Temperature control device for a cubic press

Abstract

The present application relates to the technical field of auxiliary structure of cubic press, in particular to a temperature control device of cubic press, which is applied to cubic press, and the cubic press comprises six top hammers, each of which is provided with small and large pads, and a steel ring is detachably sleeved on the top hammer, the small and large pads and the top hammer; the temperature control device of cubic press comprises a cooling liquid pipe, each top hammer is provided with a cooling liquid pipe, both ends of the cooling liquid pipe pass through the small pad, and the cooling liquid pipe is detachably arranged on the steel ring, the cooling liquid pipe is configured to receive external cold liquid, thereby breaking through the heat transfer bottleneck of traditional indirect cooling of steel ring, so that the heat of the top hammer can be directly radiated through the cooling liquid pipe, while significantly reducing the interface thermal resistance and material thermal conductivity loss in the heat conduction path, the temperature stability of the superhard material synthesis process is ensured, and the synthesis efficiency and product quality are improved.

Description

Technical Field

[0001] This invention relates to the field of auxiliary structure technology for six-sided top presses, and in particular to a temperature control device for a six-sided top press. Background Technology

[0002] The six-sided pressure press, a key high-pressure experimental device in materials science and engineering, is based on the principle of multi-directional high-pressure synergy. It constructs a hexahedral ultra-high-pressure cavity at the center of the equipment through simultaneous pressure application in six directions. Under this extreme high-pressure environment, the interatomic spacing within the material significantly decreases, and the crystal structure undergoes reorganization, thereby achieving material densification, novel phase structure-induced synthesis, and special property regulation. This technology is widely used in the microstructure optimization of metallic materials and the high-pressure sintering of ceramic matrix composites. Furthermore, it holds a central position in the field of artificial diamond synthesis—by simulating the high-temperature and high-pressure environment deep within the Earth, it induces the transformation of graphite crystal structure into a diamond lattice, enabling industrial-scale mass production.

[0003] In China's superhard material synthesis industry, the hinged beam six-sided top press has become the mainstream equipment due to its advantages such as compact structure, convenient operation, and controllable cost. The core components of this equipment, the steel ring and the top hammer, constitute the key structure for high-pressure bearing and transmission: the top hammer, as the component in direct contact with the sample, bears pressure loads of up to several gigapascals and high temperatures of thousands of degrees Celsius, becoming the main heat source of the entire system; the steel ring, through precise mechanical fit, evenly distributes the pressure in six directions, while providing lateral support for the top hammer. Due to the mechanical performance limits of the equipment materials and the stringent temperature requirements of the superhard material synthesis process, relying solely on the natural heat dissipation of the steel ring and top hammer is insufficient to meet the needs of continuous production. Therefore, an external cooling system has become an essential configuration for the stable operation of the equipment.

[0004] The water cooling system commonly used in the industry is based on the high specific heat capacity of water, which removes heat from the equipment through forced convection. In related technologies, such as Chinese patent CN206415084U, a top hammer steel ring mating structure for a six-sided hydraulic press is disclosed. The steel ring has an annular cooling water channel on its ring wall, which is connected to an external water channel. This enables water cooling of the steel ring and the top hammer. The heat dissipation efficiency of the steel ring and the top hammer can be adjusted by controlling the water flow rate, thereby controlling the temperature of the steel ring and the top hammer.

[0005] However, the aforementioned hammer and steel ring mating structure used in a six-sided hydraulic press also has some problems in actual use: the heat generated by the hammer needs to be transferred to the steel ring through the hammer-steel ring contact surface via heat conduction, and then conducted by the steel ring to the cooling water tank for heat dissipation; due to the difference in thermal conductivity between the hammer and steel ring materials, coupled with the thermal resistance at the contact interface, the heat transfer efficiency is greatly reduced, which seriously affects the temperature stability of the superhard material synthesis process, and thus leads to problems such as reduced synthesis efficiency and uneven product quality. Summary of the Invention

[0006] Therefore, it is necessary to provide a temperature control device for a six-sided top press to address the poor reliability of current six-sided top presses during use.

[0007] The above objectives are achieved through the following technical solutions:

[0008] A temperature control device for a six-sided top press is disclosed. The six-sided top press includes six top hammers, each top hammer having a small pad and a large pad. A steel ring is detachably fitted onto each top hammer, the small pad, and the large pad. The temperature control device includes a coolant pipe, with a coolant pipe inserted into each top hammer. Both ends of the coolant pipe pass through the small pad and are detachably mounted on the steel ring. The coolant pipe is configured to receive external cold liquid.

[0009] Furthermore, each of the coolant pipes is fitted with a temperature equalization tube, which is configured to receive an external cold source; the flow direction of the external cold source in the temperature equalization tube is opposite to the flow direction of the external coolant in the coolant pipe.

[0010] Furthermore, the heat exchanger tube has a spiral structure.

[0011] Furthermore, each of the heat exchange tubes is fixedly fitted with multiple fixed sleeves, which are arranged circumferentially; each fixed sleeve includes multiple fixed sleeves, which are arranged along the extension direction of the heat exchange tube; each of the multiple fixed sleeves in each fixed sleeve is fixedly connected with an adjusting strip, and the adjusting strip between adjacent fixed sleeves has a V-shaped structure with the opening facing inward. The adjusting strip is configured to reduce the opening size of the V-shaped structure when its own temperature is greater than a preset value, and to automatically recover when its own temperature is less than the preset value.

[0012] Furthermore, a heat insulation part is fixedly provided on the outer side of the small end of each of the V-shaped structures, and the heat insulation part is configured to isolate the coolant pipe and the regulating bar.

[0013] Furthermore, the external cold source is a cooling gas.

[0014] Furthermore, the top hammer is divided into two parts along the axial direction, and the coolant pipe is inserted between the two parts of the top hammer.

[0015] Furthermore, the cross-sectional shape of the heat exchanger tube is elliptical or plum blossom-shaped.

[0016] Furthermore, the portion of the coolant pipe inside the top hammer has a vortex-like shape.

[0017] Furthermore, the external cooling liquid flows in the top hammer in a direction from the inner end of the vortex to the outer end of the vortex.

[0018] The beneficial effects of this invention are:

[0019] This invention relates to a temperature control device for a six-sided top press. By setting a coolant pipe inside the top hammer and utilizing the cooling characteristics of the coolant pipe, the heat transfer bottleneck of the traditional indirect cooling of the steel ring is broken through, so that the heat of the top hammer can be directly dissipated through the coolant pipe, achieving direct heat dissipation. While significantly reducing the interfacial thermal resistance and material thermal conductivity loss in the heat conduction path, it ensures the temperature stability of the superhard material synthesis process, improves synthesis efficiency and product quality.

[0020] Furthermore, by installing a heat exchanger in each coolant pipe and setting the flow direction of the external cold source in the heat exchanger to be opposite to the flow direction of the external coolant in the coolant pipe, the heat exchanger can absorb heat from the coolant pipe. This reduces the temperature gradient in the coolant pipe while ensuring a large temperature difference between the coolant pipe and the top hammer, thereby improving the heat dissipation efficiency of the coolant pipe for the top hammer.

[0021] Furthermore, by setting a fixed sleeve and a matching regulating strip, on the one hand, the structural characteristics are utilized to ensure that the heat exchanger is always located in the central area of ​​the coolant pipe, with the axes basically coinciding, thus ensuring a uniform and stable heat exchange process; on the other hand, by utilizing the temperature deformation characteristics of the regulating strip, when the temperature of the regulating strip itself exceeds a preset value, the opening size of the V-shaped structure is reduced, increasing the number of turns of the heat exchanger corresponding to the high-temperature area of ​​the coolant pipe. This increases the heat exchange area between the heat exchanger and the high-temperature area of ​​the coolant pipe, thereby improving the cooling efficiency of the high-temperature area of ​​the coolant pipe. This prevents the local temperature abnormalities of the coolant pipe from worsening, while also allowing time for subsequent induction flow regulation, thus improving the yield rate. Attached Figure Description

[0022] Figure 1 A three-dimensional structural diagram of the temperature control device and the hammer head assembly of the six-sided top press provided in the embodiment of the present invention;

[0023] Figure 2 A cross-sectional view of the temperature control device of a six-sided top press without a heat exchanger and the assembly of the hammer head of the six-sided top press, as provided in an embodiment of the present invention.

[0024] Figure 3 An exploded view of the temperature control device for the six-sided top press and the assembly of the hammer head of the six-sided top press, provided in an embodiment of the present invention.

[0025] Figure 4 A three-dimensional structural diagram of a portion of the temperature control device for a six-sided top press provided in an embodiment of the present invention;

[0026] Figure 5 for Figure 4 Exploded view of the parts in the medium structure;

[0027] Figure 6 for Figure 5 Enlarged local structure at point A;

[0028] Figure 7 Schematic diagram of the cross-sectional shape of the coolant pipe of the temperature control device for the six-sided top press provided in the embodiment of the present invention. Figure 1 ;

[0029] Figure 8 Schematic diagram of the cross-sectional shape of the coolant pipe of the temperature control device for the six-sided top press provided in the embodiment of the present invention. Figure 2 .

[0030] in:

[0031] 1. Top hammer; 101. Pushing end; 102. Connecting end; 103. First mounting groove; 104. First mounting hole;

[0032] 2. Small pad; 201. Second mounting hole; 202. Second mounting groove;

[0033] 3. Large pad; 301. Third mounting slot;

[0034] 4. Steel ring; 401. First ring conical surface; 402. Second ring conical surface; 403. Ring surface; 404. First settling groove; 405. Bolt; 406. Second settling groove;

[0035] 5. Coolant hose; 501. Nut;

[0036] 6. Heat exchanger;

[0037] 7. Fixing sleeve;

[0038] 8. Adjusting strip;

[0039] 9. Insulation section. Detailed Implementation

[0040] 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.

[0041] 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," unless otherwise specified, include both direct and indirect connections (linkages). In the description of this invention, 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 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.

[0042] 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.

[0043] The following reference Figures 1 to 6 The temperature control device for the six-sided top press provided in the embodiments of the present invention is particularly suitable for six-sided top presses, and of course, it is also applicable to other structures that are pushed by hammers.

[0044] In existing six-sided top presses, the water cooling system is usually located inside the steel ring 4. This cooling method means that the heat generated by the top hammer 1 needs to go through a double heat conduction path to dissipate heat: first, the heat is transferred to the steel ring 4 through the contact surface between the top hammer 1 and the steel ring 4, and then the steel ring 4 conducts the heat to the cooling water channel opened on its ring wall. Finally, the heat is exchanged through the cooling water flowing in the cooling water channel.

[0045] From a heat transfer perspective, this process suffers from significant heat transfer efficiency loss: one factor is the impact of differences in material thermal conductivity; the top hammer 1 is typically made of hard alloy material (thermal conductivity approximately...). Steel ring 4 is mostly made of alloy steel (thermal conductivity approximately...). The thermal conductivity of the two materials differs by approximately 1-2 times, resulting in a significant thermal resistance effect during heat transfer across the material interface. Secondly, there is the influence of contact interface thermal resistance: although the top hammer 1 and steel ring 4 undergo precision grinding during assembly, rough peaks still exist on the contact surface at the microscale, and the actual contact area is only 30%-50% of the nominal area, forming approximately... The contact thermal resistance further hinders heat transfer.

[0046] The direct consequence of this indirect cooling mechanism is that the surface temperature field of the top hammer 1 exhibits a significant non-uniform distribution. Infrared thermal imaging measurements show that the temperature difference between the central and edge regions of the top hammer 1 can reach 80-120℃, severely exceeding the ±15℃ temperature fluctuation range required for the superhard material synthesis process. This lack of temperature stability directly leads to two problems: firstly, reduced synthesis efficiency; during the synthesis of artificial diamond, temperature fluctuations cause instability in the graphite-diamond phase transformation kinetics, reducing the crystal growth rate by 15%-25% and extending the single-furnace synthesis cycle; secondly, uneven product quality; localized overheating areas are prone to graphite residues or diamond crystal defects (such as dislocations and voids). Testing shows that high-quality type Ia diamonds account for only 60%-70% of diamonds produced using traditional cooling methods, a decrease of 15-20 percentage points compared to the ideal state.

[0047] More importantly, this temperature runaway phenomenon has a cumulative effect: under long-term operation, the top hammer 1 will develop fatigue cracks due to repeated thermal expansion and contraction, and its average service life will be shortened from 1,000 synthetic cycles to 600-700 cycles. The steel ring 4 will also suffer from material mechanical property degradation due to local overheating, causing the overall pressure transmission accuracy of the equipment to drop from ±1% to ±3%, forming a vicious cycle of "low heat dissipation efficiency - large temperature fluctuation - short equipment life".

[0048] Based on this, the temperature control device for the six-sided top press provided in this embodiment of the invention includes a coolant pipe 5. The coolant pipe 5 is configured to receive external cold liquid, which can be water, coolant, or refrigerant. During installation, the coolant pipe 5 is inserted into the top hammer 1 and located on the side away from the pushing side of the top hammer 1, ensuring that the pushing action of the top hammer 1 is not affected while maintaining effective heat dissipation for the top hammer 1. Thus, compared to the traditional cooling system that relies on a multi-stage heat transfer path of "top hammer 1 - steel ring 4 - cooling water tank," the method of directly dissipating heat from the top hammer 1 using the coolant pipe 5 significantly reduces energy loss during heat conduction. The core principle is that the external cold liquid, with its high specific heat capacity and forced convection effect, can quickly absorb heat from the top hammer 1 and carry it away from the high-temperature area, forming an efficient heat dissipation cycle.

[0049] Meanwhile, in terms of temperature stability control, the intervention of coolant pipe 5 enables precise regulation of the temperature field of the top hammer 1. Traditional indirect cooling methods, due to heat transfer delays and path losses, easily lead to uneven temperature distribution on the surface of the top hammer 1; while direct heat dissipation, through direct heat exchange between the coolant and the top hammer 1, can balance local heat accumulation in real time, ensuring the uniformity and stability of the temperature field during the synthesis of superhard materials. This temperature control mechanism plays a key role in improving synthesis efficiency and product quality: a stable temperature environment can ensure the consistency of the material phase transformation kinetics process, avoiding abnormal crystal growth rates or lattice defects caused by temperature fluctuations, thus providing a reliable temperature control basis for the industrial synthesis of high-quality superhard materials in principle.

[0050] The temperature control device for the six-sided top press utilizes a six-sided top press comprising six hammer sections. Each hammer section includes a top hammer 1, and each top hammer 1 has a pushing end 101 and a connecting end 102 arranged opposite to each other. The connecting end 102 has a columnar structure. Each connecting end 102 is provided with a small pad 2 and a large pad 3. The small pad 2 has a first frustum section and a first column section arranged coaxially. The diameter of the small end of the first frustum section is equal to the diameter of the connecting end 102 and is coaxially abutting against the connecting end 102. The diameter of the large end of the first frustum section is equal to the diameter of the first column section. The large pad 3 has a second column section, a second frustum section, and a third column section arranged coaxially and sequentially. The diameter of the small end of the second frustum section is equal to the diameter of the second column section. The diameter of the large end of the second frustum section is equal to the diameter of the third column section. The diameter of the second column section is equal to the diameter of the large end of the first frustum section and is coaxially abutting against the large end of the first frustum section.

[0051] A steel ring 4 is detachably fitted onto the top hammer 1, the small pad 2, and the large pad 3. The inner circumferential wall of the steel ring 4 is sequentially configured with a first annular conical surface 401, a second annular conical surface 402, and an annular surface 403 along the axial direction. The first annular conical surface 401 is fitted onto the connecting end 102 during installation, with its small opening and the pushing end 101 located on the same side, forming a stop fit with the top hammer 1 to ensure that the top hammer 1 can be fixed. The second annular conical surface 402 is fitted onto the first frustum section of the small pad 2 during installation, with its small opening and the pushing end 101 located on the same side. On the same side, it forms a stop with the first frustum section of the small pad 2 to ensure that the small pad 2 can be fixed; the annular surface 403 is fitted together with the first column section of the small pad 2 and the second column section of the large pad 3 during installation, and forms a surface contact; multiple first grooves 404 are opened on the outer peripheral wall of the steel ring 4, and the multiple first grooves 404 are arranged circumferentially. A bolt 405 is provided at each first groove 404, and the bolt 405 is threaded into the second column section of the large pad 3 to ensure that the large pad 3 can be fixed.

[0052] To facilitate the installation of the coolant pipe 5, a first mounting groove 103 is provided in the connecting end 102, and two first mounting holes 104 are vertically provided on the end face of the connecting end 102, both of which communicate with the first mounting groove 103. During installation, the coolant pipe 5 is inserted into the first mounting groove 103, with both ends of the coolant pipe 5 extending out of the connecting end 102 through the two first mounting holes 104 respectively. Two second mounting holes 201 are vertically provided on the end face of the first column section of the small pad 2, and two second mounting grooves 202 are provided on the end face of the first column section of the small pad 2, extending radially. Two third mounting grooves are provided on the end face of the second column section of the large pad 3. The mounting groove 301 extends radially and is correspondingly provided to the mounting groove 202. During installation, the coolant pipe 5 extends from the two ends of the two first mounting holes 104 and passes through the two second mounting holes 201 respectively. Then it is clamped by the second mounting groove 202 and the third mounting groove 301 respectively, and the ends of the pipes extend out of the space formed by the second mounting groove 202 and the third mounting groove 301. Two second recesses 406 are provided on the outer peripheral wall of the steel ring 4. The two second recesses 406 are arranged circumferentially. Nuts 501 are threaded onto both ends of the coolant pipe 5. During installation, the nuts 501 stop in the second recesses 406 to ensure that the coolant pipe 5 can be fixed.

[0053] In a further embodiment, when external cold liquid is introduced into the coolant pipe 5, a dynamic heat exchange process is formed. From the perspective of heat conduction principles, the flow of external cold liquid within the coolant pipe 5 is essentially a heat transfer process: the high-temperature region of the top hammer 1 transfers heat to the pipe wall of the coolant pipe 5 through heat conduction, and then the pipe wall exchanges heat with the external cold liquid flowing inside the pipe via convection. During this process, the external cold liquid, as a heat carrier, continuously absorbs the heat transferred by the top hammer 1 as it flows, causing its own temperature to gradually increase. This temperature increase raises a key issue: the driving force for heat exchange comes from the temperature difference. When the external cold liquid flows within the coolant pipe 5, its temperature gradually rises along the flow direction, causing the temperature difference between the cold liquid and the top hammer 1 to gradually decrease. From a thermodynamic perspective, the decrease in temperature difference directly leads to a reduction in heat exchange efficiency—because the amount of heat transferred per unit time is proportional to the temperature difference; the smaller the temperature difference, the slower the rate at which the top hammer 1 transfers heat to the cold liquid.

[0054] Specifically, at the inlet end of the coolant pipe 5, the external coolant temperature is low, creating a significant temperature difference with the high-temperature top hammer 1. At this point, the heat exchange efficiency is high, effectively removing heat from the top hammer 1. However, as the coolant flows towards the outlet end, its temperature continuously increases, and the temperature difference with the top hammer 1 gradually decreases. Near the outlet end, this temperature difference may shrink to near the critical value for heat exchange, leading to a significant decrease in heat dissipation in that area. This phenomenon of temperature difference attenuation along the flow path causes uneven temperature distribution in the top hammer 1 along the coolant pipe 5. Heat dissipation is good near the inlet end, but insufficient heat dissipation near the outlet end may result in locally higher temperatures, thus affecting the stability of the overall temperature field of the top hammer 1.

[0055] Furthermore, the existence of this temperature gradient may trigger a chain reaction: insufficient local heat dissipation will lead to uneven thermal stress distribution in the top hammer 1 material, which may exacerbate fatigue damage to the material under long-term operation; at the same time, for the synthesis process of superhard materials, the non-uniformity of the temperature field will affect the consistency of the phase transformation process, resulting in fluctuations in the performance of the synthesized product.

[0056] Based on this, in the temperature control device of the six-sided top press provided in this embodiment of the invention, a temperature equalization pipe 6 is inserted into each coolant pipe 5, and the temperature equalization pipe 6 is configured to receive an external cold source; the flow direction of the external cold source in the temperature equalization pipe 6 is opposite to the flow direction of the external cold liquid in the coolant pipe 5. Thus, during the cooling process of the top hammer 1, the external cold liquid absorbs heat and rises in temperature along the coolant pipe 5, forming a temperature gradient (low at the inlet, high at the outlet); while the external cold source in the temperature equalization pipe 6 flows in the opposite direction, and its temperature distribution exhibits the characteristic of "high at the inlet, low at the outlet". This reverse flow allows the two media to maintain a large temperature difference at each point along the flow path: at the inlet end of the coolant pipe 5, the high-temperature top hammer 1 undergoes initial heat exchange with the low-temperature external cold liquid, at which point the external cold source in the temperature equalization pipe 6 has just absorbed the heat from the outlet end, and its temperature is relatively high; while at the outlet end of the coolant pipe 5, the temperature of the external cold liquid has increased significantly, and at this point the external cold source in the temperature equalization pipe 6 is exactly the newly introduced low-temperature fluid. Through this reverse configuration, a high average temperature difference is maintained between the coolant pipe 5 and the heat exchange pipe 6 throughout the entire heat exchange process, providing a basis for efficient heat transfer. This reduces the temperature gradient within the coolant pipe 5 while ensuring a large temperature difference between the coolant pipe 5 and the top hammer 1, thereby improving the heat dissipation efficiency of the coolant pipe 5 on the top hammer 1.

[0057] Therefore, a three-stage heat transfer path is constructed: "Top Hammer 1 - Coolant Pipe 5 - Irradiator 6". The heat from Top Hammer 1 is first dissipated through the external coolant in Coolant Pipe 5, and then further cooled by the external cold source in Irradiator 6. Due to the combined effect of counter-flow and spiral structure, Coolant Pipe 5 maintains a large temperature difference with Top Hammer 1. Even if the external coolant temperature rises after absorbing heat along the path, Irradiator 6 can control its temperature within a reasonable range through continuous cooling from the counter-flowing cold source. This mechanism solves the problem of "coolant temperature rise leading to decreased heat dissipation efficiency" in a single cooling channel, enabling Top Hammer 1 to achieve a more uniform and stable heat dissipation effect during high-pressure synthesis.

[0058] Specifically, during installation, the two ends of the heat exchanger 6 penetrate the circumferential sidewalls of both ends of the coolant pipe 5, so as to both receive and discharge external cold sources and fix the heat exchanger 6.

[0059] In a further embodiment, to improve both the ease of assembly of the heat exchanger 6 and the coolant pipe 5 and the heat dissipation efficiency of the coolant pipe 5 on the top hammer 1, the heat exchanger 6 is configured as a spiral structure. Utilizing its spiral characteristics, on the one hand, when the heat exchanger 6 is inserted into the coolant pipe 5, its flexible extension characteristics can adapt to the inner diameter of the coolant pipe 5 with different diameters. Specifically, the radial dimension of the spiral structure can be elastically adjusted within a certain range—when the heat exchanger 6 is inserted into the coolant pipe 5, the outer edge of the spiral ring can dynamically fit against the inner wall of the coolant pipe 5 through slight deformation, achieving coaxial positioning without the need for precise tolerance fitting. This adaptability avoids the assembly jamming or eccentricity problems caused by dimensional deviations in traditional straight-tube pipes, and is particularly suitable for complex installation spaces inside the top hammer 1 (such as vortex-type coolant pipe 5). Furthermore, the axial extension of the spiral structure allows it to naturally extend along the bending path of the coolant pipe 5 during insertion, reducing the operational difficulty during assembly and improving engineering practicality.

[0060] On the other hand, from the perspective of heat transfer theory, the spiral structure optimizes the heat exchange process between the vapor chamber 6 and the external coolant in the following two ways: First, the geometrical enlargement of the contact area: the spiral shape transforms the straight pipe into a spatial spiral, significantly increasing the outer surface area of ​​the pipe within the same axial length. For example, the radial cross-sectional perimeter covered by a spiral pipe per unit length is larger than that of a straight pipe, causing the contact interface between the vapor chamber 6 and the external coolant to expand exponentially. This structural characteristic provides more sites for heat transfer, enhancing the convective heat transfer effect between the two. Second, fluid disturbance and turbulence effect: when the external coolant flows through the spiral vapor chamber 6, its flow trajectory is guided by the spiral structure, generating centrifugal force, which causes the fluid to form spiral turbulence in the coolant pipe 5. The fluid boundary layer thickness is reduced in the turbulent state, and the thermal resistance is reduced, thereby accelerating the heat transfer between the external coolant and the vapor chamber 6. At the same time, the disturbance of the fluid by the spiral structure can avoid the accumulation of local thermal boundary layers, allowing the vapor chamber 6 to absorb heat from the external coolant more uniformly and effectively suppressing the formation of temperature gradients in the coolant pipe 5.

[0061] Therefore, by combining the spiral heat spreader 6 with the counter-flow design, a dynamic thermal balance mechanism is further constructed: when the external coolant heats up along the flow path in the coolant pipe 5, the counter-current cold source in the spiral heat spreader 6 can absorb heat selectively at different axial positions through a larger contact area and turbulence effect—in areas with higher temperatures in the coolant pipe 5 (such as the outlet end), the denser number of spiral turns increases the heat exchange area and enhances heat dissipation; in areas with lower temperatures (such as the inlet end), the sparser number of turns balances the heat exchange intensity. This "on-demand heat dissipation" structural characteristic ensures the uniformity of the temperature field within the coolant pipe 5 in principle, enabling the top hammer 1 to obtain a stable heat dissipation effect throughout the entire area, avoiding the problem of insufficient local heat dissipation caused by the limited contact area of ​​traditional straight pipes.

[0062] In a further embodiment, to improve applicability, multiple fixing sleeves are fixedly fitted onto each heat exchanger tube 6, and the multiple fixing sleeves are arranged circumferentially; each fixing sleeve includes multiple fixing sleeves 7, and the multiple fixing sleeves 7 of the same fixing sleeve are arranged side by side and along the extension direction of the heat exchanger tube 6; each fixing sleeve 7 of each fixing sleeve is fixedly connected to an adjusting strip 8, and the adjusting strip 8 between adjacent fixing sleeves 7 has a V-shaped structure with the opening facing inward. The adjusting strip 8 can be made of a memory material, such as a memory alloy, so that when its own temperature exceeds a preset value, it can reduce the opening size of the V-shaped structure, and the V-shaped structure synchronously passes through the two connected... Each fixed sleeve 7 moves adjacent heat exchanger tubes 6 closer together, increasing the number of turns of the heat exchanger tube 6 corresponding to the high-temperature area of ​​the coolant pipe 5. This increases the heat exchange area between the heat exchanger tube 6 and the high-temperature area within the coolant pipe 5, thereby improving the cooling efficiency of the high-temperature area within the coolant pipe 5. This prevents the local temperature abnormalities in the coolant pipe 5 from worsening and allows time for subsequent flow rate adjustment, improving the yield rate. When its own temperature falls below a preset value, the V-shaped structure automatically recovers, simultaneously moving adjacent heat exchanger tubes 6 away from each other until they reset through the two fixed sleeves 7 connected to it. This avoids affecting the cooling effect of the heat exchanger tube 6 on the external coolant in its corresponding area.

[0063] Meanwhile, with the joint support of the fixed sleeve 7 and the adjusting strip 8, and by utilizing their structural characteristics, the heat exchange pipe 6 can always be located in the central area of ​​the coolant pipe 5, with their axes basically coinciding, thereby ensuring that the heat exchange process proceeds uniformly and stably.

[0064] In a further embodiment, to avoid misalignment and contraction due to rapid temperature rise when the V-shaped structure and the inner wall of the coolant pipe 5 are in direct contact, a heat insulation part 9 is fixedly provided on the outer side of the small end of each V-shaped structure. The heat insulation part 9 is configured to isolate the coolant pipe 5 and the regulating strip 8, so as to build a thermal resistance barrier between the regulating strip 8 and the inner wall of the coolant pipe 5. The heat insulation plate allows the external cold liquid and the regulating strip 8 to exchange heat through convection (i.e., the regulating strip 8 deforms by sensing the temperature change of the external cold liquid), while blocking the solid heat conduction between the coolant pipe 5 wall and the regulating strip 8. This "convective allowed, conduction blocked" mechanism enables the regulating strip 8 to accurately respond to the cold liquid temperature gradient and avoids erroneous actions caused by heat conduction from the coolant pipe 5 wall. Meanwhile, in the local high-temperature area of ​​the coolant pipe 5, the heat insulation part 9 can prevent the regulating bar 8 from shrinking excessively due to the overheating of the pipe wall, ensuring that the position adjustment of the heat exchange pipe 6 is driven only by the coolant temperature rather than the pipe wall temperature, thereby maintaining the heat exchange balance between the heat exchange pipe 6, the coolant pipe 5, and the top hammer 1, and avoiding fluctuations in heat dissipation efficiency caused by the mis-triggering of the regulating bar 8.

[0065] In this specific embodiment, the heat insulation part 9 can be configured as a heat insulation plate and made of heat insulation material, such as ceramic fiber.

[0066] It is understandable that the components that isolate the coolant pipe 5 and the regulating bar 8 can be heat insulation plates, heat insulation bars, heat insulation blocks, or other structures. These structures can be fixedly installed on the regulating bar 8 or detachably connected to the regulating bar 8.

[0067] In other embodiments, the external cold source can be configured as a cooling gas. This allows the high flow rate of the gas to be utilized, ensuring effective heat dissipation from the external coolant.

[0068] Specifically, gases have lower density and viscosity than liquids (such as water or coolant), a characteristic that allows for higher flow velocities within the vapor chamber 6. From a fluid dynamics perspective, high-velocity cooling gas enhances heat exchange through two mechanisms: firstly, it increases the convective heat transfer coefficient. According to heat transfer theory, fluid velocity is positively correlated with the convective heat transfer coefficient. When the cooling gas flows at high speed within the vapor chamber 6, it exerts a stronger scouring effect on the inner wall of the pipe, effectively thinning the fluid boundary layer and reducing thermal resistance. This effect enables the vapor chamber 6 to absorb heat from the external coolant more efficiently, especially in high-temperature areas such as the outlet of the coolant pipe 5, where the high-speed airflow can quickly carry away the accumulated heat, suppressing the formation of temperature gradients. Secondly, the turbulence effect is enhanced: the high flow velocity of the gas easily forms a turbulent state in the heat exchanger tube 6; during turbulent flow, the irregular movement of fluid micro-particles can significantly enhance the lateral heat transfer, making the heat exchange between the heat exchanger tube 6 and the external cold liquid more uniform and sufficient; compared with liquid medium, gas is more likely to reach a turbulent state under the same pipe diameter, thereby improving the heat exchange efficiency without relying on a complex pipe structure.

[0069] Furthermore, when the external cold source uses cooling gas and flows counter-currently to the external coolant, a more efficient heat exchange topology can be constructed: the low specific heat capacity of the cooling gas causes its temperature to rise rapidly after absorbing heat, but its high flow rate ensures a continuous influx of fresh, low-temperature gas into the vapor chamber 6; in the counter-flow configuration, the hotter external coolant in the coolant pipe 5 (e.g., at the outlet) comes into contact with the newly introduced low-temperature gas in the vapor chamber 6, creating a significant temperature difference; while the cooler external coolant in the coolant pipe 5 (e.g., at the inlet) comes into contact with the slightly hotter gas in the vapor chamber 6 after absorbing heat, resulting in a relatively smaller temperature difference; this distribution maximizes the average temperature difference throughout the heat exchange process, ensuring the driving force for heat transfer from a thermodynamic perspective. Moreover, the compressibility of the gas allows for more flexible control of its mass flow rate. By adjusting the gas pressure or flow rate, the heat dissipation requirements of different areas of the top hammer 1 can be matched in real time. In the high-temperature area of ​​the top hammer 1, the gas flow rate is increased to enhance heat dissipation; in the low-temperature area, the flow rate is reduced to balance energy consumption. This dynamic control capability is difficult to achieve with liquid media and is especially suitable for real-time optimization of the temperature field during the synthesis of superhard materials.

[0070] In other embodiments, the external cold source may also be a liquid such as water, coolant, or refrigerant.

[0071] In other embodiments, to facilitate the installation and maintenance of the coolant pipe 5, the top hammer 1 is divided into two parts along the axial direction, and the coolant pipe 5 is inserted between the two parts of the top hammer 1.

[0072] Specifically, the pushing end 101 and the connecting end 102 of the top hammer 1 are set separately. The first mounting groove 103 is opened on the end face of the pushing end 101 facing the connecting end 102 and the end face of the connecting end 102 facing the pushing end 101. In this way, the coolant pipe 5 can be clamped by the two first mounting grooves 103.

[0073] During assembly, firstly, the pushing end 101 and connecting end 102 of the top hammer 1 are separated. Then, the coolant pipe 5 is placed in the first mounting groove 103 on the pushing end 101 for initial positioning. Next, both ends of the coolant pipe 5 are bent to be parallel to the axis of the top hammer 1. Then, the connecting end 102 is moved closer to the pushing end 101, so that the two first mounting grooves 103 clamp the coolant pipe 5 and the two ends of the coolant pipe 5 pass through the two first mounting holes 104 respectively. Then, the small pad 2 is moved closer to the connecting end 102, so that the two ends of the coolant pipe 5 pass through the two first mounting holes 104 respectively. Insert the top hammer 1, coolant pipe 5, and small pad 2 together through the two second mounting holes 201; then insert the top hammer 1, coolant pipe 5, and small pad 2 into the large end of the steel ring 4; then bend both ends of the coolant pipe 5 to be perpendicular to the axis of the top hammer 1, and pass through the circumferential side wall of the steel ring 4, exiting from the second recess 406; then move the large pad 3 close to the small pad 2, and clamp the coolant pipe 5 through the second mounting groove 202 and the third mounting groove 301; then fix the steel ring 4 and the large pad 3 together with bolts 405; finally fix the coolant pipe 5 to the steel ring 4 with nuts 501 to complete the assembly.

[0074] In a further embodiment, due to machining errors in both the first mounting groove 103 and the coolant pipe 5, when the radius of the coolant pipe 5 is larger than the radius of the first mounting groove 103, they form an interference fit. During the assembly process where the push end 101 and the connecting end 102 approach each other, the two first mounting grooves 103 will exert radial extrusion force on the coolant pipe 5. The coolant pipe 5 (usually made of metal) will undergo plastic deformation under extrusion force exceeding its elastic limit. If the extrusion force further exceeds the strength limit, it may cause the coolant pipe 5 to rupture. This damage will directly destroy the integrity of the fluid channel of the coolant pipe 5, reduce or even block the flow cross-section of the external coolant, and thus weaken the heat dissipation capacity of the push hammer 1. In addition, the deformed coolant pipe 5 will form non-uniform contact with the push hammer 1, and local stress concentration may accelerate pipe fatigue failure, affecting the long-term reliability of the system.

[0075] If the radius of the coolant pipe 5 is smaller than the radius of the first mounting groove 103, a gap will be formed between them. After assembly, this gap will be filled with air, and the thermal conductivity of air (approximately...) The temperature difference between the top hammer and the coolant pipe is much lower than that between metal materials, forming a significant thermal resistance barrier. From the perspective of heat transfer principle, the heat of the top hammer 1 needs to be transferred through the path of "top hammer 1-air gap-coolant pipe 5". The presence of the air gap will greatly increase the thermal resistance of heat conduction, resulting in a significant decrease in heat dissipation efficiency. This effect is particularly obvious in the high temperature area of ​​the top hammer 1 - the air in the gap forms natural convection due to heating, but its heat exchange efficiency is still much lower than that of direct contact with solid, which ultimately leads to an increase in the temperature difference between the top hammer 1 and the coolant pipe 5, destroying the uniformity of the temperature field.

[0076] Whether due to interference fit or gaps, both can lead to uneven heat exchange efficiency between the coolant pipe 5 and the top hammer 1, either circumferentially or axially. This uneven heat dissipation causes significant fluctuations in the surface temperature field of the top hammer 1, deviating from the stable temperature range required for the synthesis of superhard materials. This temperature field inhomogeneity can trigger a series of derivative problems: the mechanical properties (such as hardness and strength) of the material in the locally overheated areas of the top hammer 1 will degrade due to high temperatures, accelerating the formation of fatigue cracks; the external coolant in the coolant pipe 5 will experience abrupt changes in flow velocity and temperature distribution when flowing through the deformed or gapped areas, potentially causing fluid vibration or cavitation, further exacerbating pipe damage. Furthermore, the presence of air gaps can also lead to thermal stress between the top hammer 1 and the coolant pipe 5, which may cause loosening of the assembly structure under long-term operation, compromising the pressure transmission accuracy of the equipment.

[0077] Based on this, in the temperature control device of the six-sided top press provided in the embodiments of the present invention, such as Figure 7 As shown, the cross-sectional shape of the heat exchanger 6 can be set to elliptical, and the two relatively convex parts on the heat exchanger 6 are respectively set with the two first mounting grooves 103. In this way, when the pushing end 101 and the connecting end 102 approach each other, the two first mounting grooves 103 can squeeze the heat exchanger 6 into a circle, thereby ensuring close contact between the heat exchanger 6 and the top hammer 1, and ensuring the heat dissipation effect on the top hammer 1.

[0078] In other embodiments, such as Figure 8 As shown, the cross-sectional shape of the heat exchanger 6 can also be set to a quincunx shape, which has multiple convex and concave portions arranged alternately along the circumference, and one of the convex portions of the heat exchanger 6 is correspondingly arranged with one of the first mounting grooves 103. In this way, as the pushing end 101 and the connecting end 102 approach each other, the two first mounting grooves 103 can squeeze the heat exchanger 6 into a circle, thereby ensuring close contact between the heat exchanger 6 and the top hammer 1, and ensuring the heat dissipation effect on the top hammer 1.

[0079] In other embodiments, to improve the heat dissipation effect of the coolant pipe 5 on the top hammer 1, the portion of the coolant pipe 5 inside the top hammer 1 is configured to have a spiral shape. Thus, while keeping the end face area of ​​the connection end 102 unchanged, the geometric characteristics of the spiral shape can effectively increase the number of coils in the coolant pipe 5, thereby fundamentally solving the technical problem of maximizing the heat dissipation path within a limited space.

[0080] Specifically, the vortex curve, as a special type of planar curve, follows the generation rule of "spiral extension from the center outward with a gradually increasing radius of curvature." Compared with the traditional concentric circle structure, its core advantage lies in the fact that, under the same end-face boundary conditions (i.e., the end-face area of ​​the connecting end 102 is fixed), the vortex curve can form a longer curve length with a more compact layout. Specifically, the polar coordinate equation of the vortex curve (such as Archimedean vortex ρ=αθ) determines that its radius increases linearly with the angle. This geometric characteristic allows the pipe to achieve a spatial arrangement of "increasing number of turns without overlap" within a finite plane. For example, when the end-face of the connecting end 102 is circular, the vortex-type coolant pipe 5 can start from the center and extend outward in a spiral manner, with a uniform radius increment for each turn, ensuring that more turns are made within a finite radial distance. This transforms the one-dimensional heat dissipation path of the straight pipe into a spiral extension in a two-dimensional plane, breaking through the path length limitations of traditional straight pipes or concentric circle pipes from a geometric perspective.

[0081] Meanwhile, the heat dissipation capacity of the coolant pipe 5 is positively correlated with the contact area between the pipe wall and the top hammer 1. Specifically, the vortex-shaped coolant pipe 5 significantly expands the contact interface between the pipe wall and the top hammer 1 within the same axial length by increasing the number of coils. For example, the total length of the vortex-shaped pipe can be several times greater than that of a straight pipe per unit end face area, and the corresponding contact area also increases proportionally, allowing the heat from the top hammer 1 to be transferred to the coolant pipe 5 through a larger interface, thus enhancing heat transfer efficiency.

[0082] Furthermore, the increased flow path of the external coolant within the vortex-shaped pipe leads to a longer residence time within the top hammer 1. Specifically, according to heat exchange theory, the longer the fluid residence time, the more thorough the heat exchange with the pipe wall. The vortex structure, by extending the flow path, allows the low-temperature external coolant more time to absorb heat from the top hammer 1, especially in the high-temperature region of the top hammer 1 (such as the area near the pusher end 101). The longer coiling path ensures sufficient contact between the coolant and the high-temperature region, avoiding incomplete heat dissipation due to excessively high flow rates.

[0083] More specifically, to facilitate the installation of the coolant pipe 5, the shape of the first mounting groove 103 is correspondingly set as a spiral line.

[0084] In a further embodiment, to improve the heat dissipation effect of the coolant pipe 5 on the top hammer 1, the flow direction of the external coolant within the top hammer 1 is set from the inner end of the vortex to the outer end. Thus, the external coolant exhibits a gradient characteristic of "low temperature in the middle and high temperature at the outer periphery" within the coolant pipe 5, while the temperature distribution of the top hammer 1 typically exhibits a gradient characteristic of "high temperature in the middle and low temperature at the outer periphery." When the external coolant flows, it first flows through the high-temperature inner zone, absorbing a large amount of heat before flowing to the low-temperature outer zone. This sequence of "heat exchange in the high-temperature zone first, heat exchange in the low-temperature zone later" naturally matches the temperature gradient of the top hammer 1, avoiding the problem of "insufficient heat dissipation in the high-temperature zone and excessive cooling in the low-temperature zone" caused by the fixed flow direction in traditional straight pipes.

[0085] In other embodiments, both the coolant pipe 5 and the heat exchanger 6 may be made of copper.

[0086] 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.

[0087] The above-described embodiments 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.

Claims

1. A temperature control device for a six-sided top press, characterized in that, The temperature control device of the six-sided top press is applied to the six-sided top press, which includes six top hammers. Each top hammer is provided with a small pad and a large pad. A steel ring is detachably fitted onto each top hammer, the small pad, and the large pad. The temperature control device of the six-sided top press includes a coolant pipe. Each top hammer is inserted with a coolant pipe. Both ends of the coolant pipe pass through the small pad and are detachably mounted on the steel ring. The coolant pipe is configured to receive external cold liquid. Each of the coolant pipes is fitted with a temperature distribution tube, which is configured to receive an external cold source; the flow direction of the external cold source in the temperature distribution tube is opposite to the flow direction of the external coolant in the coolant pipe; the temperature distribution tube has a spiral structure. Each of the heat exchange tubes is fixedly fitted with multiple fixed sleeves, which are arranged circumferentially. Each fixed sleeve includes multiple fixed sleeves, which are arranged along the extension direction of the heat exchange tube. Each fixed sleeve is fixedly connected with an adjusting strip. The adjusting strip between adjacent fixed sleeves has a V-shaped structure with its opening facing inward. The adjusting strip is configured to reduce the opening size of the V-shaped structure when its temperature exceeds a preset value. The V-shaped structure simultaneously drives adjacent heat exchange tubes closer together through the two fixed sleeves it is connected to. When its temperature falls below the preset value, it automatically returns to its original position. Meanwhile, with the joint support of the fixed sleeves and adjusting strips, the heat exchange tube is always located in the central area of ​​the coolant tube, with its axis basically coinciding, thus ensuring a uniform and stable heat exchange process.

2. The temperature control device for the six-sided top press according to claim 1, characterized in that, Each of the V-shaped structures has a heat insulation part fixedly provided on the outer side of the small end, and the heat insulation part is configured to isolate the coolant pipe and the regulating bar.

3. The temperature control device for the six-sided top press according to claim 1, characterized in that, The external cold source is cooling gas.

4. The temperature control device for the six-sided top press according to claim 1, characterized in that, The top hammer is divided into two parts along the axial direction, and the coolant pipe is inserted between the two parts of the top hammer.

5. The temperature control device for the six-sided top press according to claim 1, characterized in that, The portion of the coolant pipe inside the top hammer has a vortex-like shape.

6. The temperature control device for the six-sided top press according to claim 5, characterized in that, The external coolant flows in the top hammer from the inner end of the vortex to the outer end of the vortex.

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