shear stress and unidirectional vertical compressive stress. If the forging area is large, the movable beam bends upwards, and the stress state is exactly the opposite. Figure 1 ). Summary of the Invention

[0006] To overcome the above deficiencies, the present invention provides a cage system for a hydraulic press. This cage system for a hydraulic press greatly shortens the load transmission chain, simplifies the installation procedure and workload of the hydraulic press, reduces the height and weight of the hydraulic press, and has strong resistance to eccentric loads.

[0007] The technical solution adopted by this invention to solve its technical problem is: a cage system for a hydraulic press, comprising an upper cage plate, a lower cage plate, cage bolts, a bottom plate, an upper guide body, and a lower guide body. The lower cage plate is fixedly installed on the upper surface of the bottom plate. The upper cage plates are arranged parallel to each other above the lower cage plates. The upper and lower cage plates respectively form coaxially opposite cylinder mounting ports and cylinder bottom mounting ports. The upper and lower cage plates are fixedly connected together by a plurality of cage bolts arranged at intervals along the circumference of the cylinder mounting ports and cylinder bottom mounting ports. The upper cage plate, lower cage plate, bottom plate, and cage bolts form a cage-shaped structure, and the hydraulic cylinder of the hydraulic press can be accommodated within the cage-shaped structure. The bottom can be inserted into the cylinder bottom mounting port of the lower cage plate and fixedly installed on the base plate. The cylinder body of the hydraulic press's oil cylinder can be fixedly inserted into the cylinder body mounting port of the upper cage plate. The plunger of the hydraulic press's oil cylinder can extend out of the upper outer side of the cage structure through the cylinder body mounting port and self-align with the upper beam of the hydraulic press. The upper guide body is fixedly installed on the left and right sides of the upper cage plate, and the lower guide body is fixedly installed on the left and right sides of the fixed connection structure between the lower cage plate and the base plate. Both the upper and lower guide bodies have vertically extending guide surfaces. The guide surfaces on each upper and lower guide body can slide up and down along the guide plates extending vertically on the left and right columns of the hydraulic press.

[0008] As a further improvement of the invention, the lower end of the cylinder body of the hydraulic cylinder is tightly abutted against the upper side of the lower cage plate, and the upper end of the cylinder body of the hydraulic cylinder is tightly abutted against the lower side of the upper cage plate. The lower side of the upper cage plate and the upper end surface of the cylinder body of the hydraulic cylinder are respectively provided with an upper embedding groove, and the upper side of the lower cage plate and the lower end surface of the cylinder body of the hydraulic cylinder are respectively provided with a lower embedding groove. An upper positioning ring and a lower positioning ring are also provided. The upper and lower ends of the upper positioning ring are respectively inserted into the upper embedding grooves on the lower side of the upper cage plate and the upper end surface of the cylinder body of the hydraulic cylinder, thereby achieving the stop positioning of the upper cage plate and the upper end surface of the cylinder body of the hydraulic cylinder. The upper and lower ends of the lower positioning ring are respectively inserted into the lower end surface of the cylinder body of the hydraulic cylinder and the lower embedding grooves on the upper side of the lower cage plate, thereby achieving the stop positioning of the lower cage plate and the lower end surface of the cylinder body of the hydraulic cylinder.

[0009] As a further improvement to the invention, a leak-proof sealing ring, a high-pressure resistant sliding sealing ring, and a high-pressure resistant fixed sealing ring are also provided. The inner diameter of the cylinder mounting port of the upper cage plate is larger than the inner diameter of the hydraulic cylinder. An annular countersunk groove communicating with the inside of the cylinder is formed on the upper end face of the hydraulic cylinder. The upper section of the leak-proof sealing ring is inserted into the inner side of the upper cage plate, and the lower end of the leak-proof sealing ring is inserted into the annular countersunk groove on the upper end face of the hydraulic cylinder. The inner side of the leak-proof sealing ring is in dynamic sealing contact with the outer circumference of the plunger of the hydraulic cylinder. The high-pressure resistant sliding sealing ring is fixedly sleeved on the outer circumference of the lower end of the plunger of the hydraulic cylinder. The outer circumference of the high-pressure resistant sliding sealing ring is in dynamic sealing contact with the inner side of the hydraulic cylinder. The high-pressure resistant fixed seal is fixedly installed on the bottom of the hydraulic cylinder and can seal the connection between the bottom of the hydraulic cylinder and the cylinder body.

[0010] As a further improvement of the invention, a countersunk cylinder receiving groove is formed on the lower side of the upper cage plate, which is connected to its inner ring. The upper end of the cylinder of the hydraulic cylinder is inserted into the cylinder receiving groove, and the outer side wall of the upper end of the hydraulic cylinder is stopped on the inner side wall of the cylinder receiving groove.

[0011] As a further improvement to the invention, a buffer body is fixedly installed on the upper end face of the bottom of the hydraulic cylinder. After the lower end face of the piston of the hydraulic cylinder descends to the bottom, it contacts the buffer body for buffering. The bottom plate, the lower cage plate, the cylinder bottom and the buffer body together form a force transmission structure, and its total thickness exceeds the thickness of the upper cage plate.

[0012] As a further improvement of the invention, the plunger of the hydraulic cylinder is provided with an oil passage extending through it along its axial direction, and an oil inlet pipe sealing ring is provided at the upper opening of the oil passage, which can seal and connect the oil passage with the oil inlet pipe.

[0013] As a further improvement to the invention, the upper end of the plunger of the hydraulic cylinder is connected to the upper beam of the hydraulic press through a ball ring self-aligning support structure or a square ring self-aligning support structure.

[0014] As a further improvement to the invention, the upper cage plate, lower cage plate, and bottom plate are all square plates. The left and right sides of the upper cage plate, lower cage plate, and bottom plate are respectively stopped on the left and right columns of the hydraulic press. The front and rear edges of the inner sides of the left and right columns respectively form vertically extending chamfered slopes. The guide plates are fixedly installed on the chamfered slopes of the left and right columns. The guide surfaces on the upper guide plates and lower guide bodies arranged along the front-back direction on the left and right sides of the cage system form an X-shaped guide system for the cage system.

[0015] As a further improvement of the invention, a gap adjuster is installed on both the upper and lower conductors. The gap adjuster can adjust the tilt angle of the guide surfaces of the upper and lower conductors and the distance between them and the guide plates, thereby adjusting the gap between the upper guide surfaces of the upper and lower guide bodies and the upper guide plates of the left and right columns.

[0016] As a further improvement to the invention, the cage bolts include a number of coarse cage bolts and a number of fine cage bolts. The number of coarse cage bolts are distributed at the four corners of the upper cage plate and the lower cage plate; the number of fine cage bolts are distributed on the front and rear and left and right sides of the hydraulic press.

[0017] The beneficial technical effects of this invention are as follows: This invention fixes the bottom of the hydraulic cylinder to the base plate and the lower cage plate, and the plunger of the hydraulic cylinder to the upper beam of the press. The load is transmitted through the cylinder bottom, pad plate, and upper die, forming the shortest load transmission chain, which is beneficial for improving the real-time performance of hydraulic transmission and is a structural prerequisite for intelligent strain rate control. This invention designs an upper cage plate above the lower cage plate and significantly increases the distance between them. Simultaneously, cage bolts connect the upper and lower cage plates, forming a low-angular-stiffness, non-welded, detachable connection. The cylinder bottom of the hydraulic cylinder is installed in the center of the lower cage plate to form a low-angular-stiffness cage system. Under eccentric load torque, the cage system will not tip over as a whole. Instead of rotating, the upper and lower cage plates move in opposite directions. The left and right columns of the forging machine frame provide a counterforce by blocking the upper and lower cage plates, thus ensuring that the cage system has good resistance to eccentric loads. This is beneficial for the sealing and protection of the hydraulic cylinder and the cylinder guide, and can effectively extend the service life of the upper guide plate of the machine frame. The invention also greatly simplifies the installation procedure and workload of the hydraulic press, reducing the installation workload by 20-30% and greatly shortening the construction cycle of the forging hydraulic press. The invention also reduces the weight of the hydraulic press by about 15% and the height of the hydraulic press by 15-20%, which in turn reduces the height of the factory building by about 10%. Attached Figure Description

[0018] Figure 1 This is a schematic diagram of the structural principle of a high beam load transfer hydraulic press in the prior art;

[0019] Figure 2 A schematic diagram of the preliminary improved structure for extending the plunger;

[0020] Figure 3 A schematic diagram illustrating the structural principle of a further improved tilting hydraulic cylinder;

[0021] Figure 4 This is a schematic diagram of the structural principle of the plate-transfer hydraulic press using the present invention;

[0022] Figure 5 This is a perspective view of the cage system of the present invention;

[0023] Figure 6 Front view of the cage system of the present invention;

[0024] Figure 7 for Figure 6 Sectional view along line AA;

[0025] Figure 8 The diagram shows the connection principle between the upper end of the plunger of the hydraulic cylinder and the upper beam of the hydraulic press through a square ring self-aligning support structure.

[0026] Figure 9 Top view of the cage system of the present invention;

[0027] Figure 10A three-dimensional view of the cage-shaped structure formed by the present invention;

[0028] Figure 11 Front view of the cage-shaped structure formed by the present invention;

[0029] Figure 12 for Figure 11 Sectional view along the BB direction;

[0030] Figure 13 Top view of the cage-shaped structure formed by the present invention;

[0031] Figure 14 This is a force diagram of the present invention when used on a die forging hydraulic press;

[0032] Figure 15 for Figure 14 Sectional view along the CC direction. Detailed Implementation

[0033] The technical solutions of the present invention will be clearly and completely described below with reference to the accompanying drawings of the embodiments of the present invention. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments.

[0034] Example: A cage system for a hydraulic press includes an upper cage plate 11, a lower cage plate 12, cage bolts 13, a base plate 14, an upper guide body 15, and a lower guide body 16. The lower cage plate 12 is fixedly installed on the upper surface of the base plate 14. The upper cage plates 11 are arranged parallel to each other above the lower cage plate 12. The upper cage plate 11 and the lower cage plate 12 respectively have coaxially facing cylinder body 22 mounting ports and cylinder bottom 21 mounting ports. The upper cage plate 11 and the lower cage plate 12 are fixedly connected together by a plurality of cage bolts 13 arranged at intervals along the circumference of the cylinder body 22 mounting ports and the cylinder bottom 21 mounting ports. The upper cage plate 11, the lower cage plate 12, the base plate 14, and the cage bolts 13 form a cage-shaped structure. The hydraulic cylinder of the hydraulic press can be accommodated within the cage-shaped structure, and the cylinder bottom 21 of the hydraulic cylinder can be inserted into the cylinder of the lower cage plate 12. The bottom 21 is installed in the mounting port and fixedly mounted on the bottom plate 14. The cylinder body 22 of the hydraulic press can be fixedly inserted into the mounting port of the cylinder body 22 of the upper cage plate 11. The plunger 23 of the hydraulic press cylinder can extend out of the outer side of the upper end of the cage structure through the mounting port of the cylinder body 22 and be self-aligned with the upper beam 31 of the hydraulic press (connection with minimal swing). The upper guide body 15 is fixedly installed on the left and right sides of the upper cage plate 11. The lower guide body 16 is fixedly installed on the left and right sides of the fixed connection structure between the lower cage plate 12 and the bottom plate 14. Vertically extending guide surfaces 17 are formed on both the upper guide body 15 and the lower guide body 16. The guide surfaces 17 on each upper guide body 15 and lower guide body 16 can slide up and down along the guide plates 34 extending vertically on the left column 32 and the right column 33 of the hydraulic press.

[0035] The aforementioned cage system is one of the important core systems used in modern hydraulic presses, especially heavy-duty die forging hydraulic presses. It abandons the traditional design concept of beam loading and beam resisting load, which has been used in hydraulic presses for nearly 90 years since 1938. Instead, it replaces the concept of high beam load transmission (vertical pressure) with plate load transmission, thereby achieving more efficient transmission of huge pressure.

[0036] During the design process, we first lengthened the plunger 23 so that it could enter the bottom of the movable crossbeam 4, such as... Figure 2 As shown. In this way, through the base plate 14 of the movable crossbeam, tens of thousands of tons of vertical pressure are directly transmitted to the pad plate 5 below; furthermore, we rotate the hydraulic cylinder system 180 degrees, so that the cylinder bottom 21 is below and the plunger 23 is above, thus reducing the height of the hydraulic press by 10% to 15%, significantly shortening its LTC. These technological advantages result in a significant reduction in construction investment and a marked shortening of the construction period. See... Figure 3 .

[0037] The shift from beam-to-plate load transfer is crucial for transmitting vertical pressure. To improve the eccentric load resistance of the plate-to-plate structure, an upper cage plate 11 was designed above the lower cage plate 12, with a significantly increased distance between them, and they are connected with bolts (hereinafter referred to as cage bolts 13). This is a low-angular-stiffness, non-welded, detachable connection. A hydraulic cylinder base 21 is added to the center of the lower cage plate 12. Figure 4 Thus, the present invention completely abandons the sorghum load-bearing structure.

[0038] The diameter of bolt 13, compared to its length, can be considered a "two-force member" in mechanical terms. Figure 4 Since it does not bear bending moments, the cage structure can be considered a low angular stiffness structure. Compared with a high beam with high angular stiffness, it can ensure that under the action of a deflection moment M1 (clockwise), the upper cage plate 11 and the lower cage plate 12 will not flip as a whole, but will translate in approximately the opposite direction: the upper cage plate 11 to the left and the lower cage plate 12 to the right, forming an anti-deflection moment M2 (counterclockwise). Obviously, M1 = -M2 (the absolute values ​​are equal, but the signs are opposite). Figure 4 Because the deflection torque M1 acts on the lower cage plate 12, it will cause the upper cage plate 11 to shift to the right. The rightward shift of the upper cage plate 11 is hindered by the frame guiding system, forming a reaction force F1; the upper cage plate 11 is also hindered by the plunger 23, forming a reaction force F2. Clearly, the rigidity of the frame is much greater than that of the self-aligning plunger 23, so F1 will be much greater than F2. This effectively protects the sealing-guiding system at F1 and other seals in the hydraulic cylinder. This near-translational characteristic of the cage plate in the cage structure is something that high-rigidity moving transverse beams (high beams) do not possess.

[0039] Figure 13 and Figure 14 This further explains the stress situation of the cage-type anti-eccentricity system. Assuming a maximum eccentricity of e1 = 250 mm under a load of 60,000 tons, then M1 = P x e1 = 60,000 tons x 0.25 m = 15,000 tons - m. This M1 is jointly borne by the anti-eccentricity moment M2 generated by F1 and F2, i.e., (F1 + F2) = M1 / e2 = 1.5 / 2.5 = 6000 tons. The vast majority of this 6000-ton lateral thrust will be borne by the frame. For a frame with a working load of 60,000 tons, its preload will be as high as 6 x 1.5 = 90,000 tons; the 6000-ton lateral thrust will not cause problems with the strength and stiffness of the frame.

[0040] The cage bolt 13 only bears axial force and not bending moment. The eccentric load moment acting on the base plate 14 is mainly transmitted to the bearing frame of the press through the coupling effect of the cage bolt 13 with the upper cage plate 11 and the lower cage plate 12.

[0041] The eccentric loading causes elastic deformation of the cage, so that the upper cage plate 11 and the lower cage plate 12 mainly translate rather than rotate as a whole, which greatly protects the sealing and guiding systems in the hydraulic cylinder.

[0042] The connection between the cage bolt 13 and the upper cage plate 11 and lower cage plate 12 is detachable. At the installation site, the upper cage plate 11 can be easily removed to insert the cylinder body 22, completing the assembly of the entire system. This feature is extremely important for the transportation and installation of heavy-duty (e.g., 60,000 tons) and ultra-heavy-duty (e.g., 100,000 tons) presses, greatly increasing the press's manufacturability, reducing construction costs, and shortening the construction period.

[0043] Figure 1 It is a 40,000-ton high beam system using a traditional structure. As shown in the diagram, its LTC (plunger 23 (including the hinge ball) + heightened movable crossbeam + pad plate + upper mold 6) is very long, while the anti-eccentricity e is very small. The high beam significantly increases the weight of the hydraulic press and the height of the press and plant, and requires on-site assembly and winding, making construction difficult and time-consuming. Figure 4 This is a hydraulic press designed using the concept and principle of this patent. Its LTC is very short, while its anti-eccentricity e is very large, meaning that the real-time performance of the hydraulic transmission is good; the large eccentricity e means that the lateral thrust caused by the off-center load is small, which is beneficial to the protection of the seal and the in-cylinder guide and to extend the service life of the frame sliding guide plate 34.

[0044] The lower end of the cylinder body 22 of the hydraulic cylinder is tightly abutted against the upper side of the lower cage plate 12, and the upper end of the cylinder body 22 of the hydraulic cylinder is tightly abutted against the lower side of the upper cage plate 11. The lower side of the upper cage plate 11 and the upper end surface of the cylinder body 22 of the hydraulic cylinder are respectively provided with an upper embedded groove, and the upper side of the lower cage plate 12 and the lower end surface of the cylinder body 22 of the hydraulic cylinder are respectively provided with a lower embedded groove. An upper positioning ring 7 and a lower positioning ring 8 are also provided. The upper and lower ends of the upper positioning ring 7 are respectively inserted into the upper embedded grooves on the lower side of the upper cage plate 11 and the upper end surface of the cylinder body 22 of the hydraulic cylinder, thereby achieving the stop positioning of the upper cage plate 11 and the upper end surface of the cylinder body 22 of the hydraulic cylinder. The upper and lower ends of the lower positioning ring 8 are respectively inserted into the lower end surface of the cylinder body 22 of the hydraulic cylinder and the lower embedded grooves on the upper side of the lower cage plate 12, thereby achieving the stop positioning of the lower cage plate 12 and the lower end surface of the cylinder body 22 of the hydraulic cylinder. The upper positioning ring 7 and the lower positioning ring 8 work together with the cage bolt 13 to achieve the positioning and locking of the upper cage plate 11 and the lower cage plate 12 with the cylinder body 22 of the hydraulic cylinder, ensuring that the cylinder body 22 and the upper and lower cage plates 12 form a low-angular-stiffness cage system. The upper positioning ring 7 and the lower positioning ring 8 ensure the precise positioning of the upper cage plate 11 and the lower cage plate 12 with the cylinder body 22.

[0045] The system also includes a leak-proof sealing ring 24, a high-pressure resistant sliding sealing ring 25, and a high-pressure resistant fixed sealing ring 26. The inner diameter of the mounting port of the cylinder body 22 of the upper cage plate 11 is larger than the inner diameter of the cylinder body 22 of the hydraulic cylinder. An annular countersunk groove communicating with the inside of the cylinder body 22 is formed on the upper end surface of the hydraulic cylinder. The upper section of the leak-proof sealing ring 24 is inserted into the inner side of the upper cage plate 11, and the lower end of the leak-proof sealing ring 24 is inserted into the annular countersunk groove on the upper end surface of the cylinder body 22 of the hydraulic cylinder. The inner side of the leak-proof sealing ring 24 is in dynamic sealing contact with the outer circumference of the plunger 23 of the hydraulic cylinder. The high-pressure resistant sliding sealing ring 25 is fixedly sleeved on the outer circumference of the lower end of the plunger 23 of the hydraulic cylinder. The outer circumference of the high-pressure resistant sliding sealing ring 25 is in dynamic sealing contact with the inner side of the cylinder body 22 of the hydraulic cylinder. The high-pressure resistant fixed seal is fixedly installed on the cylinder bottom 21 of the hydraulic cylinder and can seal the connection between the cylinder bottom 21 and the cylinder body 22.

[0046] The high-pressure resistant sliding sealing ring 25 is a sliding seal and guiding system with gap compensation capability. It seals the high-pressure oil in the high-pressure oil area, acting on the cylinder bottom 21 to generate a pressure of 60,000 tons. When the high-pressure oil leaks, the oil reaches the leaking oil chamber, and its pressure drops to approximately zero MPa.

[0047] The anti-leakage sealing ring 24 is a low-pressure seal for leaking oil. The leaking oil will be transported back to the oil tank through the leaking oil pipe. Although the eccentric torque has a great impact on the sealing of the anti-leakage sealing ring 24, the possibility of leaking oil overflowing is very small because the oil pressure at that point is very low.

[0048] The high-pressure resistant fixed sealing ring 26 is a fixed seal with gap compensation capability. Since the cylinder bottom 21 and the lower cage plate 12 move almost synchronously, the sealing working conditions of the high-pressure resistant fixed sealing ring 26 are very good.

[0049] During loading, high-pressure oil enters the bottom high-pressure zone, and the pressure of the filling oil instantly rises to the rated pressure (e.g., 70 MPa), reaching tens of thousands of tons of rated pressure. Simultaneously, this pushes the cage system downwards, compressing the forgings and causing deformation. At this time, the high-pressure resistant sliding sealing ring 25 plays a crucial sealing role, preventing high-pressure oil from entering the low-pressure zone. This design ensures that the high-pressure resistant sliding sealing ring 25 does not bear the lateral thrust caused by off-center loading, greatly improving its working conditions. Of course, a very small amount of leaking oil (near zero pressure) will enter the low-pressure zone, which is then prevented from leaking out by the anti-leakage sealing ring 24 and discharged into the oil recovery system. The cage system design places the anti-leakage sealing ring 24 away from the bottom plate 14, at the upper cage plate 11 with a large displacement inclination. Therefore, it must withstand a certain lateral thrust (see...). Figure 4 and Figure 14 For F2), a strong guide pressure-bearing ring needs to be designed; on the other hand, the leak-proof sealing ring 24 only needs to seal unpressurized leaking oil, thereby greatly improving its sealing reliability. The function of the high-pressure resistant fixed sealing ring 26 is to prevent high-pressure leakage from the cylinder bottom 21, which is also a key seal. However, the synchronous movement of the cylinder barrel, cylinder bottom 21 and base plate 14 creates better working conditions for the high-pressure resistant fixed sealing ring 26: no influence of lateral thrust.

[0050] Using the aforementioned cage-type anti-eccentricity system, a sealing-guiding system was designed and manufactured for a 30,000-ton die forging hydraulic press. Extensive reliability engineering experiments were conducted, ultimately proving its reliability. The cage system of this invention, with its overall design theory and engineering specifications, is scientific and has been proven reliable and advanced through engineering application practice. It will undoubtedly have a profound impact on the development of various presses with small eccentric loads worldwide, especially new heavy-duty and ultra-heavy-duty die forging hydraulic presses.

[0051] The lower side of the upper cage plate 11 has a countersunk cylinder body 22 receiving groove that communicates with its inner ring. The upper end of the cylinder body 22 of the hydraulic cylinder is inserted into the cylinder body 22 receiving groove, and the outer side wall of the upper end of the hydraulic cylinder 22 stops against the inner side wall of the cylinder body 22 receiving groove. The cylinder body 22 receiving groove on the lower side of the upper cage plate 11 further limits the upper end of the hydraulic cylinder 22, improving the connection strength and positional accuracy between the upper end of the hydraulic cylinder 22 and the upper cage plate 11.

[0052] A buffer body 27 is fixedly installed on the upper surface of the cylinder bottom 21 of the hydraulic cylinder. After the lower end of the piston 23 of the hydraulic cylinder descends to the bottom, it contacts the buffer body 27 for buffering. The bottom plate 14, the lower cage plate 12, the cylinder bottom 21, and the buffer body 27 together form a force transmission structure, the total thickness of which exceeds the thickness of the upper cage plate 11. The buffer body 27, the lower cage plate 12, and the bottom plate 14 together form the foundation of the force transmission (load transmission) structure of the cage system. The hydraulic buffer body 27 is installed in the center of the cylinder bottom 21, which is also one of the force transmission components. When the hydraulic press moves downward during the idle stroke, the return cylinder overflows and discharges oil. The low-pressure filling oil enters the upper surface of the buffer body 27 from the oil pipe, pushing the cage system down a distance of several millimeters, thereby ensuring that the low-pressure filling oil enters the bottom high-pressure zone ( Figure 7 ).

[0053] The plunger 23 of the hydraulic cylinder has an oil passage 28 extending through it along its axial direction. An oil inlet pipe sealing ring 281 is provided at the upper opening of the oil passage 28, which can seal and connect the oil passage 28 with the oil inlet pipe. Hydraulic oil enters the oil passage 28 from the oil inlet pipe and continues to flow downward along the oil passage 28 into the hydraulic cylinder and into the bottom high-pressure zone.

[0054] The upper end of the plunger 23 of the hydraulic cylinder is connected to the upper beam 31 of the hydraulic press via a spherical annular self-aligning support structure 29 or a square annular self-aligning support structure 291. This invention allows the connection between the plunger 23 and the upper beam 31 to have moderate flexibility when the cage system is subjected to eccentric loads, ensuring that the angular and linear displacements of the plunger 23 and the upper beam 31 can differ moderately.

[0055] The upper cage plate 11, lower cage plate 12, and bottom plate 14 are all square plates. The left and right sides of the upper cage plate 11, lower cage plate 12, and bottom plate 14 are respectively stopped by the left column 32 and right column 33 of the hydraulic press. The front and rear edges of the inner sides of the left column 32 and right column 33 respectively form vertically extending chamfered slopes. Guide plates 34 are fixedly installed on the chamfered slopes of the left column 32 and right column 33. The guide surfaces 17 on the upper guide plates 34 and lower guide bodies 16 arranged along the front-back direction on both sides of the cage system form an X-shaped guide system for the cage system. The upper guide bodies 15 and lower guide bodies 16 are respectively installed on the upper cage plate 11 and lower cage plate 12. The guide surfaces 17 on the surfaces of the upper guide bodies 15 and lower guide bodies 16 of the cage system are paired with the guide plates 34 on the columns to bear eccentric loads and complete sliding guidance. The guide surfaces 17 of the upper guide body 15 and the lower guide body 16 located on the left and right sides of the cage system are both combined in an X-shape. Figure 15 This is to reduce the adverse effects of thermal expansion of the guidance system.

[0056] Both the upper and lower conductors are equipped with gap adjusters 18, which can adjust the tilt angle of the guide surfaces 17 of the upper and lower conductors and the distance between them and the guide plate 34, thereby adjusting the gap between the guide surfaces 17 of the upper guide body 15 and the lower guide body 16 and the upper guide plate 34 of the left column 32 and the right column 33. The upper and lower conductors have an L-shaped block structure, with V-shaped openings formed in the front and rear parts of the left and right sides of the upper cage plate 11, lower cage plate 12, and bottom plate 14. The upper conductor is accommodated in the V-shaped openings on the left and right side walls of the upper cage plate 11, and the lower conductor is accommodated in the V-shaped openings on the left and right sides of the superimposed structure of the lower cage plate 12 and the bottom plate 14. The horizontally extending sidewalls of the L-shaped block structure of the upper and lower conductors are flat against the upper surfaces of the upper cage plate 11 and the lower cage plate 12, respectively. The vertically extending sidewalls of the L-shaped block structure of the upper and lower conductors are flat against the left and right side walls of the upper cage plate 11 and the lower cage plate 12, respectively. The upper and lower conductors are mounted on the upper cage plate 11 and lower cage plate 12 respectively, which are able to rotate around the vertical axis and slide linearly along the side wall of the vertical V-shaped groove. The gap adjuster 18 is installed on the side wall of the upper and lower conductors extending vertically. The gap adjuster 18 drives the upper and lower conductors to slide or rotate in the V-shaped groove on the side wall of the upper cage plate 11 and lower cage plate 12, changing the gap between the guide surface 17 of the upper and lower conductors and the guide plate 34 on the left column 32 and right column 33. After adjustment, the upper and lower conductors can be locked.

[0057] The cage bolts 13 include a plurality of coarse cage bolts 131 and a plurality of fine cage bolts 132. The plurality of coarse cage bolts 131 are distributed at the four corners of the upper cage plate 11 and the lower cage plate 12; the plurality of fine cage bolts 132 are distributed on the front, rear, left and right sides of the hydraulic press. The upper cage plate 11 and the lower cage plate 12 are connected by the coarse and fine cage bolts 132. The coarse cage bolts 131 are distributed at the four corners of the cage plate; the fine cage bolts 132 are distributed on the front and sides of the hydraulic press to ensure the connection strength between the upper cage plate 11 and the lower cage plate 12.

Claims

1. A cage system for a hydraulic press, characterized in that: The system includes an upper cage plate (11), a lower cage plate (12), cage bolts (13), a bottom plate (14), an upper guide body (15), and a lower guide body (16). The lower cage plate is fixedly installed on the upper surface of the bottom plate. The upper cage plates are arranged parallel to each other above the lower cage plates. The upper and lower cage plates have coaxially facing cylinder mounting ports and cylinder bottom mounting ports, respectively. The upper and lower cage plates are fixedly connected together by a number of cage bolts arranged at intervals along the circumference of the cylinder mounting ports and cylinder bottom mounting ports. The upper cage plate, lower cage plate, bottom plate, and cage bolts form a cage-shaped structure. The hydraulic cylinder of the hydraulic press can be accommodated in the cage-shaped structure. The cylinder bottom (21) of the hydraulic press's oil cylinder can be inserted into the cylinder bottom mounting port of the lower cage plate and... The cylinder body (22) of the hydraulic press is fixedly installed on the base plate and can be fixedly inserted into the cylinder body mounting port of the upper cage plate. The plunger (23) of the hydraulic press cylinder can extend out of the upper outer side of the cage structure through the cylinder body mounting port and self-align with the upper beam (31) of the hydraulic press. The upper guide body is fixedly installed on the left and right sides of the upper cage plate, and the lower guide body is fixedly installed on the left and right sides of the fixed connection structure between the lower cage plate and the base plate. Vertically extending guide surfaces (17) are formed on both the upper and lower guide bodies. The guide surfaces on each upper and lower guide body can slide up and down along the guide plates (34) extending vertically on the left column (32) and right column (33) of the hydraulic press, respectively.

2. The cage system for a hydraulic press as described in claim 1, characterized in that: The lower end of the cylinder body of the hydraulic cylinder is tightly abutted against the upper side of the lower cage plate, and the upper end of the cylinder body of the hydraulic cylinder is tightly abutted against the lower side of the upper cage plate. The lower side of the upper cage plate and the upper end face of the cylinder body of the hydraulic cylinder are respectively provided with an upper embedded groove, and the upper side of the lower cage plate and the lower end face of the cylinder body of the hydraulic cylinder are respectively provided with a lower embedded groove. An upper positioning ring (7) and a lower positioning ring (8) are also provided. The upper and lower ends of the upper positioning ring are respectively inserted into the upper embedded grooves on the lower side of the upper cage plate and the upper end face of the cylinder body of the hydraulic cylinder, thereby achieving the stop positioning of the upper cage plate and the upper end face of the cylinder body of the hydraulic cylinder. The upper and lower ends of the lower positioning ring are respectively inserted into the lower end face of the cylinder body of the hydraulic cylinder and the lower embedded grooves on the upper side of the lower cage plate, thereby achieving the stop positioning of the lower cage plate and the lower end face of the cylinder body of the hydraulic cylinder.

3. The cage system for a hydraulic press as described in claim 1 or 2, characterized in that: It is also equipped with a leak-proof sealing ring (24), a high-pressure resistant sliding sealing ring (25), and a high-pressure resistant fixed sealing ring (26). The inner diameter of the cylinder mounting port of the upper cage plate is larger than the inner diameter of the cylinder of the hydraulic cylinder. An annular countersunk groove communicating with the inside of the cylinder is formed on the upper end surface of the cylinder of the hydraulic cylinder. The upper part of the leak-proof sealing ring is inserted into the inner side of the upper cage plate, and the lower part of the leak-proof sealing ring is inserted into the annular countersunk groove on the upper end surface of the cylinder of the hydraulic cylinder. The inner side of the leak-proof sealing ring is in dynamic sealing contact with the outer circumference of the plunger of the hydraulic cylinder. The high-pressure resistant sliding sealing ring is fixedly sleeved on the outer circumference of the lower end of the plunger of the hydraulic cylinder. The outer circumference of the high-pressure resistant sliding sealing ring is in dynamic sealing contact with the inner side of the cylinder of the hydraulic cylinder. The high-pressure resistant fixed seal is fixedly installed on the bottom of the hydraulic cylinder and can seal the connection between the bottom of the hydraulic cylinder and the cylinder body.

4. The cage system for a hydraulic press as described in claim 3, characterized in that: The lower side of the upper cage plate has a countersunk cylinder receiving groove that communicates with its inner ring. The upper end of the cylinder body of the hydraulic cylinder is inserted into the cylinder receiving groove, and the outer side wall of the upper end of the hydraulic cylinder is stopped on the inner side wall of the cylinder receiving groove.

5. The cage system for a hydraulic press as described in claim 1, characterized in that: A buffer body (27) is fixedly installed on the upper end face of the bottom of the hydraulic cylinder. After the lower end face of the piston of the hydraulic cylinder descends to the bottom, it contacts the buffer body for buffering. The bottom plate, the lower cage plate, the cylinder bottom and the buffer body together form a force transmission structure, and its total thickness exceeds the thickness of the upper cage plate.

6. The cage system for a hydraulic press as described in claim 1, characterized in that: The hydraulic cylinder has an oil passage (28) extending through it along its axial direction inside the plunger. An oil inlet pipe sealing ring (281) is provided at the upper opening of the oil passage. The oil inlet pipe sealing ring can seal and connect the oil passage with the oil inlet pipe.

7. The cage system for a hydraulic press as described in claim 1, characterized in that: The upper end of the plunger of the hydraulic cylinder is connected to the upper beam of the hydraulic press through a ball ring self-positioning support structure (29) or a square ring self-positioning support structure (291).

8. The cage system for a hydraulic press as described in claim 1, characterized in that: The upper cage plate, lower cage plate, and bottom plate are all square plates. The left and right sides of the upper cage plate, lower cage plate, and bottom plate are respectively stopped on the left and right columns of the hydraulic press. The front and rear edges of the inner sides of the left and right columns respectively form vertically extending chamfered slopes. The guide plates are fixedly installed on the chamfered slopes of the left and right columns. The guide surfaces on the upper guide plates and lower guide bodies arranged along the front-back direction on the left and right sides of the cage system form an X-shaped guide system for the cage system.

9. The cage system for a hydraulic press as described in claim 8, characterized in that: Both the upper and lower conductors are equipped with gap adjusters (18). The gap adjusters can adjust the tilt angle of the guide surfaces of the upper and lower conductors and the distance between them and the guide plates, thereby adjusting the gap between the upper guide surfaces of the upper and lower guide bodies and the upper guide plates of the left and right columns.

10. The cage system for a hydraulic press as described in claim 8, characterized in that: The cage bolts include several coarse cage bolts (131) and several fine cage bolts (132). The coarse cage bolts are distributed at the four corners of the upper and lower cage plates; the fine cage bolts are distributed on the front, back and left and right sides of the hydraulic press.

Images