A cubic press for synthetic diamond

Abstract

This invention relates to the field of superhard material synthesis equipment, specifically to a six-sided press for synthetic diamond, comprising a top hammer assembly with six sets, each set including a first locking structure. The first locking structure can apply a circumferentially uniformly distributed force to the positioning ring, thereby locking and fixing the positioning ring and the large pad in a coaxial state, ensuring the stability and coaxial accuracy of the connection between the positioning ring and the large pad, and effectively avoiding positioning offset or locking failure caused by uneven force.

Description

Technical Field

[0001] This invention relates to the field of superhard material synthesis equipment, and in particular to a six-sided press for synthetic diamond. Background Technology

[0002] The six-sided press for synthetic diamond is a core piece of equipment that uses high-temperature, high-pressure technology to achieve the phase transformation from graphite to diamond. It is widely used in the large-scale production of industrial-grade diamonds and some specialty diamonds, and is one of the mainstream pieces of equipment in the current field of synthetic diamond synthesis. The core purpose of the six-sided press for synthetic diamond is to provide a stable, extreme environment for diamond growth. Through precise control, it generates a high pressure of 10-16 GPa and a high temperature of 1200-2000℃ within the synthesis chamber, meeting the requirements for thermodynamically stable diamond crystal growth while ensuring the safety and efficiency of the synthesis process.

[0003] The six-sided press for synthetic diamond mainly consists of a main frame, a hydraulic system, and a hammer assembly. The main frame provides stable support, while the hydraulic system outputs driving force. The core hammer assembly includes a piston, pad, hammers, and positioning rings. Six hammers advance synchronously in three dimensions, and in conjunction with a heating system, the hydraulic energy is converted into high pressure of 10-16 GPa and high temperature of 1200-2000℃, creating conditions for the phase transformation of graphite into diamond.

[0004] However, existing technologies often use multiple screws to fix the pad and the locating ring along the circumference of the locating ring. During the tightening of these screws, due to differences in operating techniques, deviations in thread machining accuracy, and uneven force distribution among the screws, the locating ring and the pad are difficult to be evenly stressed. This leads to eccentricity between the pad, the locating ring, and the top hammer, resulting in uneven pressure distribution within the synthesis cavity. This causes an unstable diamond crystal growth environment, easily producing products with numerous internal defects and poor quality. Simultaneously, the eccentricity of the top hammer leads to force imbalance, accelerating its wear and damage, significantly shortening its service life, and increasing production costs. Summary of the Invention

[0005] Therefore, it is necessary to provide a six-sided press for synthetic diamonds that addresses the problem of eccentricity of the pads, positioning rings, and top hammers caused by the use of multiple screws for fixing in current six-sided presses for synthetic diamonds.

[0006] The above objectives are achieved through the following technical solutions:

[0007] A six-sided press for synthetic diamonds, comprising:

[0008] Support.

[0009] A mold carrier for containing synthetic raw materials.

[0010] The top hammer assembly comprises six groups, each group including a working piston, a large pad, a small pad, a top hammer, a positioning ring, and a first locking structure. The working piston is slidably mounted on the bracket, and the working pistons of the six groups of top hammer assemblies are arranged on the bracket in a preset manner. In the axial direction of the working piston, the large pad, the small pad, and the top hammer are arranged sequentially, and the top hammer can contact the surface of the mold carrier.

[0011] The positioning ring is sleeved on the outside of the small pad and the top hammer, and the positioning ring is coaxially fixedly connected to the large pad. The positioning ring is used to fix the top hammer and the small pad to the large pad coaxially.

[0012] The first locking structure can generate a circumferentially uniformly distributed force on the positioning ring to coaxially lock the positioning ring and the large pad.

[0013] Furthermore, the first locking structure includes multiple locking sliders and a first driving mechanism; the outer wall of the large pad is provided with an annular groove with an opening away from its own axis, the annular groove being used to accommodate multiple locking sliders; the multiple locking sliders are evenly distributed in the annular groove; the multiple locking sliders abut each other end to end in sequence, forming an annular structure that can expand and contract radially; the inner wall of the locking slider is set as a first inclined surface, the annular groove is provided with a second inclined surface that cooperates with the first inclined surface, after the multiple locking sliders expand radially in the annular groove, the first inclined surface and the second inclined surface can fit tightly together, and the outer wall of the locking slider can abut against the inner wall of the positioning ring.

[0014] The first driving mechanism can drive multiple locking sliders to move synchronously within the annular groove, so that the multiple locking sliders can expand radially under the action of the first inclined surface and the second inclined surface; the first driving mechanism can also maintain the contact state between the locking sliders and the large pad and the positioning ring, so as to lock the large pad and the positioning ring.

[0015] Furthermore, the first locking structure also includes a plurality of hydraulic jacks, which are evenly distributed along the circumference of the large pad. One end of each hydraulic jack is slidably connected to a locking slider, and the other end of each hydraulic jack is slidably connected to the large pad.

[0016] The first driving mechanism includes a hydraulic cylinder and a second hydraulic chamber. The second hydraulic chamber is disposed inside the large pad and is filled with hydraulic oil. The second hydraulic chamber can connect multiple hydraulic jacks and the hydraulic cylinder. The hydraulic cylinder can drive multiple hydraulic jacks to move synchronously along the axial direction of the large pad through the hydraulic oil.

[0017] Furthermore, the outer wall of the locking slider is configured as a friction rough surface, which is used to enhance the friction between the locking slider and the positioning ring.

[0018] Furthermore, the top hammer assembly also includes a rotating structure. When the locking slider moves within the annular groove, the rotating structure drives multiple locking sliders to rotate around the axis of the large pad to change the contact area between the outer wall of the locking slider and the inner wall of the positioning ring.

[0019] Furthermore, the rotating structure includes a telescopic top ball and a guide groove. The telescopic top ball is slidably connected to the side wall of the hydraulic jack, and the guide groove is disposed on the large pad. The guide groove is used to guide the telescopic top ball to drive the hydraulic jack to rotate around the axis of the large pad. A first elastic element is disposed between the telescopic top ball and the hydraulic jack. The elastic force of the first elastic element always causes the telescopic top ball to extend out of the hydraulic jack and embed into the guide groove.

[0020] Furthermore, the guide groove has multiple vertical sections and multiple inclined sections, which are connected end to end in an alternating manner; a protrusion is provided in the middle of the vertical section, which is used to restrict the telescopic top bead from sliding in the opposite direction along the guide groove.

[0021] Furthermore, the top hammer assembly also includes a second locking structure, which can generate an axial force on the positioning ring to further lock the positioning ring and the large pad.

[0022] Furthermore, the second locking structure includes a sliding plate, a supporting elastic element, and a pre-tightening bolt. The sliding plate is coaxially slidably connected to the positioning ring. A mounting plate extends radially from the outer wall of the large pad, and the mounting plate is located between the sliding plate and the positioning ring along the axial direction of the large pad. One end of the supporting elastic element is fixedly connected to the sliding plate, and the other end of the supporting elastic element abuts against the mounting plate. The elastic force of the supporting elastic element always keeps the sliding plate and the mounting plate away from each other. The pre-tightening bolt can penetrate the sliding plate and is fixedly connected to the positioning ring by threads.

[0023] Furthermore, the supporting elastic element is configured as a disc spring, which has a small deformation along the axial direction of the large pad.

[0024] The beneficial effects of this invention are:

[0025] This invention provides a six-sided pressing machine for synthetic diamond, including a set of six sets of top hammer assemblies, each set including a first locking structure. The first locking structure applies a uniformly distributed circumferential force to the positioning ring. This force ensures that the positioning ring and the large pad are locked together while maintaining coaxiality, guaranteeing the stability and coaxial accuracy of the connection between the positioning ring and the large pad, and effectively preventing positioning offset or locking failure caused by uneven force. Attached Figure Description

[0026] Figure 1 This is a schematic diagram of a six-sided press for synthetic diamonds provided in an embodiment of the present invention;

[0027] Figure 2 for Figure 1 Top view of the structure shown;

[0028] Figure 3 for Figure 2 A cross-sectional view along the AA direction;

[0029] Figure 4 This is a schematic diagram of the top hammer assembly in a six-sided top press for synthetic diamonds provided in an embodiment of the present invention. The outer shell of the machine body is hidden for easy observation.

[0030] Figure 5 for Figure 4 The front view of the structure shown;

[0031] Figure 6 for Figure 5 Cross-sectional view along the BB direction;

[0032] Figure 7 for Figure 6 A magnified view of a section at point C;

[0033] Figure 8 for Figure 6 A magnified view of a section at point D;

[0034] Figure 9 This is a schematic diagram of the positioning ring in a six-sided press for synthetic diamonds, provided in an embodiment of the present invention.

[0035] Figure 10 This is a schematic diagram of the locking slider in a six-sided press for synthetic diamonds, provided in an embodiment of the present invention.

[0036] Figure 11 This is a schematic diagram of the structure of a large pad in a six-sided press for synthetic diamonds provided in an embodiment of the present invention;

[0037] Figure 12 for Figure 11 A magnified view of a section at point E in the middle.

[0038] in:

[0039] 110. Base;

[0040] 210. Machine casing; 220. Working piston; 230. Large pad; 231. Fixing bolt; 232. Guide slide; 233. Mounting plate; 240. Locking slider; 241. Hydraulic jack; 242. Telescopic jack ball; 250. Small pad; 260. Jack; 270. Positioning ring; 271. Sliding plate; 272. Disc spring; 273. Preload bolt;

[0041] 310. Mold carrier. Detailed Implementation

[0042] To make the objectives, technical solutions, and advantages of this invention clearer, the invention will be further described in detail below through embodiments and in conjunction with the accompanying drawings. It should be understood that the specific embodiments described herein are merely illustrative of the invention and are not intended to limit the invention.

[0043] The component designations used in this document, such as "first" and "second," are merely for distinguishing the described objects and do not have any sequential or technical meaning. The terms "connection" and "linkage" used in this invention, unless otherwise specified, include both direct and indirect connections (linkages). It should be understood that the terms "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," "clockwise," and "counterclockwise," indicating orientations or positional relationships, are based on the orientations or positional relationships shown in the accompanying drawings and are used only for the convenience of describing the invention and simplifying the description. They do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as limiting the invention.

[0044] In this invention, unless otherwise explicitly specified and limited, "above" or "below" the second feature can mean that the first feature is in direct contact with the second feature, or that the first feature is in indirect contact with the second feature through an intermediate medium. Furthermore, "above," "over," and "on top" of the second feature can mean that the first feature is directly above or diagonally above the second feature, or simply that the first feature is at a higher horizontal level than the second feature. "Below," "below," and "under" the second feature can mean that the first feature is directly below or diagonally below the second feature, or simply that the first feature is at a lower horizontal level than the second feature.

[0045] The following reference Figures 1 to 12 This invention describes a six-sided press for synthetic diamonds provided in an embodiment of the present invention.

[0046] The present invention provides a six-sided press for synthetic diamonds, comprising a mold carrier 310, a base 110, a bracket, a hammer assembly, and a drive assembly.

[0047] The mold carrier 310 has a centrally symmetrical cubic or hexahedral structure and is made of pyrophyllite composite material that is resistant to high temperature and pressure and has a certain degree of elasticity, enabling it to withstand high temperature and pressure without local deformation or breakage. A synthesis cavity is located at the geometric center of the mold carrier 310 to hold the synthesis raw materials. A heating element is also installed in the mold carrier 310 to generate heat through electrical current and efficiently transfer the heat to the synthesis cavity, providing a high-temperature environment for the synthesis raw materials.

[0048] The base 110 is fixedly installed on the ground or other fixed support surface to provide stable support for other components.

[0049] The support frame comprises six housing shells 210. One end of one housing shell 210 is fixedly connected to the base 110, providing a reference for the subsequent installation of other housing shells 210. Each housing shell 210 has pin holes machined on adjacent end faces. By inserting cylindrical pins into the pin holes of adjacent housing shells 210, a fixed connection between the multiple housing shells 210 is achieved. All housing shells 210 are arranged in a three-dimensional orthogonal distribution on the base 110 with overlapping intersection points. Through the positioning and fixing action of the cylindrical pins, a rigid overall frame structure is formed.

[0050] The top hammer assembly is set with six groups, each group of top hammer assembly includes a working piston 220, a large pad 230, a small pad 250, a top hammer 260 and a positioning ring 270.

[0051] The housing 210 has a pre-reserved sliding cavity for cooperating with the working piston 220. The outer wall of the working piston 220 fits tightly with the inner wall of the sliding cavity of the housing 210, and is completely embedded in the housing 210. The working piston 220 is used to drive the large pad 230, the small pad 250, and the top hammer 260 to move axially synchronously. The housing 210 provides radial limit and motion guidance for the working piston 220, ensuring that the working piston 220 can only move linearly along the axial direction and avoid radial deviation.

[0052] One end of the large pad 230 is fixedly connected to the end face of the working piston 220 by a fixing bolt 231, and the other end face is in contact with one end face of the small pad 250, and the axis of the large pad 230 coincides with the axis of the working piston 220. The large pad 230 is used to buffer the force transmitted by the working piston 220 and evenly distribute the force to the small pad 250.

[0053] The small pad 250 has a large end face and a small end face along the axial direction. The large end face fits into the end face of the large pad 230, and the small end face fits into the rear end face of the top hammer 260. The axis of the small pad 250 coincides with the axis of the large pad 230. The small pad 250 is used to accommodate the size difference between the large pad 230 and the top hammer 260, so as to realize the transition and transmission of force between the large pad 230 and the top hammer 260.

[0054] The front end face of the ejector hammer 260 is in direct contact with the mold carrier 310, and the rear end face of the ejector hammer 260 is in contact with the small end face of the small pad 250. The ejector hammer 260 is used to convert the force transmitted by the small pad 250 into the high pressure required for the synthesis chamber. By using six ejector hammers 260 to extrude synchronously from three-dimensional orthogonal directions, a high-pressure environment for synthesis is constructed.

[0055] The positioning ring 270 is a hollow annular structure with through holes penetrating both axial ends. These through holes are divided into a large-diameter end and a small-diameter end along the axis. The positioning ring 270 is fixedly connected to the large pad 230. The top hammer 260 and the small pad 250 are sequentially inserted into the positioning ring 270 from the large-diameter end. A limiting platform is provided at the rear end of the top hammer 260. After the top hammer 260 and the small pad 250 are installed in place, the small-diameter end of the positioning ring 270 can restrict the limiting platform at the rear end of the top hammer 260 to prevent the top hammer 260 from detaching from the positioning ring 270, while the front end of the top hammer 260 can extend out of the positioning ring 270. The positioning ring 270 is used to keep the small pad 250 and the top hammer 260 coaxially fixed with the large pad 230.

[0056] The drive assembly includes a hydraulic cylinder (not shown) and a first hydraulic chamber. The hydraulic cylinder serves as a power source, outputting continuous and uniform hydraulic energy. The first hydraulic chamber connects the hydraulic cylinder and the working piston 220, and is filled with hydraulic oil. When the hydraulic cylinder outputs hydraulic energy, the hydraulic oil generates pressure within the first hydraulic chamber. This pressure is transmitted to the working piston 220, pushing it to move linearly along the sliding cavity of the outer casing 210. This, in turn, causes the large pad 230, the small pad 250, and the top hammer 260 to move axially synchronously, thereby pressurizing the synthesis chamber.

[0057] However, in traditional six-sided top presses, the positioning ring 270 and the large pad 230 are fixed by multiple screws. During the tightening process, due to differences in operating techniques, thread machining accuracy deviations, and assembly sequence, the preload of each screw cannot be completely uniform. This causes the positioning ring 270 to experience unbalanced force, resulting in a misalignment between its axis and the axis of the large pad 230, making strict coaxiality impossible. The misalignment between the positioning ring 270 and the large pad 230 directly leads to the misalignment of the axes of the small pad 250 and the top hammer 260, reducing the alignment accuracy of the six sets of top hammer assemblies and causing uneven pressure distribution within the synthesis chamber. This not only affects the growth quality of diamond crystals, leading to an increased product defect rate, but also accelerates the wear of the top hammer 260 due to the unbalanced force, shortening its service life and increasing equipment maintenance costs.

[0058] Based on this, the top hammer assembly also includes a first locking structure, which can apply a circumferentially uniformly distributed force to the positioning ring 270. Through this circumferentially uniform force, the positioning ring 270 and the large pad 230 are locked and fixed in a coaxial state.

[0059] Specifically, the first locking structure includes multiple locking sliders 240, multiple hydraulic jacks 241, and a first drive mechanism.

[0060] The locking slider 240 has an arc-shaped block structure. Multiple locking sliders 240 are connected end-to-end in sequence to form a ring structure that can expand and contract radially. Adjacent locking sliders 240 abut against each other through guide slopes with the same deflection angle. When adjacent locking sliders 240 abut, the guide slopes of the two locking sliders 240 are completely in contact. Each locking slider 240 has a sliding groove at one end and a sliding protrusion at the other end that mates with the sliding groove. The sliding protrusion of one locking slider 240 can be embedded into the sliding groove of an adjacent locking slider 240, forming a connection structure that can slide relative to each other along the guide slope. This ensures that multiple locking sliders 240 can slide smoothly along the guide slope to achieve synchronous expansion or contraction.

[0061] The outer wall of the large pad 230 has a coaxially arranged annular groove with an opening away from its own axis. This groove accommodates multiple locking sliders 240, providing installation and movement space for the sliders. The multiple locking sliders 240 are completely accommodated within the annular groove of the large pad 230, allowing them to move within the groove. The annular structure formed by the multiple locking sliders 240 is coaxial with the large pad 230. Each locking slider 240 has a first inclined surface that gradually slopes away from the small pad 250 from the inside out along the radial direction of the large pad 230. The inner wall of the annular groove of the large pad 230 has a second inclined surface, allowing the first inclined surface to fit tightly against the second inclined surface. The outer wall of the locking slider 240 is cylindrical, allowing it to abut against the inner wall of the positioning ring 270.

[0062] Multiple locking sliders 240 have a first state and a second state.

[0063] When multiple locking sliders 240 are in the first state, the multiple locking sliders 240 are connected end to end through the guide slope to form a complete ring structure, and the whole is located in the ring groove of the large pad 230 near the small pad 250.

[0064] As the multiple locking sliders 240 move away from the small pad 250 within the annular groove of the large pad 230, adjacent locking sliders 240 slide relative to each other along the guide ramps because there is no fixed constraint between them. The originally connected annular structure gradually expands, and the adjacent locking sliders 240 separate, with the overall outer diameter gradually increasing during the separation process. During this process, because the guide ramps on which the adjacent locking sliders 240 abut are identical, the axes of the multiple locking sliders 240 remain coaxial with the axis of the large pad 230. Simultaneously, the positions of the multiple locking sliders 240 within the annular groove gradually move away from the small pad 250 until the locking sliders 240 enter the second state.

[0065] When the locking slider 240 enters the second state, the first inclined surface of the locking slider 240 is in close contact with the second inclined surface of the annular groove of the large pad 230, and the cylindrical surface of the locking slider 240 is in close contact with the inner wall of the positioning ring 270.

[0066] Multiple hydraulic jacks 241 are evenly distributed circumferentially along a large pad 230. One end of each hydraulic jack 241 is slidably connected to a locking slider 240, and the other end is slidably connected to the large pad 230, with the sliding direction along the axial direction of the large pad 230. An annular plate is fixedly connected to the ends of the multiple hydraulic jacks 241, and the central axis of the annular plate coincides with the central axis of the large pad 230. The connection points between the annular plate and each hydraulic jack 241 are evenly distributed circumferentially along the annular plate. The annular plate ensures synchronous movement of the multiple hydraulic jacks 241 along the axial direction of the large pad 230.

[0067] The first drive mechanism includes a second hydraulic chamber (not shown in the figure) and connecting pipes.

[0068] The second hydraulic chamber is located inside the large pad 230. One end of the second hydraulic chamber is connected to the first hydraulic chamber through a connecting pipe with a valve. The valve on the connecting pipe can control the opening and closing of the first and second hydraulic chambers and the flow of hydraulic oil. The other end of the second hydraulic chamber is connected to the end of multiple hydraulic pushers 241 away from the locking slider 240.

[0069] When it is necessary to lock the positioning ring 270, the valve is opened, and the hydraulic oil in the first hydraulic chamber enters the second hydraulic chamber through the connecting pipeline. The hydraulic oil pressure pushes the hydraulic jack 241 to move axially along the large pad 230. The hydraulic jack 241 then applies a stable thrust to the locking slider 240, driving the locking slider 240 to move, so that multiple locking sliders 240 switch from the first state to the second state, so that the first inclined surface of the locking slider 240 is tightly fitted with the second inclined surface of the annular groove of the large pad 230, and the cylindrical surface of the locking slider 240 is tightly abutted against the inner wall of the positioning ring 270.

[0070] When the locking slider 240 switches to the second state, the second hydraulic chamber continuously transmits hydraulic energy to multiple hydraulic jacks 241. The hydraulic jacks 241 synchronously push the locking slider 240 along the axial direction of the large pad 230. Under the thrust, the first inclined surface of the locking slider 240 is tightly fitted with the second inclined surface of the annular groove of the large pad 230. Because the first and second inclined surfaces are perfectly matched, a radially outward component force is formed, causing the multiple locking sliders 240 to expand uniformly in the circumferential direction. At the same time, the cylindrical surface of the locking slider 240 is tightly abutted against the inner wall of the positioning ring 270. Since the multiple locking sliders 240 are evenly distributed in the circumference of the large pad 230, and the thrust of the hydraulic jacks 241 is completely synchronized, the force exerted by each locking slider 240 on the inner wall of the positioning ring 270 is equal in magnitude and points towards the center of the positioning ring 270. This uniform radial force forces the axis of the positioning ring 270 to completely coincide with the axis of the large pad 230, and remains stable under the continuous hydraulic support force of the hydraulic oil in the second hydraulic chamber, thereby achieving absolute coaxial locking between the positioning ring 270 and the large pad 230.

[0071] When it is necessary to unlock the positioning ring 270, the hydraulic cylinder reduces the hydraulic oil pressure in the second hydraulic chamber. Under the action of the pressure difference, the hydraulic jack 241 moves axially along the large pad 230 toward the small pad 250, and the locking slider 240 moves downward synchronously under the action of the hydraulic jack 241. As the downward movement proceeds, the first inclined surface of the locking slider 240 gradually disengages from the second inclined surface of the annular groove of the large pad 230, and the radial expansion component between the locking slider 240 and the large pad 230 disappears. At the same time, the cylindrical surface of the locking slider 240 gradually separates from the inner wall of the positioning ring 270, and the radial constraint force on the positioning ring 270 is released. When the hydraulic jack 241 drives the locking slider 240 to move downward until it is completely out of contact with the large pad 230 and the positioning ring 270, the locking slider 240 releases its locking effect on the large pad 230 and the positioning ring 270, and the positioning ring 270 is unlocked, allowing for free position adjustment or disassembly.

[0072] Thus, the second hydraulic chamber provides synchronous and uniform hydraulic thrust to multiple hydraulic jacks 241, ensuring that the locking sliders 240 distributed circumferentially along the large pad 230 are subjected to completely consistent forces. The first inclined surface of the locking slider 240 is in close contact with the second inclined surface of the annular groove of the large pad 230, converting the axial thrust of the hydraulic jacks 241 into a uniform radial expansion force. Furthermore, the cylindrical surface of the locking slider 240 is in close contact with the inner wall of the positioning ring 270, forming a uniform radial constraint force along the circumference of the positioning ring 270. This forces the axis of the positioning ring 270 to coincide with the axis of the large pad 230, enabling the positioning ring 270 and the large pad 230 to achieve high-precision coaxial locking. This simultaneously drives the small pad 250, the jack hammer 260, and the large pad 230 to maintain strict coaxiality, avoiding the problem of uneven pressure distribution within the synthesis chamber.

[0073] Furthermore, the outer wall of the locking slider 240 is configured as a friction-rough surface. The outer wall of the locking slider 240, i.e., the cylindrical surface where the locking slider 240 contacts the inner wall of the positioning ring 270, is configured as a friction-rough surface, completely covering the contact area between the locking slider 240 and the positioning ring 270. The friction-rough surface is used to enhance the friction between the locking slider 240 and the positioning ring 270, ensuring that there is no relative sliding between the locking slider 240 and the positioning ring 270 during the use of the six-sided top press.

[0074] Furthermore, when the hydraulic jack 241 pushes the locking slider 240 to move, since the hydraulic jack 241 only moves along the axial direction, the contact area between the locking slider 240 and the positioning ring 270 is easily fixed. After long-term use, the contact surface will experience local wear, affecting the coaxial locking stability of the positioning ring 270 and the large pad 230.

[0075] Based on this, the top hammer assembly also includes a rotating structure, which is used to drive multiple locking sliders 240 to rotate around the axis of the large pad 230 during the movement of the locking slider 240 in the annular groove of the large pad 230, so as to change the contact area between the cylindrical surface of the locking slider 240 and the inner wall of the positioning ring 270, and avoid excessive wear in a single area of ​​the locking slider 240.

[0076] Specifically, when the first inclined surface of the locking slider 240 is in close contact with the second inclined surface of the annular groove of the large pad 230, and the cylindrical surface of the locking slider 240 is in close contact with the inner wall of the positioning ring 270, there is a uniform interval between the multiple locking sliders 240.

[0077] The rotating structure includes a telescopic top ball 242 and a guide groove 232.

[0078] The telescopic ball bearing 242 is slidably connected to the side wall of the hydraulic jack 241, and the sliding direction is perpendicular to the axis of the hydraulic jack 241. A first elastic element, which is a spring, is provided between the telescopic ball bearing 242 and the hydraulic jack 241. The spring always applies a spring force to the telescopic ball bearing 242 away from the hydraulic jack 241, so that the telescopic ball bearing 242 continuously extends out of the hydraulic jack 241.

[0079] A guide groove 232 is provided on the large pad 230, and the telescopic ball 242 can be embedded in the guide groove 232. The guide groove 232 includes multiple vertical sections and multiple inclined sections, which are staggered and connected end to end with smooth joints. The rotation angle of the hydraulic jack 241 can be controlled by controlling the angle at the joint between the vertical and inclined sections. When the telescopic ball 242 moves along the vertical section, the hydraulic jack 241 moves only axially; when the telescopic ball 242 enters the inclined section, the inclined section of the guide groove 232 drives the telescopic ball 242 to drive the hydraulic jack 241 to rotate around the axis of the large pad 230, thereby driving the locking slider 240 to rotate synchronously through the hydraulic jack 241. A protrusion is provided in the middle of the vertical section of the guide groove 232, which extends towards the axis of the large pad 230 to form a limit when the telescopic ball 242 moves along the guide groove 232.

[0080] When the hydraulic jack 241 pushes the locking slider 240 away from the small pad 250, the telescopic ball 242 is located below the protrusion. The protrusion completely prevents the telescopic ball 242 from moving in the opposite direction along the vertical section, ensuring that the telescopic ball 242 can only move along the inclined section. As the telescopic ball 242 on the hydraulic jack 241 gradually moves upward along the inclined section, the telescopic ball 242 drives the hydraulic jack 241 to rotate around the axis of the large pad 230. When the locking slider 240 enters the second state, the telescopic ball 242 is located above the protrusion in the vertical section. At this time, due to the continuous outward elastic force applied by the spring to the telescopic ball 242, the telescopic ball 242 is tightly attached to the inner wall of the guide groove 232. The protrusion prevents the telescopic ball 242 from sliding down on its own, ensuring that the locking slider 240 is stably maintained in the second state.

[0081] As the hydraulic jack 241 drives the locking slider 240 closer to the small pad 250, the telescopic ball 242 moves downward along the vertical section. At this time, the hydraulic jack 241 can generate sufficient thrust to make the telescopic ball 242 overcome the spring force and retract into the hydraulic jack 241 to pass over the protrusion, thereby resetting the locking slider 240.

[0082] Thus, by moving the telescopic top ball 242 along the inclined section of the guide groove 232, the hydraulic top column 241 and the locking slider 240 are driven to rotate around the axis of the large pad 230, so that the cylindrical surface of the locking slider 240 is in uniform contact with the inner wall of the positioning ring 270, thus avoiding local wear of the inner wall of the positioning ring 270.

[0083] In one embodiment, the top hammer assembly further includes a second locking structure, which can apply a force along the axial direction of the large pad 230 to the positioning ring 270, forming an axial constraint force between the positioning ring 270 and the large pad 230, thereby further enhancing the locking effect between the positioning ring 270 and the large pad 230.

[0084] Specifically, the second locking structure includes a sliding plate 271, a supporting elastic element, and a pre-tightening bolt 273.

[0085] The sliding plate 271 is an annular plate structure, coaxially arranged and slidably connected with the positioning ring 270, with the sliding direction along the axial direction of the positioning ring 270. The outer wall surface of the large pad 230 extends radially away from its own axis to form a mounting plate 233. The mounting plate 233 is an annular flange structure and is located between the sliding plate 271 and the positioning ring 270. The supporting elastic element is a disc spring 272, which has a small deformation along the axial direction of the large pad 230. One end of the disc spring 272 is fixedly connected to the end face of the sliding plate 271 facing the mounting plate 233, and the other end directly abuts against the end face of the mounting plate 233 facing the sliding plate 271. The elastic force of the disc spring 272 always keeps the sliding plate 271 and the mounting plate 233 away from each other. The preload bolt 273 is a columnar structure with external threads. The upper wall of the positioning ring 270 is provided with an internal thread that mates with the external thread. The preload bolt 273 can penetrate the sliding plate 271 and be fixedly connected to the positioning ring 270 by threads, thereby locking the axial position of the sliding plate 271 and the positioning ring 270.

[0086] During the installation of the positioning ring 270, the pre-tightening bolt 273 is first passed through the sliding plate 271, and then the threaded end of the pre-tightening bolt 273 is screwed into the positioning ring 270. As the pre-tightening bolt 273 is continuously screwed, its head generates an axial pulling force on the sliding plate 271 towards the positioning ring 270, causing the sliding plate 271 to move closer to the positioning ring 270 along the axial direction. Simultaneously, during this process, the sliding plate 271 compresses the disc spring 272, and the disc spring 272 generates an axial elastic reaction force due to deformation. When the deformation of the disc spring 272 reaches a preset value, the axial pre-tightening of the positioning ring 270 is completed. At this time, the elastic reaction force of the disc spring 272 is transmitted to the large pad 230 through the mounting plate 233, and simultaneously to the positioning ring 270 through the pre-tightening bolt 273, forming an initial axial pre-tightening force. Under the action of this pre-tightening force, the positioning ring 270 is constrained in the opposite direction, ensuring complete contact between the mating surfaces of the small pad 250 and the large pad 230.

[0087] After the first locking structure completes the coaxial locking of the positioning ring 270 and the large pad 230 through the locking slider 240, the pre-tightening bolt 273 is tightened again with torque. The pre-tightening bolt 273 further compresses the disc spring 272, increasing the elastic reaction force of the disc spring 272. This elastic reaction force is transmitted to the large pad 230 through the mounting plate 233, and at the same time to the positioning ring 270 through the pre-tightening bolt 273, forming a larger axial locking force between the positioning ring 270 and the large pad 230, thereby achieving further locking of the positioning ring 270 and the large pad 230.

[0088] Thus, the elastic reaction force of the disc spring 272 applies a continuous axial preload to the positioning ring 270 and the large pad 230, and at the same time, the preload bolt 273 further locks the sliding plate 271 and the positioning ring 270.

[0089] The technical features of the above embodiments can be combined in any way. For the sake of brevity, not all possible combinations of the technical features in the above embodiments are described. However, as long as there is no contradiction in the combination of these technical features, they should be considered to be within the scope of this specification.

[0090] The embodiments described above are merely illustrative of several implementations of the present invention, and while the descriptions are specific and detailed, they should not be construed as limiting the scope of the invention. It should be noted that those skilled in the art can make various modifications and improvements without departing from the concept of the present invention, and these modifications and improvements all fall within the scope of protection of the present invention. Therefore, the scope of protection of the present invention should be determined by the appended claims.

Claims

1. A cubic press for synthetic diamond, characterized by comprising: include: support; A mold carrier for containing synthetic raw materials; The top hammer assembly comprises six sets, each set including a working piston, a large pad, a small pad, a top hammer, a positioning ring, and a first locking structure; the working piston is slidably mounted on the bracket, and the working pistons of the six sets of top hammer assemblies are arranged on the bracket in a preset manner; in the axial direction of the working piston, the large pad, the small pad, and the top hammer are arranged sequentially, and the top hammer can contact the surface of the mold carrier; The positioning ring is sleeved on the outside of the small pad and the top hammer, and the positioning ring is coaxially fixedly connected to the large pad. The positioning ring is used to fix the top hammer and the small pad to the large pad coaxially. The first locking structure can generate a circumferentially uniformly distributed force on the positioning ring to coaxially lock the positioning ring and the large pad. The first locking structure includes multiple locking sliders and a first driving mechanism; the outer wall of the large pad is provided with an annular groove with an opening away from its own axis, the annular groove being used to accommodate multiple locking sliders; the multiple locking sliders are evenly distributed in the annular groove; the multiple locking sliders abut each other end to end in sequence, forming an annular structure that can expand and contract radially; the inner wall of the locking slider is provided with a first inclined surface, the annular groove is provided with a second inclined surface that cooperates with the first inclined surface, after the multiple locking sliders expand radially in the annular groove, the first inclined surface and the second inclined surface can fit tightly together, and the outer wall of the locking slider can abut against the inner wall of the positioning ring; The first driving mechanism can drive multiple locking sliders to move synchronously within the annular groove, so that the multiple locking sliders can expand radially under the action of the first inclined surface and the second inclined surface; the first driving mechanism can also maintain the contact state between the locking sliders and the large pad and the positioning ring, so as to lock the large pad and the positioning ring. The first locking structure further includes a plurality of hydraulic jacks, which are evenly distributed along the circumference of the large pad. One end of each hydraulic jack is slidably connected to a locking slider, and the other end of each hydraulic jack is slidably connected to the large pad. The first driving mechanism includes a hydraulic cylinder and a second hydraulic chamber. The second hydraulic chamber is disposed inside the large pad and is filled with hydraulic oil. The second hydraulic chamber can connect multiple hydraulic jacks and the hydraulic cylinder. The hydraulic cylinder can drive multiple hydraulic jacks to move synchronously along the axial direction of the large pad through the hydraulic oil.

2. The cubic press for synthetic diamond according to claim 1, characterized by The outer wall of the locking slider is configured as a friction rough surface, which is used to enhance the friction between the locking slider and the positioning ring.

3. The cubic press for synthetic diamond according to claim 1, characterized by The top hammer assembly also includes a rotating structure. When the locking slider moves within the annular groove, the rotating structure drives multiple locking sliders to rotate around the axis of the large pad to change the contact area between the outer wall of the locking slider and the inner wall of the positioning ring.

4. The cubic press for synthetic diamond according to claim 3, characterized by The rotating structure includes a telescopic ball and a guide groove. The telescopic ball is slidably connected to the side wall of the hydraulic jack. The guide groove is disposed on the large pad and is used to guide the telescopic ball to drive the hydraulic jack to rotate around the axis of the large pad. A first elastic element is disposed between the telescopic ball and the hydraulic jack. The elastic force of the first elastic element always causes the telescopic ball to extend out of the hydraulic jack and embed into the guide groove.

5. The cubic press for synthetic diamond according to claim 4, characterized by The guide groove has multiple vertical sections and multiple inclined sections, which are connected end to end in an alternating manner; a protrusion is provided in the middle of the vertical section, which is used to restrict the telescopic top bead from sliding in the opposite direction along the guide groove.

6. The six-sided press for synthetic diamonds according to claim 1, characterized in that, The top hammer assembly also includes a second locking structure, which can generate an axial force on the positioning ring to further lock the positioning ring and the large pad.

7. The six-sided press for synthetic diamonds according to claim 6, characterized in that, The second locking structure includes a sliding plate, a supporting elastic element, and a pre-tightening bolt. The sliding plate is slidably connected to the positioning ring on the same axis. A mounting plate extends radially from the outer wall of the large pad, and the mounting plate is located between the sliding plate and the positioning ring along the axial direction of the large pad. One end of the supporting elastic element is fixedly connected to the sliding plate, and the other end of the supporting elastic element abuts against the mounting plate. The elastic force of the supporting elastic element always keeps the sliding plate and the mounting plate away from each other. The pre-tightening bolt can penetrate the sliding plate and is fixedly connected to the positioning ring by threads.

8. The six-sided press for synthetic diamonds according to claim 7, characterized in that, The supporting elastic element is configured as a disc spring, which has a small deformation along the axial direction of the large pad.

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