A cubic press with back bending and a method for dynamically adjusting the position pressure of a top hammer

Abstract

The application discloses a back-bending type cubic press and a top hammer position pressure dynamic adjusting method, relates to the technical field of superhard material synthesis equipment, and comprises the following parts: two groups of end face racks; four groups of side face racks, which are matched with the two groups of end face racks and jointly form the overall rack structure of the back-bending type cubic press; a displacement sensor, which is arranged at the middle part of the outer side of the end face rack and the side face rack and is used for collecting displacement data of the end face rack, the side face rack and a hydraulic cylinder; the hydraulic cylinder, which is arranged at the middle part of the inner side of the end face rack and the side face rack and provides hydraulic power output for the pressing operation of the back-bending type cubic press; and a hinge beam shape correcting mechanism, which is arranged at the outer side of the side face rack and is used for correcting the deformation of the side hinge beam of the side face rack. The beam body in the application adopts a unique back-bending type structure design, and a method for real-time and collaborative dynamic adjustment of the top hammer position and the applied pressure during the pressing process is provided, so that the beam body is always in the optimal stress state.

Description

Technical Field

[0001] This invention relates to the field of equipment technology for the synthesis of superhard materials, and more specifically, to a back-bending six-sided top press and a method for dynamically adjusting the position and pressure of the top hammer. Background Technology

[0002] In the synthesis of superhard materials (such as synthetic diamond and cubic boron nitride) and high-end functional ceramics, the six-sided top press is the core equipment for creating a high-temperature and high-pressure synthesis environment. It forms a closed synthesis cavity by synchronously pressing the material towards the center through six axial top hammers. The uniformity and stability of pressure and temperature within the synthesis cavity directly determine the integrity of the crystal structure, the consistency of performance, and the production yield of the synthesized product; these are core control indicators in this field. Traditional six-sided top presses often adopt a hinged main structure, relying on a complex combination of multiple hinge pairs and beams to achieve synchronous force application in six directions. This structure has numerous hinge points. During long-term high-load cyclic operation, mechanical backlash easily develops at each hinge point due to factors such as processing errors and component wear, and it is difficult to maintain consistent backlash in all directions. This inconsistent mechanical backlash is directly transmitted to the six top hammers, causing them to fail to achieve precise alignment, thus creating an unavoidable off-center loading phenomenon within the synthesis cavity. Off-center loading not only causes pressure gradient distortion and uneven temperature field distribution in the synthesis chamber, leading to quality problems such as product lattice defects and uneven crystal growth, but also causes abnormal wear or even breakage of the top hammer, significantly reducing the service life of the top hammer and severely restricting the overall operating life and production economy of the six-sided top press.

[0003] Currently, the solutions to the aforementioned off-center loading problem are still limited to improving the static machining accuracy of parts and relying on manual debugging to complete the initial alignment of the equipment. These methods cannot monitor and actively compensate for the dynamic alignment deviation of the top hammer caused by factors such as thermal deformation, dynamic wear, and component fatigue during equipment operation. They are passive and lagging solutions. Due to the lack of an effective online monitoring and dynamic compensation mechanism, the off-center loading problem of the top hammer cannot be fundamentally corrected, becoming a key bottleneck restricting the improvement of machining accuracy and production efficiency of the six-sided top press.

[0004] In the prior art, patent CN202510596415.8 discloses a frame-type six-sided top press, which achieves six-way synchronous pressurization through a linkage mechanism, improving the pressure uniformity to a certain extent. However, the mechanical linkage structure of this solution is highly complex, and the pressurization accuracy is prone to decline due to component wear during long-term use. Patent CN108905898A discloses an arched bearing hinge beam and a six-sided top press. By extending the beam ears along the axial direction of the bearing body and forming an arched structure from the bearing surface to the pin hole, the tensile stress borne by the traditional hinge beam is converted into compressive stress, improving the bearing capacity and fatigue life of the individual pressure-bearing component. However, this solution only focuses on the improvement of the static mechanical structure to optimize the stress state of the component, without involving the real-time coordinated control of the six top hammers during the dynamic pressurization process. Furthermore, it still does not solve the problem of inconsistent mechanical clearance caused by too many hinge points, and cannot fundamentally solve the technical problem of dynamic eccentric loading of the top hammers.

[0005] No effective solutions have yet been proposed to address the problems in the relevant technologies. Summary of the Invention

[0006] (a) Technical problems to be solved To address the shortcomings of existing technologies, this invention provides a back-bending six-sided jacking press and a method for dynamically adjusting the position and pressure of the jacking hammer. It has the advantage of dynamically adjusting the position and pressure of the beam and jacking hammer in a back-bending six-sided jacking press, thereby solving the dynamic off-center load problem caused by inconsistent mechanical clearance in traditional hinged six-sided jacking presses.

[0007] (II) Technical Solution To achieve the advantages of dynamic adjustment of the beam and hammer position and pressure of the back-bend six-sided top press mentioned above, the specific technical solution adopted in this invention is as follows: According to one aspect of the present invention, a back-bending six-sided top press is provided, comprising: two sets of end face frames; four sets of side frames, which cooperate with the two sets of end face frames to jointly form the overall frame structure of the back-bending six-sided top press; displacement sensors, disposed at the middle of the outer side of the end face frames and the side frames, for collecting displacement data of the end face frames, the side frames and the hydraulic cylinders; hydraulic cylinders, disposed at the middle of the inner side of the end face frames and the side frames, for providing hydraulic power output for the pressurization operation of the back-bending six-sided top press; and a hinge beam straightening mechanism, disposed on the outer side of the side frames, for correcting the deformation of the side hinge beams of the side frames, ensuring the structural accuracy of the side frames and the structural stability of the entire frame.

[0008] According to another aspect of the present invention, a method for dynamically adjusting the position pressure of the top hammer of a back-bending six-sided top press is also provided, the method comprising: S1. Determine whether the pressurization process of the backbend type six-sided top press is the first run. If not, proceed to step S2; if yes, proceed to the initialization process. S2. Collect the actual pressure value and actual displacement value of all top hammers, calculate the average actual pressure of all top hammers based on the collected actual pressure value, and calculate the pressure deviation between the average actual pressure and the preset target pressure. S3. Based on the actual displacement values ​​collected, select the hammer with the smallest actual displacement value as the position reference, and calculate the position deviation of the remaining hammers relative to the position reference. S4. Based on the position deviation of each hammer, if the absolute value of the position deviation of any hammer is greater than the position synchronization tolerance, the pressure compensation amount of each hammer is calculated by the position sub-loop PID controller, and a pressure command is generated in combination with the leading or lagging state of the hammer; if the absolute value of the position deviation of all hammers is less than or equal to the position synchronization tolerance, the control amount is calculated by the pressure fine-tuning loop PID controller based on the pressure deviation of each hammer and a pressure command is generated. S5. Based on the generated pressure command, drive each hammer to perform the corresponding motion action. After the action is executed, perform detection. If the pressure deviation or position deviation of any hammer exceeds the preset safety threshold, proceed to step S7. If the pressure deviation and position deviation of all hammers do not exceed the preset safety threshold, return to step S2 to perform the next round of data acquisition and control, forming a closed-loop control process. S6. Continue to execute the closed-loop control process consisting of steps S2 to S5 until the pressurization time reaches the preset process setting value or the actual pressure value reaches the preset target final value, then stop the closed-loop control. S7. Save historical data of pressure, displacement, commands and alarms for all top hammers during the entire pressurization process.

[0009] (III) Beneficial Effects Compared with the prior art, the present invention provides a back-bending six-sided top press and a method for dynamically adjusting the position and pressure of the top hammer, which has the following beneficial effects: (1) The beam in this invention adopts a unique back-bending structure design, the core of which is to actively transform the destructive tensile stress borne by the traditional beam into compressive stress, thereby giving full play to the compressive strength potential of the material itself; based on this structural characteristic, this invention provides a method for real-time and coordinated dynamic adjustment of the position of the top hammer and the applied pressure during the pressurization process, so as to ensure that the beam is always in the optimal stress state.

[0010] (2) This invention effectively solves the inherent problems of fatigue cracking and low load-bearing efficiency of the beam body of the traditional six-sided top press due to stress concentration; by improving stress distribution, the fatigue life of the beam body is greatly extended, and the operational reliability and synthesis process stability of the press are improved; this invention provides a key equipment foundation for the efficient and long-life preparation of large cavity, high-performance superhard materials.

[0011] (3) The present invention ensures the extreme uniformity and stability of the pressure field and temperature field in the synthesis cavity, thereby significantly improving the crystal integrity, performance consistency and synthesis yield of superhard material synthesis products. Attached Figure Description

[0012] To more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the drawings used in the embodiments will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0013] Figure 1 This is a schematic diagram of the structure of a back-bending six-sided top press according to an embodiment of the present invention; Figure 2 This is a cross-sectional view of a back-bending six-sided top press according to an embodiment of the present invention; Figure 3 This is a partial structural diagram of the end face frame of the back-bending six-sided top press according to an embodiment of the present invention; Figure 4 This is a partial structural diagram of the lower end fixed seat in a back-bending six-sided top press according to an embodiment of the present invention; Figure 5 This is a partial structural diagram of the side frame in a back-bending six-sided top press according to an embodiment of the present invention; Figure 6 This is a partial structural schematic diagram of the hinge beam straightening mechanism in a back-bending six-sided top press according to an embodiment of the present invention; Figure 7 This is a partial structural diagram of the front fixed seat in a back-bending six-sided top press according to an embodiment of the present invention; Figure 8 yes Figure 7 A magnified view of a section at point A in the middle; Figure 9 This is a partial structural diagram of the rear fixed seat in a back-bending six-sided top press according to an embodiment of the present invention; Figure 10 yes Figure 9 A magnified view of a section at point B in the middle; Figure 11 This is a partial structural schematic diagram of the hydraulic cylinder in a back-bending six-sided top press according to an embodiment of the present invention; Figure 12 This is a cross-sectional view of the hydraulic cylinder in the back-bending six-sided top press according to an embodiment of the present invention; Figure 13 This is a flowchart of a method for dynamically adjusting the position and pressure of the top hammer in a back-bending six-sided top press according to an embodiment of the present invention.

[0014] In the picture: 1. End face frame; 101. Lower end fixed seat; 1011. Support base; 1012. Reinforcing block; 102. Upper end fixed seat; 103. End face hinge beam; 104. Pin shaft; 2. Side frame; 201. Front support block of side frame; 202. Rear support block of side frame; 203. Strain gauge; 204. Side hinge beam; 205. Screw mounting seat; 3. Displacement sensor; 4. Hydraulic cylinder; 401. Cylinder body; 402. Piston; 403, Guide sleeve; 404, Y-type seal ring; 405, Sealing ring; 406, O-ring seal ring; 407, Guide block; 408, Top seat; 409, Steel ring; 410, Top hammer; 5, Hinge beam straightening mechanism; 501, Front screw; 502, Front fixed seat; 5021, Front fixed seat base plate; 5022, First bearing mounting seat; 5023, Second bearing mounting seat; 5024, Third bearing mounting seat; 50 25. First bearing; 5026. First lead screw; 5027. First bevel gear; 5028. Second bevel gear; 5029. Second bearing; 50210. Second lead screw; 50211. Third bevel gear; 50212. Fourth bevel gear; 50213. Third bearing; 50214. Steering lead screw; 50215. Fifth bevel gear; 50216. First handwheel; 50217. Sixth bevel gear ; 503, Rear fixed seat; 5031, Rear fixed seat base plate; 5032, First worm gear bearing mounting seat; 5033, Second worm gear bearing mounting seat; 5034, Third worm gear bearing mounting seat; 5035, First worm gear bearing; 5036, Long worm; 5037, Second handwheel; 5038, Second worm gear bearing; 5039, Third worm gear bearing; 50310, Worm gear; 504, Upper screw; 505, Lower screw post. Detailed Implementation

[0015] To further illustrate the various embodiments, the present invention provides accompanying drawings, which are part of the disclosure of the present invention. These drawings are mainly used to illustrate the embodiments and can be used in conjunction with the relevant descriptions in the specification to explain the operating principles of the embodiments. With reference to these drawings, those skilled in the art should be able to understand other possible implementation methods and the advantages of the present invention. The components in the drawings are not drawn to scale, and similar component symbols are generally used to represent similar components.

[0016] According to an embodiment of the present invention, a back-bending six-sided top press and a method for dynamically adjusting the position and pressure of the top hammer are provided.

[0017] The present invention will now be further described in conjunction with the accompanying drawings and specific embodiments, such as... Figures 1-12As shown, the back-bending six-sided top press according to an embodiment of the present invention includes: two sets of end face frames 1; four sets of side frames 2, which cooperate with the two sets of end face frames 1 to jointly form the overall frame structure of the back-bending six-sided top press; displacement sensors 3, which are disposed at the middle of the outer side of the end face frames 1 and the side frames 2, for collecting displacement data of the end face frames 1, the side frames 2 and the hydraulic cylinders 4; hydraulic cylinders 4, which are disposed at the middle of the inner side of the end face frames 1 and the side frames 2, for providing hydraulic power output for the pressurization operation of the back-bending six-sided top press; and hinge beam straightening mechanism 5, which is disposed on the outer side of the side frames 2, for correcting the deformation of the side hinge beams 204 of the side frames 2, to ensure the structural accuracy of the side frames 2 and the structural stability of the entire frame.

[0018] In this optional embodiment, the end frame 1 includes a lower fixed seat 101 connected to the hydraulic cylinder 4. An upper fixed seat 102 is provided on the side of the lower fixed seat 101 away from the hydraulic cylinder 4. Several end hinge beams 103 are provided around the lower fixed seat 101 and the upper fixed seat 102. The end hinge beams 103 are connected to each other by a pin 104. The lower fixed seat 101 includes a support base 1011 connected to the hydraulic cylinder 4. Several reinforcing blocks 1012 are provided on the side of the support base 1011 near the upper fixed seat 102, thereby improving the overall structural rigidity and load-bearing capacity.

[0019] It should be further explained that the end face hinge beam 103 is uniformly forged, with a groove in the middle. After being arranged in a horizontal and vertical combination, it is installed between the upper fixed seat 102 and the lower fixed seat 101. The upper fixed seat 102 and the lower fixed seat 101 are connected by bolts. In order to strengthen the end face hinge beam 103, the lower fixed seat 101 is composed of a reinforcing block 1012 and a support base 1011. The reinforcing block 1012 and the support base 1011 are connected by welding. The reinforcing block 1012 is arranged in the gap where the end face hinge beams 103 intersect.

[0020] In this optional embodiment, the side frame 2 includes a front support block 201 connected to the hydraulic cylinder 4. A rear support block 202 is symmetrically arranged on the side of the front support block 201 away from the hydraulic cylinder 4. Several strain gauges 203 are arranged in the middle of the side of the front support block 201 away from the hydraulic cylinder 4. Several side hinge beams 204 are provided at the top and bottom of the front support block 201 and the rear support block 202. The side hinge beams 204 cooperate with the pins 104. The side hinge beams 204 and the end face hinge beams 103 are staggered. A screw mounting seat 205 is provided at the bottom and top of the side hinge beams 204, thereby ensuring the structural stability and operational monitorability of the side frame 2.

[0021] It should be further explained that the side hinge beam 204 is connected by the pin 104, and the side hinge beam 204 is connected to the screw mounting seat 205 by bolts. Strain gauges 203 are installed on the outside of the side hinge beam 204 to collect the deformation of the side hinge beam 204. After the side hinge beam 204 and the pin 104 are engaged, they are installed between the rear support block 202 and the front support block 201 of the side frame. The rear support block 202 and the front support block 201 of the side frame are fixedly connected by bolts.

[0022] In this optional embodiment, the hydraulic cylinder 4 includes a cylinder body 401 disposed in the middle of the inner side of the end frame 1 and the side frame 2. A piston 402 is disposed inside the cylinder body 401. The piston 402 and the cylinder body 401 are engaged by a guide sleeve 403. A Y-type sealing ring 404, a sealing ring 405 and an O-type sealing ring 406 are sequentially disposed between the piston 402 and the cylinder body 401. A guide block 407 is disposed on one side of the guide sleeve 403. A top seat 408 is disposed on one side of the piston 402. A steel ring 409 is disposed on one side of the top seat 408. A top hammer 410 is disposed on one side of the steel ring 409, thereby ensuring the accuracy, sealing and structural stability of the hydraulic cylinder 4 during pressurization.

[0023] It should be further explained that, through interference fit, the steel ring 409 applies a certain radial preload to the top hammer 410. At the same time, the steel ring 409 is provided with threaded holes, and the reliability of the overall connection is improved by the set screw. The steel ring 409 is fitted on the outside of the adjustment groove at the front end of the top seat 408. Four sets of bolts are threaded at equal intervals on the outside of the steel ring 409. One end of these bolts is tightened against the adjustment groove, so that the steel ring 409 and the top seat 408 are relatively fixed. The cylinder body 401 serves as the main body of the hydraulic cylinder 4. The end of the cylinder body 401 is equipped with a guide sleeve 403. The inner diameter of the guide sleeve 403 matches the piston 402 to guide the reciprocating motion of the piston. The piston 402 is located inside the cylinder body 401. The O-ring seal 406, Y-ring seal 404, and sealing ring 405 are installed in the groove of the piston 402 and fit against the cylinder body 401 to form a seal.

[0024] In this optional embodiment, the hinge beam straightening mechanism 5 includes a front screw 501 disposed on one side of the side frame rear support block 202. A front fixed seat 502 and a rear fixed seat 503 are sequentially disposed on the side of the front screw 501 away from the side frame rear support block 202. An upper screw 504 and a lower screw post 505 are passed through the middle of the front fixed seat 502 and the rear fixed seat 503. The front fixed seat 502 includes a front fixed seat base plate 5021 that passes through the front screw 501. A plurality of first bearing mounting seats 5022, second bearing mounting seats 5023, and third bearing mounting seats 5024 are disposed on one side of the front fixed seat base plate 5021. A first bearing 5025 is disposed inside the first bearing mounting seat 5022. A first lead screw 5026 is provided through the bearing housing 5023. A first bevel gear 5027 is provided at both ends of the first lead screw 5026, and a second bevel gear 5028 is provided on one side of the first lead screw 5026. A second bearing 5029 is provided inside the second bearing mounting base 5023. A second lead screw 50210 is provided through the second bearing 5029. A third bevel gear 50211, meshing with the second bevel gear 5028, is provided at one end of the second lead screw 50210, and a fourth bevel gear 50212 is provided at the other end of the second lead screw 50210. A third bearing 50213 is provided inside the third bearing mounting base 5024. A steering lead screw 50214 is provided through the third bearing 50213. One end of the lead screw 50214 is provided with a fifth bevel gear 50215 that meshes with the fourth bevel gear 50212, and the other end of the steering lead screw 50214 is provided with a first handwheel 50216; each of the four corners of the front fixed base plate 5021 is provided with a sixth bevel gear 50217 that meshes with the first bevel gear 5027, and the sixth bevel gear 50217 is sleeved on the outside of the front screw 501; the rear fixed base 503 includes a rear fixed base plate 5031 provided on one side of the front screw 501, and one side of the rear fixed base plate 5031 is provided with a plurality of first worm gear bearing mounting seats 5032, second worm gear bearing mounting seats 5033 and third worm gear bearing mounting seats 5034, the interior of the first worm gear bearing mounting seat 5032 is provided with A first worm gear bearing 5035 is provided, and a long worm 5036 is installed through the interior of the first worm gear bearing 5035. A second handwheel 5037 is provided at one end of the long worm 5036. A second worm gear bearing 5038 that mates with the upper screw 504 is provided inside the second worm gear bearing mounting seat 5033. A third worm gear bearing 5039 that mates with the lower screw column 505 is provided inside the third worm gear bearing mounting seat 5034. The second worm gear bearing 5038 and the third worm gear bearing 5039, located in the middle of the rear fixed base plate 5031, are connected by a worm wheel 50310, and the worm wheel 50310 meshes with the long worm 5036, thereby effectively correcting the deformation of the hinge beam and ensuring the overall structural accuracy and operational stability of the frame.

[0025] It should be further explained that the bearing mounting base is connected to the front fixed base plate 5021 by bolts. The front fixed base plate 5021 has holes for installing the sixth bevel gear 50217 of the front screw 501. The sixth bevel gear 50217, which mates with the front fixed base plate 5021, has a spiral structure inside and is connected to the front screw 501. The sixth bevel gear 50217 mates with the bearing mounting base via a bearing. The first lead screw 5026, the second lead screw 50210, and the steering lead screw 50214 are fixed to the bevel gear by set screws or welding. At the same time, the steering lead screw 50214 is fixed to the first handwheel 50216 by a pin connection. By rotating the first handwheel 50216, the front screw 501 can be moved back and forth. The rear fixed base plate 5031 is connected to the worm gear bearing mounting seat by bolts. The worm gear bearing mounting seat cooperates with the worm gear bearing. The long worm 5036 is connected to the first worm gear bearing mounting seat 5032 through the first worm gear bearing 5035. The end of the long worm 5036 is fixed to the second handwheel 5037 by a pin. At the same time, the long worm 5036 cooperates with the worm gear 50310. The worm gear 50310 is assembled on the second worm gear bearing mounting seat 5033 and the third worm gear bearing mounting seat 5034 through the second worm gear bearing 5038 and the third worm gear bearing 5039. The threads on both sides of the worm gear 50310 rotate in opposite directions. By rotating the second handwheel 5037, the upper screw 504 and the lower screw column 505 can be moved in opposite directions.

[0026] like Figure 13 As shown, according to another embodiment of the present invention, a method for dynamically adjusting the position pressure of the top hammer of a back-bending six-sided top press is also provided, the method comprising: S1. Determine whether the pressurization process of the backbend type six-sided top press is the first run. If not, proceed to step S2; if yes, proceed to the initialization process.

[0027] It should be noted that the system first determines whether the current pressurization process is the first run; if it is the first run, it enters the initialization process; if it is not the first run (for example, after being suspended due to a fault and then resumed or after multiple rounds of synthesis), it skips the initialization process and directly enters the starting step S2 of the real-time control loop.

[0028] In this optional embodiment, the initialization process includes: setting the target pressure-time curve, the target displacement-time curve, and control parameters according to process requirements. The control parameters include position synchronization tolerance, pressure deviation tolerance, and initial parameters of each PID controller. Based on the setting results, zero-point calibration is performed on all displacement sensors 3 and preset pressure sensors. Micro-strain values ​​obtained by each strain gauge 203 are collected, and the micro-strain values ​​are converted into deformation. The corresponding range is calculated. If the range is less than or equal to the maximum range, step S2 is executed. If the range is greater than the maximum range, an alarm is issued and the corresponding handwheel is adjusted. The range is continuously monitored until the range is less than or equal to the maximum range, and then step S2 is executed.

[0029] It should be added that, according to the process requirements of the material to be synthesized, the target pressure-time curve (PT curve) and the target displacement-time curve (ST curve) are set; and the key parameters required for the adjustment process are set: (1) Position synchronization tolerance. : The maximum allowable displacement deviation threshold between each hammer; exceeding this value will trigger position synchronization compensation; (2) Pressure deviation tolerance : The maximum allowable deviation threshold between the actual pressure of a single top hammer and the target pressure; (3) Beam deformation consistency tolerance (4) PID controller parameters: Set the initial proportional coefficient, integral time, and derivative time for the PID controllers of the pressure main loop, position secondary loop, and pressure fine-tuning loop respectively; including the PID1 coefficient of the pressure main loop: the proportional coefficient of the pressure main loop. Pressure main loop integral time Pressure main ring differential time Position subloop PID2 coefficient: Position subloop proportional coefficient Location secondary loop integration time Position secondary loop differential time ; PID3 coefficient of pressure fine-tuning loop: proportional coefficient of pressure fine-tuning loop Pressure fine-tuning loop integral time Position secondary loop differential time The system controls all top hammers to contact the reference surface with a small force. In this state, the displacement sensor readings of all top hammers are zeroed, and the pressure sensor readings are calibrated to the preset initial contact force value. Zero-point calibration is performed on the pressure and displacement sensors of all top hammers, and a hinge beam deformation consistency check and manual calibration are executed. The system first completes the calibration of each sensor; then, it reads the micro-strain values ​​measured by the strain gauges of each hinge beam. And convert it into shape variables Calculate its range ;like Then proceed to step S2; if The system will issue an alarm prompt: "Inconsistent hinge beam deformation, please manually adjust." The operator will then manually adjust the corresponding adjustment mechanism (handwheel) based on the data displayed. The system will continue monitoring until... After the operator confirms, the process proceeds to S2.

[0030] S2. Collect the actual pressure value and actual displacement value of all top hammers 410, calculate the average actual pressure of all top hammers 410 based on the collected actual pressure value, and calculate the pressure deviation between the average actual pressure and the preset target pressure.

[0031] It should be noted that in each control cycle, the system synchronously reads six top hammers (indexes). Real-time data: Current actual pressure values ​​of all top hammers. Compared with actual displacement value Meanwhile, according to the current time Obtain the target pressure value from the preset curve. Target displacement reference value: Calculate the pressure deviation between the average pressure of all top hammers at the current moment and the target pressure, and use this as the input to the main pressure loop; the overall pressure deviation... The calculation is as follows: In the formula, For total pressure deviation, For target pressure, This represents the current actual pressure value of each top hammer.

[0032] S3. Based on the actual displacement value collected, select the top hammer 410 with the smallest actual displacement value as the position reference, and calculate the position deviation of the remaining top hammers 410 relative to the position reference.

[0033] It should be noted that the actual displacement values ​​of all the top hammers were compared. The hammer with the smallest actual displacement (i.e., the hammer that advances the slowest) is determined as the position synchronization reference for the current cycle, and its displacement is denoted as . For each top hammer Calculate the displacement difference between it and the position reference: ;like This indicates that the hammer is lagging behind; if If , it means that the top hammer is ahead.

[0034] S4. Based on the position deviation of each top hammer 410, if the absolute value of the position deviation of any top hammer 410 is greater than the position synchronization tolerance, the pressure compensation amount of each top hammer is calculated by the position sub-loop PID controller, and a pressure command is generated in combination with the leading or lagging state of the top hammer 410; if the absolute value of the position deviation of all top hammers 410 is less than or equal to the position synchronization tolerance, the control amount is calculated by the pressure fine-tuning loop PID controller based on the pressure deviation of each top hammer 410 and a pressure command is generated.

[0035] It should be further explained that, based on the positional deviation of each of the six top hammers... Parallel calculation of the pressure control commands for each of the six top hammers. : 1. (Pressure main loop output calculation) Calculate the overall pressure deviation. The input is fed to the main pressure loop PID controller (PID1) to calculate the reference pressure adjustment amount used to drive the overall pressure to approach the target. ,Right now: The discrete positional calculation formula for PID1 is: In the formula, , , For discrete-time indexing, These are the proportional, derivative, and integral coefficients of the pressure main loop controller, respectively. For integration time, The sampling period; For the first The output value of the main pressure loop in each control cycle, i.e., the reference pressure adjustment amount. For the first Overall pressure deviation for each control cycle; This is a discrete-time index, representing the current index as the [number]th [time]. One control cycle; The index in the summation operation represents the value from the initial time ( ) to the current time ( All historical cycles of ).

[0036] 2. For each top hammer Judgment and calculation: (1) When the position deviation exceeds the limit (strong synchronization is required), that is: hour: Position deviation Input position secondary loop PID controller (PID2) to calculate the pressure compensation amount used to correct position deviation. Since position synchronization requires a fast response and avoids integral saturation, an incremental PID controller is used. ; In the formula, , , These are the proportional, derivative, and integral coefficients of the position secondary loop PID controller. For integration time, The sampling period is specified; the final pressure command is generated. If the hammer strikes ahead, take -; if the hammer strikes lag behind, take +. For the first The first control cycle, the... The increment of the compensation amount at the position of the top hammer; For the first The first control cycle, the... The absolute value of the compensation amount for the position of the top hammer; For the first The first control cycle, the... The positional deviation of the top hammer.

[0037] (2) When the positional deviation is within the tolerance (requiring fine pressure adjustment), that is: hour: The synchronization between the top hammers is good, but the individual pressure accuracy needs to be adjusted carefully; calculate the individual pressure deviation of this top hammer: ,Will Input pressure fine-tuning loop PID controller (PID3) to calculate fine pressure fine-tuning amount. The calculation is as follows: In the formula, , , For discrete-time indexing, These are the proportional, derivative, and integral coefficients of the pressure fine-tuning loop controller, respectively. For integration time, The sampling period is defined as follows; and the final pressure command is generated as follows. ; For the first The first control cycle, the... The pressure adjustment amount of the top hammer; For the first The first control cycle, the... Individual pressure deviation of each top hammer; For the final message sent to the Pressure control commands for the top hammer electro-hydraulic servo valve; This serves as the common reference pressure for the main pressure ring, ensuring the overall pressure trend is correct.

[0038] S5. Based on the generated pressure command, drive each top hammer 410 to perform the corresponding movement action. After the action is executed, perform detection. If the pressure deviation or position deviation of any top hammer 410 exceeds the preset safety threshold, then execute step S7. If the pressure deviation and position deviation of all top hammers 410 do not exceed the preset safety threshold, then return to step S2 to execute the next round of data acquisition and control, forming a closed-loop control process.

[0039] It should be noted that the six pressure commands calculated will be... The signals are sent to the corresponding high-response electro-hydraulic servo valves of the hammers. The servo valves adjust the hydraulic oil flow and direction according to the electrical signals, thereby precisely controlling the output force of the corresponding hammer cylinders and driving the hammers to move according to the commands. Before the end of each cycle, safety monitoring is performed to check whether any hammer meets the following requirements: (Pressure exceeded limit) or (Position deviation exceeds the safety threshold, among which) Greater than If an anomaly is detected, the normal cycle is immediately interrupted and the process jumps to emergency handling step S7. If everything is normal, the process returns to step S2 and begins the acquisition and adjustment of the next control cycle, forming a real-time closed-loop control.

[0040] S6. Continue executing the closed-loop control process consisting of steps S2 to S5 until the pressurization time reaches the preset process setting value or the actual pressure value reaches the preset target final value, then stop the closed-loop control.

[0041] It should be noted that when the pressurization time reaches the process set value or the pressure reaches the target final value, it signifies that the pressurization process has ended normally as planned; subsequently, the process enters S7.

[0042] S7. Save historical data of pressure, displacement, commands and alarms corresponding to all top hammers 410 during the entire pressurization process.

[0043] It should be noted that regardless of whether the process ends normally or is abnormally interrupted, the system will record all timestamps from the entire pressurization process during this round. , , Data such as alarm signs are completely saved to the historical database for process analysis, quality traceability and controller parameter optimization.

[0044] like Figure 13 As shown, a method for dynamically adjusting the position and pressure of the top hammer in a back-bending six-sided top press specifically includes: Step 1: If this is the first run of the pressurization process, proceed to Step 2; otherwise, proceed directly to Step 5.

[0045] Step 2: Set the target pressure-time curve according to the process requirements. (curve) and target displacement-time curve ( curve).

[0046] Step 3: Set control parameters, including position synchronization tolerance. Pressure deviation tolerance and the initial parameters of each PID controller.

[0047] Step 4: Perform zero-point calibration on all pressure and displacement sensors 3 of the top hammer, and perform hinge beam deformation consistency check and manual calibration: The system first completes the calibration of each sensor; then, it reads the micro-strain values ​​measured by the strain gauges of each hinge beam. And convert it into shape variables Calculate its range ;like Then proceed to step 5; if The system will issue an alarm prompt: "Inconsistent hinge beam deformation, please manually adjust." The operator will then manually adjust the corresponding adjustment mechanism (handwheel) based on the data displayed. The system will continue monitoring until... After the operator confirms, the process proceeds to step 5.

[0048] Step 5: The system reads the current actual pressure value of all top hammers. Compared with actual displacement value .

[0049] Step 6: Calculate the average actual pressure and target pressure at the current moment. pressure deviation .

[0050] Step 7: Select the hammer with the smallest displacement value as the position reference, and calculate the positional deviation of the remaining hammers from this reference. This requires comparing the actual displacement values ​​of all the top hammers. The hammer with the smallest displacement value (i.e., the hammer that advances the slowest) is determined as the position synchronization reference for the current cycle, and its displacement is denoted as . For each top hammer Calculate the displacement difference between it and the position reference: ;like This indicates that the hammer is lagging behind; if If , it means that the top hammer is ahead.

[0051] Step 8: Perform dynamic adjustment calculations: Read the current position deviation of each top hammer. If the hammer is arbitrarily topped Then, the pressure compensation amount of each top hammer is calculated through the position subloop PID. And based on whether it is ahead or behind, according to Generate pressure command; if all top hammers Then, based on the individual pressure deviation of each top hammer... The fine-tuning amount is calculated by PID control through the pressure fine-tuning loop. , and according to Generate pressure commands; this requires considering the positional deviations of the six top hammers. Calculate the pressure control commands for each of the six top hammers. .

[0052] Step 9: Calculate the pressure command. The output is sent to the electro-hydraulic servo valve corresponding to each top hammer to drive the top hammer to move.

[0053] Step 10: Real-time monitoring and judgment: If any hammer pressure exceeds the limit or position deviation exceeds the safety threshold, immediately jump to step 12; otherwise, return to step 5 to carry out the next round of data collection and adjustment to form a closed loop.

[0054] Step 11: Continue executing the closed loop consisting of steps 5 to 10 until the pressurization time reaches the process set value or the pressure reaches the target final value; then, the process proceeds to step 12.

[0055] Step 12: Save all historical data of top hammer pressure, displacement, commands and alarms throughout the entire pressurization process.

[0056] This invention uses a six-sided top press for synthesizing high-quality diamonds as an example to explain in detail the implementation process of the dynamic adjustment method; the press has a nominal thrust of 40MN per cylinder and is equipped with a high-precision pressure sensor (accuracy...). ) and a magnetic grating displacement sensor (resolution 0.001mm) to control the sampling period of the system. The specific steps are as follows: I. System Initialization and Preparation Phase: 1. Process curve setting: (1) Target pressure curve (PT): linearly rises from 0MPa to 5.5GPa within 300s, holds pressure for 600s and then releases pressure; (2) Target displacement curve (ST): preset synchronous displacement trajectory according to the compression characteristics of pyrophyllite pressure transmission medium.

[0057] 2. Parameter settings: (1) Position synchronization tolerance (2) Pressure deviation tolerance (3) Tolerance for uniformity of beam deformation (4) The PID parameters use optimized preset values: , , ; , , ; , , .

[0058] 3. Sensor Calibration and Structural Adjustment: The system controls six top hammers to lightly touch the reference surface for alignment. The system automatically resets all displacement sensor readings to zero and calibrates the pressure sensor readings to the preset initial contact force. Subsequently, the system reads strain gauge data from key locations on each hinge beam to obtain micro-strain values. ,because If the hinge beam deformation is consistent, the system will directly enter the dynamic adjustment cycle; otherwise, it will prompt for manual adjustment (by rotating the handwheel).

[0059] II. Dynamic Adjustment Stage During Pressurization: 1. Scenario 1: During the middle of pressurization, slight positional asynchrony occurs. ): Data collection: (1) Actual pressure: (2) Actual displacement: Overall pressure deviation calculate: Positional deviation ( Calculation: Position reference (Top Hammer 3 is the slowest), according to Calculate the positional deviation of each hammer, and obtain .

[0060] Multimodal dynamic adjustment calculation: (1) Calculation of pressure main ring: , , , Substituting into the PID1 formula, the reference pressure adjustment amount is obtained. : ; (2) Judge and calculate each top hammer: ① For the #4 top hammer: Enter strong location synchronization mode; , , Substitute into PID2: ;get Generate the final instruction (lookahead -): ② Other jacks (1#, 2#, 3#, 5#, 6#): Enter the fine-tuning pressure mode. , , Substitute into PID3: ;get: , , , , The final pressure command calculated is as follows: , , , , .

[0061] Command execution and monitoring: The system will execute six The command is sent to the corresponding electro-hydraulic servo valve; the monitoring in the next control cycle shows that the displacement speed of top hammer 4 slows down due to the decrease in command pressure, while the other top hammers undergo fine pressure adjustment; after several cycles, the position deviation of all top hammers converges to within 0.03mm, and the system automatically switches back to the full pressure fine-tuning mode.

[0062] 2. Scenario 2: Pressure holding stage, high-precision pressure uniform control ( At this point, the system is in a steady state and the position is well synchronized. All top hammers are in fine pressure adjustment mode (PID3 operation); individual pressure deviation: PID3, through its proportional and integral actions ( Output the corresponding Gentle and slow compensation is applied; eventually, the pressure of each hammer stabilizes at... Within the range, the pressure field is highly uniform.

[0063] 3. Scenario 3: Abnormal Disturbance Simulation and System Protection (Assuming Instantaneous Increase in Friction of Top Hammer 3 Sealing Ring): If At that time, the system detected that the displacement growth rate of the top hammer 3 dropped sharply by 80%. Stagnation; its positional deviation Within three control cycles, the value rapidly increased from +0.01mm to +0.08mm. The system immediately activated the strong synchronization mode for the trigger position of the top hammer 3. PID2, based on a larger value... Quickly calculate the compensation pressure , The pressure is significantly increased (e.g., by 0.25 GPa) to overcome the increased frictional resistance; simultaneously, the main pressure ring (PID1) and the pressure fine-tuning rings (PID3) of the other top hammers work together to slightly reduce the pressure on the other top hammers to maintain the stability of the overall cavity pressure; after about 12 seconds, the displacement of top hammer 3 catches up. Once the pressure returns to within 0.03mm, the system automatically switches its control mode back to the fine pressure adjustment mode.

[0064] III. Process Data Recording: After the entire pressurization process is completed, the system automatically saves a complete data packet containing timestamps, including: all top hammer data. , , 1kHz sampled data, calculated in real time , , Values, real-time output values ​​of each PID controller (PID1, PID2, PID3), and hinge beam deformation ( The data includes all alarm events; the process data is shown in Table 1.

[0065] Table 1 Process Data Sheet To fully demonstrate the significant advancements of the dynamic adjustment method for top hammer position and pressure described in this invention compared to existing technologies, a comparative analysis is conducted below based on simulation experiments from multiple key performance dimensions (based on a Φ650mm cylinder diameter six-sided top press, with a target pressure of 5.5GPa); as shown in Table 2.

[0066] Table 2 Comparison of Core Control Performance This invention achieves real-time strong synchronization control by introducing a position sub-loop (PID2), improving the mechanical synchronization accuracy between the top hammers by more than 50%, fundamentally reducing the geometric distortion of the cavity caused by position asynchrony. Employing a collaborative control strategy of a pressure main loop (PID1) and a pressure fine-tuning loop (PID3), it achieves a leap from overall pressure tracking to fine and uniform force output of each top hammer, significantly improving the consistency of the pressure field. The system possesses multi-modal adaptive adjustment capabilities, capable of identifying position or pressure changes within milliseconds and automatically switching to the corresponding control mode (such as the strong position synchronization mode), thereby greatly enhancing anti-interference capabilities and system self-recovery performance. Furthermore, this dynamic adjustment method, combined with the arched beam structure, transforms the beam stress from tensile stress to compressive stress, while real-time load balancing avoids local overload, significantly extending the service life of key structural components such as the hinge beam and top hammers.

[0067] In this invention, unless otherwise explicitly specified and limited, the terms "installation," "setting," "connection," "fixing," "screw connection," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal connection of two components or the interaction between two components. Unless otherwise explicitly limited, those skilled in the art can understand the specific meaning of the above terms in this invention according to the specific circumstances.

[0068] The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of the present invention should be included within the protection scope of the present invention.

Claims

1. A back-bending type six-sided top press, characterized in that, include: Two sets of end face frames (1); Four sets of side frames (2) cooperate with two sets of end frames (1) to form the overall frame structure of the back-bending six-sided top press. The displacement sensor (3) is located at the middle of the outer side of the end frame (1) and the side frame (2) to collect displacement data of the end frame (1), the side frame (2) and the hydraulic cylinder (4); Hydraulic cylinder (4) is located in the middle of the inner side of the end frame (1) and the side frame (2) to provide hydraulic power output for the pressurization operation of the back bending six-sided top press. The hinge beam straightening mechanism (5) is located on the outside of the side frame (2) and is used to correct the deformation of the side hinge beam (204) of the side frame (2) to ensure the structural accuracy of the side frame (2) and the structural stability of the whole frame.

2. The back-bending six-sided top press according to claim 1, characterized in that, The end face frame (1) includes a lower end fixed seat (101) connected to the hydraulic cylinder (4). An upper end fixed seat (102) is provided on the side of the lower end fixed seat (101) away from the hydraulic cylinder (4). Several end face hinge beams (103) are provided around the lower end fixed seat (101) and the upper end fixed seat (102). The end face hinge beams (103) are connected to each other by pins (104).

3. A back-bending six-sided top press according to claim 2, characterized in that, The lower end fixing seat (101) includes a support base (1011) connected to the hydraulic cylinder (4), and the support base (1011) has a plurality of reinforcing blocks (1012) on the side near the upper end fixing seat (102).

4. A back-bending six-sided top press according to claim 3, characterized in that, The side frame (2) includes a front support block (201) connected to the hydraulic cylinder (4). A rear support block (202) is symmetrically arranged on the side of the front support block (201) away from the hydraulic cylinder (4). Several strain gauges (203) are arranged in the middle of the side of the front support block (201) away from the hydraulic cylinder (4). The front support block (201) of the side frame and the rear support block (202) of the side frame are provided with a number of side hinge beams (204) at their top and bottom ends, and the side hinge beams (204) cooperate with the pin (104). The side hinge beams (204) and the end face hinge beams (103) are staggered. The bottom and top ends of the side hinge beams (204) are provided with screw mounting seats (205).

5. A back-bending six-sided top press according to claim 1, characterized in that, The hydraulic cylinder (4) includes a cylinder body (401) disposed in the middle of the inner side of the end frame (1) and the side frame (2). A piston (402) is disposed inside the cylinder body (401). The piston (402) and the cylinder body (401) are engaged by a guide sleeve (403). A Y-type sealing ring (404), a sealing ring (405) and an O-type sealing ring (406) are disposed sequentially between the piston (402) and the cylinder body (401). A guide block (407) is disposed on one side of the guide sleeve (403). A top seat (408) is provided on one side of the piston (402), a steel ring (409) is provided on one side of the top seat (408), and a top hammer (410) is provided on one side of the steel ring (409).

6. A back-bending six-sided top press according to claim 4, characterized in that, The hinge beam straightening mechanism (5) includes a front screw (501) disposed on one side of the rear support block (202) of the side frame. A front fixed seat (502) and a rear fixed seat (503) are sequentially disposed on the side of the front screw (501) away from the rear support block (202) of the side frame. An upper screw (504) and a lower screw column (505) are disposed through the middle of the front fixed seat (502) and the rear fixed seat (503).

7. A back-bending six-sided top press according to claim 6, characterized in that, The front fixing seat (502) includes a front fixing seat base plate (5021) that passes through the front screw (501). A plurality of first bearing mounting seats (5022), second bearing mounting seats (5023) and third bearing mounting seats (5024) are provided on one side of the front fixing seat base plate (5021). A first bearing (5025) is provided inside the first bearing mounting seat (5022). A first lead screw (5026) passes through the first bearing (5025). A first bevel gear (5027) is provided at both ends of the first lead screw (5026). A second bevel gear (5028) is provided on one side of the first lead screw (5026). The second bearing mounting base (5023) is provided with a second bearing (5029) inside, and a second lead screw (50210) is provided through the second bearing (5029). One end of the second lead screw (50210) is provided with a third bevel gear (50211) that meshes with the second bevel gear (5028), and the other end of the second lead screw (50210) is provided with a fourth bevel gear (50212). The third bearing mounting base (5024) is provided with a third bearing (50213) inside, and a steering screw (50214) is provided through the third bearing (50213). One end of the steering screw (50214) is provided with a fifth bevel gear (50215) that meshes with the fourth bevel gear (50212), and the other end of the steering screw (50214) is provided with a first handwheel (50216). The four corners of the front fixed base plate (5021) are provided with a sixth bevel gear (50217) that meshes with the first bevel gear (5027), and the sixth bevel gear (50217) is sleeved on the outside of the front screw (501).

8. A back-bending six-sided top press according to claim 7, characterized in that, The rear fixing seat (503) includes a rear fixing seat base plate (5031) disposed on one side of the front screw (501). A plurality of first worm gear bearing mounting seats (5032), second worm gear bearing mounting seats (5033) and third worm gear bearing mounting seats (5034) are disposed on one side of the rear fixing seat base plate (5031). A first worm gear bearing (5035) is disposed inside the first worm gear bearing mounting seat (5032). A long worm (5036) is disposed through the first worm gear bearing (5035). A second handwheel (5037) is disposed at one end of the long worm (5036). The second worm gear bearing mounting base (5033) is provided with a second worm gear bearing (5038) that cooperates with the upper screw (504). The third worm gear bearing mounting base (5034) is provided with a third worm gear bearing (5039) that cooperates with the lower screw (505). The second worm gear bearing (5038) and the third worm gear bearing (5039) located in the middle of the rear fixed base plate (5031) are connected by a worm wheel (50310), and the worm wheel (50310) meshes with the long worm (5036).

9. A method for dynamically adjusting the position pressure of the top hammer in a back-bending six-sided jacking press, used to achieve dynamic adjustment of the position pressure of the top hammer in a back-bending six-sided jacking press as described in claims 1-8, characterized in that, The method includes: S1. Determine whether the pressurization process of the backbend type six-sided top press is the first run. If not, proceed to step S2; if yes, proceed to the initialization process. S2. Collect the actual pressure value and actual displacement value of all top hammers (410), calculate the average actual pressure of all top hammers (410) based on the collected actual pressure value, and calculate the pressure deviation between the average actual pressure and the preset target pressure. S3. Based on the actual displacement value collected, select the top hammer (410) with the smallest actual displacement value as the position reference, and calculate the position deviation of the remaining top hammers (410) relative to the position reference. S4. Based on the position deviation of each top hammer (410), if the absolute value of the position deviation of any top hammer (410) is greater than the position synchronization tolerance, the pressure compensation amount of each top hammer is calculated by the position sub-loop PID controller, and a pressure command is generated in combination with the leading or lagging state of the top hammer (410); if the absolute value of the position deviation of all top hammers (410) is less than or equal to the position synchronization tolerance, the control amount is calculated by the pressure fine-tuning loop PID controller based on the pressure deviation of each top hammer (410) and a pressure command is generated. S5. Based on the generated pressure command, drive each top hammer (410) to perform the corresponding motion action. After the action is performed, perform the detection. If the pressure deviation or position deviation of any top hammer (410) exceeds the preset safety threshold, then execute step S7. If the pressure deviation and position deviation of all top hammers (410) do not exceed the preset safety threshold, then return to step S2 to execute the next round of data acquisition and control, forming a closed-loop control process. S6. Continue to execute the closed-loop control process consisting of steps S2 to S5 until the pressurization time reaches the preset process setting value or the actual pressure value reaches the preset target final value, then stop the closed-loop control. S7. Save the historical data of pressure, displacement, command and alarm corresponding to all top hammers (410) during the entire pressurization process.

10. The method for dynamically adjusting the position and pressure of the top hammer in a back-bending six-sided top press according to claim 9, characterized in that, The initialization process includes: According to the process requirements, target pressure-time curves, target displacement-time curves, and control parameters are set. The control parameters include position synchronization tolerance, pressure deviation tolerance, and initial parameters of each PID controller. Based on the set results, zero-point calibration is performed on all displacement sensors (3) and preset pressure sensors, micro-strain values ​​are collected from each strain gauge (203), and the micro-strain values ​​are converted into deformation and the corresponding range is calculated. If the range is less than or equal to the maximum range, proceed to step S2; if the range is greater than the maximum range, issue an alarm and adjust the corresponding handwheel, continuously monitor the range until the range is less than or equal to the maximum range, then proceed to step S2.

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