An ultrahigh-pressure hot sleeve body and an ultrahigh-pressure vessel

Abstract

The application relates to an ultrahigh-pressure hot sleeve body and an ultrahigh-pressure container, and relates to the technical field of high-pressure container design.The application comprises an inner layer sleeve body which is an integrated structure; a middle layer sleeve body which is sleeved outside the inner layer sleeve body, the middle layer sleeve body comprising a plurality of arc-shaped plates which are arranged along the circumference of the inner layer sleeve body, the centers of the arc-shaped plates coinciding with the center of the inner layer sleeve body; and an outer layer sleeve body which is sleeved outside the middle layer sleeve body, the outer layer sleeve body comprising a plurality of annular rings which are arranged along the axial direction of the inner layer sleeve body, the centers of the annular rings coinciding with the centers of the arc-shaped plates. The application solves the problem that, for large-diameter ultrahigh-pressure containers, the thickness of the single-layer forged piece after division is still relatively large, may exceed the forming capacity limit of the existing forging equipment of a manufacturing factory, and in the forging and subsequent heat treatment processes, due to the excessively large cross-section thickness of the forged piece, there is a significant temperature gradient between the core and the surface layer, which may cause the mechanical properties of the core and the surface layer of the forged piece to be seriously uneven, and there is a problem that it is difficult to manufacture and it is difficult to produce qualified products.

Description

Technical Field

[0001] This invention relates to the field of high-pressure vessel design technology, specifically to an ultra-high pressure thermal sleeve and an ultra-high pressure vessel. Background Technology

[0002] Ultra-high pressure vessels are pressure vessels designed for pressures greater than or equal to 100 MPa, and are widely used in ultra-high pressure synthesis, isostatic pressing, energy storage, and national defense. With the development of industrial technology, the diameter requirements for ultra-high pressure vessels are becoming larger and larger, while the working pressure is also constantly increasing, which poses extremely high challenges to the manufacturing of the vessel's shell, end structure, and sealing performance.

[0003] In existing technologies, the double-layer hot-sleeving structure is a widely adopted technical solution to address the difficulties in manufacturing single-layer thick-walled forgings. This structure typically consists of an inner cylinder and an outer cylinder. Utilizing the principle of thermal expansion and contraction of materials, the outer cylinder is heated and expanded before being fitted into the inner cylinder. After cooling, an interference fit generates pre-tightening stress between the layers, thereby improving the overall load-bearing capacity of the container. Compared to single-layer integral forging structures, the double-layer hot-sleeving structure reduces the thickness requirements of individual forgings to a certain extent, improves the stress distribution of the material, and is suitable for manufacturing medium-diameter and medium-to-high-pressure containers.

[0004] However, as pressure requirements continue to increase, the thickness of the single layer required for the double-layer heat-shrink structure also needs to be increased accordingly. For large-diameter ultra-high pressure vessels, the thickness of the single-layer forging after distribution is often still large, which may exceed the forming capacity limit of the manufacturer's existing forging equipment. Furthermore, during forging and subsequent heat treatment, due to the excessive thickness of the forging cross section, there is a significant temperature gradient between the core and the surface layer, which may cause serious unevenness in the mechanical properties of the core and the surface layer of the forging. All of these issues present challenges in manufacturing and make it difficult to produce qualified products. Summary of the Invention

[0005] This application provides an ultra-high pressure hot jacket and an ultra-high pressure vessel, which can solve the problem that in the prior art, as the pressure index continues to increase, the single-layer thickness required for the double-layer hot jacket structure also needs to be increased accordingly. For large-diameter ultra-high pressure vessels, the thickness of the single-layer forging after distribution is often still large, which may exceed the forming capacity limit of the manufacturer's existing forging equipment. Furthermore, during the forging and subsequent heat treatment processes, due to the excessive thickness of the forging cross-section, there is a significant temperature gradient between the core and the surface layer, which may cause serious unevenness in the mechanical properties of the core and the surface layer of the forging. All of these issues result in high manufacturing difficulty and make it difficult to produce qualified products.

[0006] In a first aspect, embodiments of this application provide an ultra-high pressure thermal sleeve, which includes: The inner cylindrical body is a one-piece molded structure; A middle layer cylinder is sleeved on the outside of the inner layer cylinder. The middle layer cylinder includes a plurality of arc-shaped plates arranged along the circumference of the inner layer cylinder, and the center of the arc-shaped plates coincides with the inner layer cylinder. The outer cylinder is sleeved on the outside of the middle cylinder. The outer cylinder includes a plurality of rings arranged along the axial direction of the inner cylinder, and the center of the rings coincides with the center of the arc plate.

[0007] In one embodiment, the middle layer cylinder and the outer layer cylinder have the same length in the axial direction, the inner layer cylinder has a shorter length in the axial direction than the middle layer cylinder, and both ends of the inner layer cylinder are provided with sealing mechanisms. The sealing mechanisms are located inside the middle layer cylinder and are used to cooperate with the inner layer cylinder, the middle layer cylinder and the outer layer cylinder to form a cavity.

[0008] In one embodiment, the inner side of the middle cylinder is provided with a connecting groove, and the sealing mechanism includes: A sealing cap is disposed at the end of the inner cylinder and extends partially into the inner cylinder; A shearing ring is located on the side of the sealing cap away from the inner cylinder. The shearing ring is engaged in the connecting groove. The shearing ring and the sealing cap abut against each other, and the contact surface between the shearing ring and the sealing cap is an inclined surface. If the sealing cap moves away from the inner cylinder, the shearing ring moves into the connecting groove.

[0009] In one embodiment, the sealing mechanism further includes an installation assembly comprising a plurality of installation screws passing through the shear ring, the middle cylinder, and the outer cylinder. The installation screws are provided with two spaced-apart installation nuts, which respectively abut against the inner side of the shear ring and the outer side of the outer cylinder.

[0010] In one embodiment, the mounting assembly further includes a hydraulic drive located inside the shear ring and connected to the sealing cap. The hydraulic drive is connected to all mounting screws and is used to drive the mounting screws to move radially along the middle cylinder, so that the shear ring abuts against the connecting groove.

[0011] In one embodiment, all arc-shaped plates are provided with the connecting groove, and the shearing ring includes arc-shaped units corresponding to the arc-shaped plates one by one, and the arc-shaped units are engaged in the connecting groove of the corresponding arc-shaped plates.

[0012] In one embodiment, the sealing cap includes a large-diameter section and a small-diameter section. The large-diameter section is disposed at the end of the inner cylinder, and the outer diameter of the large-diameter section is larger than the inner diameter of the inner cylinder and matches the inner diameter of the middle cylinder. The small-diameter section extends into the inner cylinder.

[0013] In one embodiment, the end of the small-diameter section extending into the inner cylinder is provided with a mounting groove, the mounting groove being located outside the small-diameter section, and a sealing assembly is provided within the mounting groove, the sealing assembly comprising: A triangular pad is provided on the inclined surface at the bottom of the mounting groove, and one of the right-angled sides of the triangular pad abuts against the inner side of the inner cylinder. A sealing ring is disposed within the mounting groove and located on the side of the triangular pad away from the large diameter section, the sealing ring being used to abut against the other right-angled side of the triangular pad.

[0014] In one embodiment, the sealing assembly further includes a retaining ring located on the side of the sealing ring away from the triangular gasket, the side of the retaining ring away from the sealing ring being flush with the end of the small-diameter section extending into the inner cylinder.

[0015] Secondly, embodiments of this application also provide an ultra-high pressure vessel, which includes the aforementioned ultra-high pressure thermal sleeve.

[0016] The beneficial effects of the technical solutions provided in this application include: In designing this ultra-high pressure hot jacket, the inner jacket is a one-piece structure, with the middle jacket fitted over it. The middle jacket includes multiple arc-shaped plates arranged circumferentially around the inner jacket, the centers of which coincide with the centers of the inner jacket. The outer jacket is fitted over the middle jacket, and includes multiple rings arranged axially around the inner jacket, the centers of which coincide with the centers of the arc-shaped plates. By decomposing the jacket wall thickness into three layers—inner, middle, and outer—specifically, by using multiple circumferentially arranged arc-shaped plates to splice the middle jacket and multiple axially arranged rings to stack the outer jacket, this design breaks down the traditional ultra-high pressure vessel's requirement for an ultra-thick, large-diameter integral forging into multiple smaller, smaller independent forgings. The dimensions and thickness of individual arc plates and rings can be controlled within the forming capacity of existing forging equipment. Furthermore, due to the significantly reduced thickness of the middle arc plate and outer ring, the temperature gradient between the core and surface of the forging cross-section is greatly reduced during forging and subsequent heat treatment. This avoids defects such as coarse grains, uneven microstructure, and insufficient density in the core caused by inconsistent cooling rates in thick-walled forgings. It ensures the uniformity and compliance rate of the mechanical properties of each layer of the cylinder material. It also solves the problem in existing technologies where, as pressure parameters continue to increase, the required single-layer thickness of the double-layer heat-shrink structure also needs to increase synchronously. For large-diameter ultra-high-pressure vessels, the distributed single-layer forging thickness is often still large, potentially exceeding the forming capacity limit of the manufacturer's existing forging equipment. Moreover, during forging and subsequent heat treatment, the excessive thickness of the forging cross-section creates a significant temperature gradient between the core and surface, potentially causing severe inhomogeneity in the mechanical properties of the forging core and surface, all of which present manufacturing difficulties and make it hard to produce qualified products. Attached Figure Description

[0017] To more clearly illustrate the technical solutions in the embodiments of this application, the accompanying drawings used in the description of the embodiments will be briefly introduced below. Obviously, the accompanying drawings described below are only some embodiments of this application. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0018] Figure 1 This is a schematic diagram of an embodiment of an ultra-high pressure thermal sleeve of the present invention.

[0019] Figure 2 This is a schematic cross-sectional view of an embodiment of an ultra-high pressure thermal sleeve according to the present invention.

[0020] Figure 3 This is a schematic diagram of the sealing mechanism in an embodiment of an ultra-high pressure thermal sleeve of the present invention.

[0021] Figure 4 This is a schematic diagram of the sealing component in an embodiment of an ultra-high pressure thermal sleeve of the present invention.

[0022] In the diagram: 1. Inner cylinder; 2. Middle cylinder; 21. Arc plate; 3. Outer cylinder; 31. Circular ring; 4. Sealing mechanism; 41. Sealing cover; 42. Shear ring; 43. Mounting assembly; 431. Mounting screw; 432. Mounting nut; 433. Hydraulic drive component; 5. Sealing assembly; 51. Triangular washer; 52. Sealing ring; 53. Retaining ring; 6. Cover. Detailed Implementation

[0023] To enable those skilled in the art to better understand the present application, the technical solutions in the embodiments of the present application will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present application, and not all embodiments. Based on the embodiments in the present application, all other embodiments obtained by those of ordinary skill in the art without creative effort are within the scope of protection of the present application.

[0024] This application provides an ultra-high pressure hot jacket and an ultra-high pressure vessel, which can solve the problem that in the prior art, as the pressure index continues to increase, the single-layer thickness required for the double-layer hot jacket structure also needs to increase accordingly. For large-diameter ultra-high pressure vessels, the thickness of the single-layer forging after distribution is often still large, which may exceed the forming capacity limit of the manufacturer's existing forging equipment. Furthermore, during the forging and subsequent heat treatment processes, due to the excessive thickness of the forging cross-section, there is a significant temperature gradient between the core and the surface layer, which may cause serious unevenness in the mechanical properties of the core and the surface layer of the forging. All of these problems result in high manufacturing difficulty and difficulty in producing qualified products.

[0025] like Figure 1 and Figure 2 As shown, in one aspect, this application provides an ultra-high pressure thermal sleeve, which includes: The inner cylinder 1 is a one-piece molded structure; The middle layer cylinder 2 is sleeved on the outside of the inner layer cylinder 1. The middle layer cylinder 2 includes a plurality of arc-shaped plates 21 arranged around the inner layer cylinder 1, and the center of the arc-shaped plates 21 coincides with the inner layer cylinder 1. The outer cylinder 3 is sleeved on the outside of the middle cylinder 2. The outer cylinder 3 includes a plurality of rings 31 arranged along the axial direction of the inner cylinder 1. The center of the rings 31 coincides with the center of the arc plate 21.

[0026] In designing this ultra-high pressure hot jacket, the inner cylinder 1 is a one-piece molded structure. The middle cylinder 2 is fitted outside the inner cylinder 1. The middle cylinder 2 includes multiple arc-shaped plates 21 arranged circumferentially along the inner cylinder 1, with the center of the arc-shaped plates 21 coinciding with the center of the inner cylinder 1. The outer cylinder 3 is fitted outside the middle cylinder 2. The outer cylinder 3 includes multiple rings 31 arranged axially along the inner cylinder 1, with the center of the rings 31 coinciding with the center of the arc-shaped plates 21. By decomposing the cylinder wall thickness into three layers—inner, middle, and outer—specifically, by using multiple arc-shaped plates 21 arranged circumferentially to splice the middle cylinder 2, and by using multiple rings 31 arranged axially to stack the outer cylinder 3, this design decomposes the ultra-thick, large-diameter integral forgings required by traditional ultra-high pressure vessels into multiple independent forgings with smaller thicknesses and dimensions. The dimensions and thickness of individual arc-shaped plates 21 and rings 31 can be controlled within the forming capacity range of existing forging equipment. Furthermore, due to the significantly reduced thickness of the middle arc-shaped plate 21 and the outer ring 31, the temperature gradient between the core and surface of the forging cross-section is greatly reduced during forging and subsequent heat treatment. This avoids defects such as coarse grains, uneven microstructure, and insufficient density in the core caused by inconsistent cooling rates in thick-walled forgings. It ensures the uniformity and compliance rate of the mechanical properties of each layer of the cylinder material. It also solves the problem in existing technologies where, as pressure parameters continue to increase, the required single-layer thickness of the double-layer heat-shrink structure also needs to increase synchronously. For large-diameter ultra-high-pressure vessels, the distributed single-layer forging thickness is often still large, potentially exceeding the forming capacity limit of the manufacturer's existing forging equipment. Moreover, during forging and subsequent heat treatment, the excessive thickness of the forging cross-section creates a significant temperature gradient between the core and surface, potentially causing severe inhomogeneity in the mechanical properties of the forging core and surface, all of which present manufacturing difficulties and make it hard to produce qualified products.

[0027] like Figure 1 and Figure 2 As shown, in some optional embodiments, the middle layer cylinder 2 and the outer layer cylinder 3 have the same length in the axial direction, the inner layer cylinder 1 has a shorter length in the axial direction than the middle layer cylinder 2, and both ends of the inner layer cylinder 1 are provided with sealing mechanisms 4. The sealing mechanisms 4 are located inside the middle layer cylinder 2 and are used to cooperate with the inner layer cylinder 1, the middle layer cylinder 2 and the outer layer cylinder 3 to form a cavity.

[0028] In this embodiment, the middle layer cylinder 2 and the outer layer cylinder 3 have the same axial length, while the inner layer cylinder 1 has a shorter axial length than the middle layer cylinder 2. Sealing mechanisms 4 are provided at both ends of the inner layer cylinder 1, located inside the middle layer cylinder 2. These sealing mechanisms 4 work together with the inner layer cylinder 1, middle layer cylinder 2, and outer layer cylinder 3 to form a cavity. The shorter axial length of the inner layer cylinder 1 compared to the middle and outer layers creates a stepped installation space between the ends of the inner layer cylinder 1 and the ends of the middle layer cylinder 2. This space is specifically designed to accommodate the sealing mechanisms 4, avoiding an increase in the overall length of the inner layer cylinder for their installation. The sealing mechanisms 4 are located within the axial coverage area of ​​the middle layer cylinder 2 and the outer layer cylinder 3, effectively placing the crucial sealing mechanism 4 inside the multi-layer cylinder. Under ultra-high pressure conditions, this layout not only prevents the sealing mechanism 4 from being subjected to external mechanical impact or damage, but also, in the event of a leak due to seal failure, uses the middle and outer cylinders as a barrier to prevent the high-pressure medium from being directly sprayed outward, thus playing a secondary containment safety protection role and greatly improving the safety of equipment operation.

[0029] like Figure 1 and Figure 3 As shown, in some optional embodiments, the inner side of the middle cylinder 2 is provided with a connecting groove, and the sealing mechanism 4 includes: A sealing cap 41 is disposed at the end of the inner cylinder 1 and extends partially into the inner cylinder 1; The shear ring 42 is located on the side of the sealing cover 41 away from the inner cylinder 1. The shear ring 42 is engaged in the connecting groove. The shear ring 42 and the sealing cover 41 abut against each other, and the contact surface between the shear ring 42 and the sealing cover 41 is an inclined surface. If the sealing cover 41 moves away from the inner cylinder 1, the shear ring 42 moves into the connecting groove.

[0030] In this embodiment, a connecting groove is provided on the inner side of the middle cylinder 2. The sealing mechanism 4 includes a sealing cap 41 and a shear ring 42. The sealing cap 41 is located at the end of the inner cylinder 1 and partially extends into the inner cylinder 1. The shear ring 42 is located on the side of the sealing cap 41 away from the inner cylinder 1. The shear ring 42 is engaged in the connecting groove, and the shear ring 42 and the sealing cap 41 abut against each other. The contact surface between the shear ring 42 and the sealing cap 41 is an inclined surface. If the sealing cap 41 moves away from the inner cylinder 1, the shear ring 42 moves into the connecting groove. Through the inclined surface fit design between the sealing cap 41 and the shear ring 42, the axial thrust generated by the pressure of the medium inside the container is cleverly converted into the radial expansion force of the shear ring 42. When the pressure inside the container increases, the tendency of the sealing cap 41 to move away from the inner cylinder increases, thereby pushing the shear ring 42 to be more tightly engaged in the connecting groove of the middle cylinder 2. This self-tightening sealing mechanism, which tightens with increasing pressure, effectively overcomes the shortcomings of traditional bolted connections that are prone to loosening and leakage under ultra-high pressure conditions, ensuring the sealing stability of the container under extreme pressure fluctuations. The shear ring 42, positioned within the connecting groove on the inner side of the middle cylinder 2, allows a significant portion of the axial force borne by the sealing cover 41 to be directly transmitted to the middle cylinder 2 via the shear ring 42, which is then constrained by the outer cylinder 3.

[0031] In this example, a cover 6 is also provided on the outside of the sealing mechanism 4. The side of the cover 6 away from the sealing mechanism 4 is flush with the ends of the middle cylinder 2 and the outer cylinder 3.

[0032] like Figure 1 and Figure 3 As shown, in some optional embodiments, the sealing mechanism 4 further includes an installation assembly 43, which includes a plurality of installation screws 431. The installation screws 431 pass through the shear ring 42, the middle cylinder 2 and the outer cylinder 3. The installation screws 431 are provided with two spaced-apart installation nuts 432, which abut against the inner side of the shear ring 42 and the outer side of the outer cylinder 3, respectively.

[0033] In this embodiment, the sealing mechanism 4 further includes an installation component 43, which includes multiple installation screws 431. The installation screws 431 pass through the shear ring 42, the middle cylinder 2, and the outer cylinder 3. Each installation screw 431 has two spaced-apart installation nuts 432, which abut against the inner side of the shear ring 42 and the outer side of the outer cylinder 3, respectively. Through the cooperation of the installation screws 431 and the two installation nuts 432, a pre-tightening force can be applied to the shear ring 42, ensuring it is tightly locked into the connecting groove of the middle cylinder 2 even when the container is not pressurized or under low pressure. This compensates for the insufficient clamping force of the self-tightening sealing structure during low-pressure stages, ensuring the initial sealing performance of the container during startup, pressure testing, and low-pressure operation, and eliminating the risk of leakage during pressurization. The mounting screw 431 passes through the shear ring 42, the middle cylinder 2 and the outer cylinder 3, connecting the end sealing mechanism 4 with the multi-layer structure of the cylinder. This connection method allows the end load to be transmitted more evenly to the outer cylinder 3, enhances the positional stability of the end structure relative to the main body of the cylinder, prevents the sealing mechanism from axial movement or skew due to pressure fluctuations or external vibrations, and improves the overall stability of the container operation.

[0034] like Figure 3 As shown, in some optional embodiments, the mounting assembly 43 further includes a hydraulic drive 433 located inside the shear ring 42 and connected to the sealing cap 41. The hydraulic drive 433 is connected to all mounting screws 431 and is used to drive the mounting screws 431 to move radially along the middle cylinder 2, so that the shear ring 42 is held against the connecting groove.

[0035] In this embodiment, the mounting assembly 43 further includes a hydraulic drive component 433, located inside the shear ring 42 and connected to the sealing cap 41. The hydraulic drive component 433 is connected to all mounting screws 431 and drives the mounting screws 431 to move radially along the middle cylinder 2, causing the shear ring 42 to abut against the connecting groove. By actively driving the mounting screws 431 radially with the hydraulic drive component 433, sufficient initial interference fit is established between the shear ring 42 and the connecting groove of the middle cylinder 2 before the container is pressurized. This dual protection mechanism of active pre-tightening and passive self-tightening minimizes the risk of end seal failure in ultra-high pressure vessels under low pressure or no-load conditions. Furthermore, the hydraulic drive component 433, connected to all mounting screws 431, can synchronously drive multiple mounting screws 431 radially. Compared to manually tightening nuts one by one, hydraulic drive ensures that the expansion force on the shear ring 42 is highly uniform in the circumferential direction.

[0036] In this example, the hydraulic drive 433 includes a hydraulic pump and a hydraulic rod corresponding to the mounting screw 431. The hydraulic pump drives the mounting screw 431 to move radially by controlling the extension and retraction of the hydraulic rod.

[0037] In some optional embodiments, all arc plates 21 are provided with connecting grooves, and the shear ring 42 includes arc units corresponding to the arc plates 21, with the arc units being engaged in the connecting grooves of the corresponding arc plates 21.

[0038] In this embodiment, all arc-shaped plates 21 are provided with connecting grooves, and the shear ring 42 includes arc-shaped units corresponding to the arc-shaped plates 21 one by one. The arc-shaped units are locked in the connecting grooves of the corresponding arc-shaped plates 21. The shear ring 42 adopts a segmented structure corresponding to the arc-shaped plates 21 of the middle layer cylinder 2, so that the force-bearing unit of the shear ring 42 is perfectly matched with the support unit of the middle layer cylinder 2. This avoids the stress concentration phenomenon caused by structural discontinuity when the integral shear ring 42 crosses the splice seam of the arc-shaped plates 21, prevents the risk of deformation or breakage of the shear ring 42 due to a sudden change in stiffness at the splice seam, and ensures the structural integrity of the end locking structure. Compared with the integral shear ring 42, which requires large deformation expansion to fit into the middle layer cylinder 2, the segmented arc-shaped units can be independently installed into the corresponding connecting grooves. This design significantly reduces the interference requirements during the assembly process, avoids surface scratches or dimensional damage caused by forced assembly, simplifies the assembly process, and improves assembly efficiency and yield.

[0039] like Figure 1 and Figure 3 As shown, in some optional embodiments, the sealing cap 41 includes a large-diameter section and a small-diameter section. The large-diameter section is disposed at the end of the inner cylinder 1. The outer diameter of the large-diameter section is larger than the inner diameter of the inner cylinder 1 and matches the inner diameter of the middle cylinder 2. The small-diameter section extends into the inner cylinder 1.

[0040] In this embodiment, the sealing cap 41 includes a large-diameter section and a small-diameter section. The large-diameter section is located at the end of the inner cylinder 1, and its outer diameter is larger than the inner diameter of the inner cylinder 1, matching the inner diameter of the middle cylinder 2. The small-diameter section extends into the inner cylinder 1. The small-diameter section of the sealing cap 41, extending into the inner cylinder 1, combined with the structure of the large-diameter section matching the inner diameter of the middle cylinder 2, forms a dual radial support system of internal and external positioning. The small-diameter section prevents the sealing cap 41 from shifting inward, and the large-diameter section prevents it from shifting outward. This bidirectional constraint ensures that the sealing cap 41 is coaxial with the cylinder axis. Under ultra-high pressure conditions, this effectively avoids excessively high or low unilateral sealing pressure caused by the misalignment of the sealing cap 41, preventing sealing failure and component wear.

[0041] like Figure 3 and Figure 4 As shown, in some optional embodiments, the end of the small-diameter section extending into the inner cylinder 1 is provided with a mounting groove, the mounting groove being located outside the small-diameter section, and a sealing assembly 5 is provided within the mounting groove. The sealing assembly 5 includes: A triangular pad 51 is provided on the inclined surface at the bottom of the mounting groove, and one right-angled side of the triangular pad 51 abuts against the inner side of the inner cylinder 1. The sealing ring 52 is disposed in the mounting groove and located on the side of the triangular pad 51 away from the large diameter section. The sealing ring 52 is used to abut against the other right-angle side of the triangular pad 51.

[0042] In this embodiment, an installation groove is provided at the end of the small-diameter section extending into the inner cylinder 1. The installation groove is located outside the small-diameter section, and a sealing assembly 5 is provided inside the installation groove. The sealing assembly 5 includes a triangular pad 51 and a sealing ring 52. The triangular pad 51 is disposed on the inclined surface at the bottom of the installation groove, and one right-angled side of the triangular pad 51 abuts against the inner side of the inner cylinder 1. The sealing ring 52 is disposed inside the installation groove and is located on the side of the triangular pad 51 away from the large-diameter section. The sealing ring 52 abuts against the other right-angled side of the triangular pad 51. Through the combination of the sealing ring 52 and the triangular pad 51, during the initial pressurization or low-pressure stage of the container, the sealing ring 52 provides the initial sealing specific pressure by its own elastic deformation to prevent media leakage. During the ultra-high pressure stage, the triangular pad 51 bears the main load and deforms to fill the microscopic gaps. This design overcomes the defect of a single elastic sealing ring being prone to extrusion failure under ultra-high pressure and achieves reliable sealing across the entire pressure range. When the internal pressure increases, the medium pressure acts on the sealing ring 52, which in turn pushes the triangular pad 51 so that its right-angled side presses more tightly against the inner cylinder wall. This structure uses the medium pressure itself as the sealing power source, achieving a self-tightening sealing effect where the sealing specific pressure automatically increases with the increase of the medium pressure, significantly improving the sealing safety under ultra-high pressure conditions.

[0043] like Figure 3 and Figure 4 As shown, in some optional embodiments, the sealing assembly 5 further includes a retaining ring 53, which is located on the side of the sealing ring 52 away from the triangular pad 51, and the side of the retaining ring 53 away from the sealing ring 52 is flush with the end of the small diameter section that extends into the inner cylinder 1.

[0044] In this embodiment, the sealing assembly 5 also includes a retaining ring 53, which is located on the side of the sealing ring 52 away from the triangular gasket 51. The side of the retaining ring 53 away from the sealing ring 52 is flush with the end of the small-diameter section extending into the inner cylinder 1. Under ultra-high pressure conditions, the sealing ring 52 is easily squeezed into the mating gap due to excessive pressure, resulting in shear fracture. The retaining ring 53, located on the side of the sealing ring 52 away from the triangular gasket 51, provides a rigid axial support backing for the sealing ring 52. When the medium pressure rises sharply, the retaining ring 53 effectively prevents the plastic flow of the sealing ring 52 towards the gap, ensuring the structural integrity of the sealing ring 52 under ultra-high pressure conditions and significantly extending the service life of the sealing assembly.

[0045] like Figure 1 and Figure 2 As shown, on the other hand, this application also provides an ultra-high pressure vessel, which includes the aforementioned ultra-high pressure thermal sleeve.

[0046] In designing this ultra-high pressure hot jacket, the inner cylinder 1 is a one-piece molded structure. The middle cylinder 2 is fitted outside the inner cylinder 1. The middle cylinder 2 includes multiple arc-shaped plates 21 arranged circumferentially along the inner cylinder 1, with the center of the arc-shaped plates 21 coinciding with the center of the inner cylinder 1. The outer cylinder 3 is fitted outside the middle cylinder 2. The outer cylinder 3 includes multiple rings 31 arranged axially along the inner cylinder 1, with the center of the rings 31 coinciding with the center of the arc-shaped plates 21. By decomposing the cylinder wall thickness into three layers—inner, middle, and outer—specifically, by using multiple arc-shaped plates 21 arranged circumferentially to splice the middle cylinder 2, and by using multiple rings 31 arranged axially to stack the outer cylinder 3, this design decomposes the ultra-thick, large-diameter integral forgings required by traditional ultra-high pressure vessels into multiple independent forgings with smaller thicknesses and dimensions. The dimensions and thickness of individual arc-shaped plates 21 and rings 31 can be controlled within the forming capacity range of existing forging equipment. Furthermore, due to the significantly reduced thickness of the middle arc-shaped plate 21 and the outer ring 31, the temperature gradient between the core and surface of the forging cross-section is greatly reduced during forging and subsequent heat treatment. This avoids defects such as coarse grains, uneven microstructure, and insufficient density in the core caused by inconsistent cooling rates in thick-walled forgings. It ensures the uniformity and compliance rate of the mechanical properties of each layer of the cylinder material. It also solves the problem in existing technologies where, as pressure parameters continue to increase, the required single-layer thickness of the double-layer heat-shrink structure also needs to increase synchronously. For large-diameter ultra-high-pressure vessels, the distributed single-layer forging thickness is often still large, potentially exceeding the forming capacity limit of the manufacturer's existing forging equipment. Moreover, during forging and subsequent heat treatment, the excessive thickness of the forging cross-section creates a significant temperature gradient between the core and surface, potentially causing severe inhomogeneity in the mechanical properties of the forging core and surface, all of which present manufacturing difficulties and make it hard to produce qualified products.

[0047] In the description of this application, it should be noted that the terms "upper," "lower," etc., indicating the orientation or positional relationship are based on the orientation or positional relationship shown in the accompanying drawings, and are only for the convenience of describing this application and simplifying the description, and 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 a limitation of this application. Unless otherwise expressly specified and limited, the terms "installed," "connected," and "linked" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication between two elements. For those skilled in the art, the specific meaning of the above terms in this application can be understood according to the specific circumstances.

[0048] It should be noted that in this application, relational terms such as "first" and "second" are used merely to distinguish one entity or operation from another, and do not necessarily require or imply any such actual relationship or order between these entities or operations. Furthermore, the terms "comprising," "including," or any other variations thereof are intended to cover non-exclusive inclusion, such that a process, method, article, or apparatus that comprises a list of elements includes not only those elements but also other elements not expressly listed, or elements inherent to such a process, method, article, or apparatus. Without further limitations, an element defined by the phrase "comprising one..." does not exclude the presence of other identical elements in the process, method, article, or apparatus that includes said element.

[0049] The above description is merely a specific embodiment of this application, enabling those skilled in the art to understand or implement this application. Various modifications to these embodiments will be readily apparent to those skilled in the art, and the general principles defined herein may be implemented in other embodiments without departing from the spirit or scope of this application. Therefore, this application is not to be limited to the embodiments shown herein, but is to be accorded the widest scope consistent with the principles and novel features claimed herein.

Claims

1. An ultra-high pressure thermal sleeve, characterized in that, include: The inner cylindrical body (1) is a one-piece molded structure; The middle layer cylinder (2) is sleeved on the outside of the inner layer cylinder (1). The middle layer cylinder (2) includes a plurality of arc-shaped plates (21) arranged around the circumference of the inner layer cylinder (1). The center of the arc-shaped plates (21) coincides with the inner layer cylinder (1). The outer cylinder (3) is sleeved on the outside of the middle cylinder (2). The outer cylinder (3) includes a plurality of rings (31) arranged along the axial direction of the inner cylinder (1). The center of the rings (31) coincides with the center of the arc plate (21).

2. The ultra-high pressure thermal sleeve body as described in claim 1, characterized in that, The middle layer cylinder (2) and the outer layer cylinder (3) have the same length in the axial direction. The inner layer cylinder (1) has a shorter length in the axial direction than the middle layer cylinder (2). Both ends of the inner layer cylinder (1) are provided with sealing mechanisms (4). The sealing mechanisms (4) are located inside the middle layer cylinder (2). The sealing mechanisms (4) are used to cooperate with the inner layer cylinder (1), the middle layer cylinder (2) and the outer layer cylinder (3) to form a cavity.

3. The ultra-high pressure thermal sleeve body as described in claim 2, characterized in that, The inner side of the middle cylinder (2) is provided with a connecting groove, and the sealing mechanism (4) includes: A sealing cap (41) is disposed at the end of the inner cylinder (1) and extends partially into the inner cylinder (1). A shear ring (42) is located on the side of the sealing cap (41) away from the inner cylinder (1). The shear ring (42) is engaged in the connecting groove. The shear ring (42) and the sealing cap (41) abut against each other, and the contact surface between the shear ring (42) and the sealing cap (41) is an inclined surface. If the sealing cap (41) moves away from the inner cylinder (1), the shear ring (42) moves into the connecting groove.

4. The ultra-high pressure thermal sleeve body as described in claim 3, characterized in that, The sealing mechanism (4) further includes an installation assembly (43), which includes a plurality of installation screws (431). The installation screws (431) pass through the shear ring (42), the middle cylinder (2) and the outer cylinder (3). The installation screws (431) are provided with two spaced installation nuts (432), which abut against the inner side of the shear ring (42) and the outer side of the outer cylinder (3) respectively.

5. The ultra-high pressure thermal sleeve body as described in claim 4, characterized in that, The mounting assembly (43) further includes a hydraulic drive (433) located inside the shear ring (42) and connected to the sealing cap (41). The hydraulic drive (433) is connected to all mounting screws (431) and is used to drive the mounting screws (431) to move radially along the middle cylinder (2) so that the shear ring (42) abuts against the connecting groove.

6. The ultra-high pressure thermal sleeve body as described in claim 3, characterized in that, All the arc plates (21) are provided with the connecting groove, and the shearing ring (42) includes arc units that correspond one-to-one with the arc plates (21), and the arc units are locked in the connecting groove of the corresponding arc plates (21).

7. The ultra-high pressure thermal sleeve body as described in claim 3, characterized in that, The sealing cap (41) includes a large-diameter section and a small-diameter section. The large-diameter section is located at the end of the inner cylinder (1). The outer diameter of the large-diameter section is larger than the inner diameter of the inner cylinder (1) and matches the inner diameter of the middle cylinder (2). The small-diameter section extends into the inner cylinder (1).

8. The ultra-high pressure thermal sleeve body as described in claim 7, characterized in that, The end of the small-diameter section extending into the inner cylinder (1) is provided with an installation groove, the installation groove being located outside the small-diameter section, and a sealing assembly (5) is provided within the installation groove, the sealing assembly (5) comprising: A triangular pad (51) is provided on the inclined surface at the bottom of the mounting groove, and one right-angled side of the triangular pad (51) abuts against the inner side of the inner cylinder (1); A sealing ring (52) is disposed in the mounting groove and located on the side of the triangular pad (51) away from the large diameter section. The sealing ring (52) is used to abut against the other right-angle side of the triangular pad (51).

9. The ultra-high pressure thermal sleeve body as described in claim 8, characterized in that, The sealing assembly (5) also includes a retaining ring (53), which is located on the side of the sealing ring (52) away from the triangular pad (51), and the side of the retaining ring (53) away from the sealing ring (52) is flush with the end of the small diameter section that extends into the inner cylinder (1).

10. An ultra-high pressure vessel, characterized in that, Includes an ultra-high pressure thermal sleeve body as described in any one of claims 1-9.

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