A pressure vessel opening and closing structure

Abstract

The application discloses a pressure container opening and closing structure, which comprises an upper cavity, a lower cavity, a horizontal moving driving assembly and a lock catch assembly. The upper cavity is fixedly arranged, and the lower cavity is horizontally movable and can move horizontally between a first position and a second position. When the lower cavity is located at the first position, the lower cavity is located at the side of the upper cavity, so that material loading and unloading operation is facilitated; when the lower cavity is located at the second position, the lower cavity is located directly below the upper cavity and forms a sealed pressure container cavity with the upper cavity. The lock catch assembly comprises a plurality of lock catches, and the upper cavity and the lower cavity are locked when the lower cavity is located at the second position. The application adopts a horizontal moving opening and closing mode to replace a traditional vertical lifting mode, and a large lifting cylinder and a complicated lifting guide component are not needed, so that the equipment occupied space and the air source consumption are remarkably reduced. In addition, the lower cavity is horizontally moved with high safety, an additional mechanical limiting protection mechanism is not needed, and the system cost is effectively reduced.

Description

Technical Field

[0001] This invention relates to the field of battery manufacturing equipment technology, and in particular to a pressure vessel opening and closing structure. Background Technology

[0002] Existing quick-opening square pressure vessel structures for liquid injection machines typically employ a fixed upper chamber and a vertically rising and falling lower chamber for opening and closing. The specific working process is as follows: an external mechanism places the battery material to be processed into the lower chamber. Then, lifting cylinders installed on both sides of the chamber drive the lower chamber vertically upwards along guide components. Once the lower chamber is in position and aligned with the upper chamber, a locking mechanism installed around the square chamber automatically locks it closed via cylinder drive, completing the chamber sealing process. Subsequent filling and degassing processes then proceed. When the chamber is opened, the above steps are performed in reverse order.

[0003] However, this vertical lifting and opening structure has the following technical drawbacks: First, the vertical lifting of the lower cavity requires lifting cylinders with large stroke and thrust. These cylinders must be installed on both sides of the cavity, and corresponding lifting guide components are needed to ensure motion accuracy, resulting in a large overall structural footprint. Large cylinders consume a lot of air, usually requiring additional compressed air tanks to ensure air supply, significantly increasing accessory costs. Second, because the locking mechanism around the square cavity needs to avoid the vertically lifting lower cavity, the locking mechanism and the lower cavity flange are usually designed with a staggered toothed ring structure. This avoidance structure results in poor load-bearing capacity of the locking mechanism. To compensate for this defect, the thickness of the toothed ring and flange must be increased, thus increasing the manufacturing cost of the cavity. Third, because the upper and lower cavities are installed vertically separately, sufficient material entry and exit space must be reserved between the upper and lower cavities to facilitate material entry through external mechanisms. This makes the overall pressure vessel larger in the height direction, which is not conducive to a compact layout. Fourth, the lower cavity relies on cylinder lifting to change position. In the event of manual maintenance or program malfunction, there is a safety hazard of abnormal lifting of the cavity causing personal injury. Therefore, four sets of mechanical limit protection mechanisms (scapegoat mechanisms) need to be set in each cavity as safety redundancy, which further increases the complexity and cost of the system. Summary of the Invention

[0004] In order to overcome the shortcomings of the prior art, the present invention provides a pressure vessel opening and closing structure that adopts lateral movement opening and closing, occupies little space, has high locking strength and is safe to operate.

[0005] The technical solution adopted by this invention to solve its technical problem is: A pressure vessel opening and closing structure includes: an upper cavity, fixedly disposed; a lower cavity, movable in a horizontal direction, capable of lateral movement between a first position and a second position, wherein in the first position the lower cavity is located to the side of the upper cavity, and in the second position the lower cavity is located directly below the upper cavity and forms a sealed pressure vessel chamber with the upper cavity; a lateral movement drive assembly for driving the lower cavity to move between the first position and the second position; and a locking assembly including multiple latches for locking the upper cavity and the lower cavity when the lower cavity is in the second position.

[0006] Furthermore, the bottom of the upper cavity is provided with an upper flange, and the top of the lower cavity is provided with a lower flange. Multiple latches of the locking assembly are arranged circumferentially along the upper flange and the lower flange. When the lower cavity moves to the second position, the upper flange and the lower flange are positioned opposite each other and aligned, and the multiple latches lock the upper flange and the lower flange.

[0007] Furthermore, the locking assembly includes a first locking buckle fixed to the upper flange and a second locking buckle fixed to the lower flange. Both the first and second locking buckles have concave cross-sections, and each locking buckle includes a fixed end and an outwardly extending snap-fit ​​end. The fixed end of the first locking buckle is fixed to the upper flange, and the snap-fit ​​end faces the lower flange. The first locking buckle is located on both sides of the lower cavity's moving path and at the moving end point. The fixed end of the second locking buckle is fixed to the lower flange, and the snap-fit ​​end faces the upper flange. The second locking buckle is located on the starting side of the lower cavity's moving path. When the lower cavity moves to the second position, the snap-fit ​​end of the first locking buckle engages with the lower flange, and the snap-fit ​​end of the second locking buckle engages with the upper flange.

[0008] Furthermore, the horizontal cross-sections of both the upper cavity and the lower cavity are rectangular, and the moving path is parallel to a pair of sides of the rectangle; the first latch is disposed on the distal end of the upper flange along the moving direction and on both sides perpendicular to the moving direction, and the second latch is disposed on the proximal end of the lower flange along the moving direction; when the lower cavity moves to the second position, the engaging end of the first latch engages with the distal end of the lower flange along the moving direction and on both sides perpendicular to the moving direction, and the engaging end of the second latch engages with the proximal end of the upper flange along the moving direction.

[0009] Furthermore, at least one of the upper flange and the lower flange is provided with an annular sealing groove, and a sealing ring is provided in the sealing groove; when the lower cavity moves to the second position, the sealing ring is pressed between the upper flange and the lower flange to form a seal.

[0010] Furthermore, the sealing ring is an expansion sealing ring; when the lower cavity moves to the second position and the plurality of latches are locked, the expansion sealing ring is inflated by air to form a seal between the upper flange and the lower flange.

[0011] Furthermore, the transverse drive assembly includes: a linear guide rail, arranged along the moving direction of the lower cavity; a slider, slidably arranged on the linear guide rail; an adapter plate, fixed on the slider, the lower cavity being mounted on the slider via the adapter plate; and a drive member, used to drive the slider to move along the linear guide rail.

[0012] Furthermore, the driving component is a motor, and the transverse drive assembly also includes a rack mounting plate and an adapter rod. The rack mounting plate is provided with a rack extending along the direction of the linear guide rail, and the rack mounting plate is connected to the adapter plate through the adapter rod. The motor drives the rack, thereby moving the rack mounting plate and the adapter rod, and thus driving the adapter plate to move.

[0013] Furthermore, the lower cavity is connected to the adapter plate via an elastic support member, and the lower cavity can float vertically relative to the adapter plate; the lower cavity is provided with vertical guide holes around its perimeter, and the adapter plate is provided with guide posts that cooperate with the vertical guide holes. The guide posts are inserted into the vertical guide holes to limit the horizontal displacement of the lower cavity relative to the adapter plate.

[0014] Furthermore, the second position includes two locations, respectively on both sides of the first position, with one upper cavity corresponding to each second position.

[0015] The beneficial effects of this invention are: This invention discloses a pressure vessel opening and closing structure, comprising an upper cavity, a lower cavity, a lateral movement drive assembly, and a locking assembly. The upper cavity is fixedly disposed, while the lower cavity is movable horizontally, capable of lateral movement between a first position and a second position. When the lower cavity is in the first position, it is located to the side of the upper cavity, facilitating material loading and unloading operations; when the lower cavity is in the second position, it is located directly below the upper cavity, forming a sealed pressure vessel chamber with the upper cavity. By employing an opening and closing method where the lower cavity moves laterally in the horizontal direction, the lateral drive assembly only needs to provide horizontal driving force, without needing to overcome the gravity of the lower cavity. Therefore, there is no need to use a large lifting cylinder, significantly reducing the space occupied by the equipment and air consumption. Since the lower cavity moves horizontally from the side into the area below the upper cavity, the locking assembly can lock directly from the periphery of the cavity without the need for a clearance structure, resulting in strong load-bearing capacity of the locking assembly and reducing the flange thickness. The lateral movement of the lower cavity only requires a clearance of about 2mm, resulting in a low overall height. There is no risk of the lower cavity falling when moving horizontally, ensuring high safety and eliminating the need for additional mechanical limit protection mechanisms, effectively reducing system costs and improving the compactness and safety of the equipment. Attached Figure Description

[0016] The present invention will be further described below with reference to the accompanying drawings and embodiments.

[0017] Figure 1 This is a three-dimensional structural schematic diagram of the present invention; Figure 2 This is a cross-sectional schematic diagram of the present invention facing the second position; Figure 3 yes Figure 2 Enlarged view of point A in the middle; Figure 4 This is a schematic diagram of the structure when the upper cavity and the lower cavity of the present invention are combined.

[0018] in, 1. Upper cavity; 11. Upper flange; 2. Lower cavity; 21. Lower flange; 22. Guide hole; 3. First position; 4. Second position; 5. Lateral movement drive assembly; 51. Linear guide rail; 52. Slider; 53. Adapter plate; 531. Guide post; 54. Drive component; 55. Rack mounting plate; 551. Adapter rod; 552. Rack; 56. Elastic support component; 6. Locking assembly; 61. First lock; 62. Second lock; 63. Fixed end; 64. Snap-fit ​​end; 7. Annular sealing groove; 71. Expansion sealing ring; 8. Support frame. Detailed Implementation

[0019] The following will clearly and completely describe the concept, specific structure, and technical effects of the present invention in conjunction with embodiments and accompanying drawings, so as to fully understand the purpose, features, and effects of the present invention. Obviously, the described embodiments are only a part of the embodiments of the present invention, not all of them. Other embodiments obtained by those skilled in the art based on the embodiments of the present invention without creative effort are all within the scope of protection of the present invention. Furthermore, all connections / linkages involved in the patent do not simply refer to direct contact between components, but rather to the ability to form a better connection structure by adding or reducing connecting accessories according to specific implementation conditions. The various technical features in this invention can be combined interactively without contradicting each other.

[0020] Reference Figure 1 , Figure 2 This invention provides a pressure vessel opening and closing structure, including an upper cavity 1, a lower cavity 2, a lateral movement drive assembly 5, a locking assembly 6, and a support frame 8. The support frame 8 serves as the basic frame of the entire opening and closing structure, supporting the upper cavity 1, the lower cavity 2, and the lateral movement drive assembly 5. The support frame 8 can be a frame structure welded from structural steel, an aluminum profile assembly structure, or a cast integral structure, possessing sufficient strength and rigidity to withstand various loads generated by the pressure vessel during operation.

[0021] The upper cavity 1 is fixedly installed on the upper part of the support frame 8 and is fixedly connected to the support frame by bolts, welding or other fixing methods, and remains stationary during operation. The lower cavity 2 is movably connected to the support frame 8 through the transverse drive assembly 5 and can move along the support frame 8.

[0022] The lateral movement drive assembly 5 is used to drive the lower cavity 2 to move between the first position 3 and the second position 4, thereby realizing the horizontal lateral movement of the lower cavity 2. The locking assembly 6 includes multiple locking latches, which lock the upper cavity 1 and the lower cavity 2 when the lower cavity 2 moves to the second position 4, without the need for an additional locking drive mechanism.

[0023] The locking assembly 6 can be implemented in various ways. For example, the locking assembly can be a mechanical snap-fit ​​locking assembly, which engages and disengages through elastic deformation. Another example is a bolt-connected locking assembly, which uses bolts to fix the upper and lower cavities 2. Yet another example is a quick-connect locking assembly, which achieves rapid locking through rotation or push-pull. Still another example is a pneumatically or hydraulically driven automatic locking assembly, which uses a cylinder or hydraulic cylinder to drive the locking and unlocking. These different types of locking assemblies can all achieve a reliable connection between the upper and lower cavities 2, ensuring the sealing and safety of the pressure vessel.

[0024] The working principle of this invention is as follows: the lower cavity 2 is driven horizontally from a first position 3 on the side to a second position 4 directly below the upper cavity 1 by the lateral drive component 5. After moving into position, the locking component 6 locks the upper cavity 1 and the lower cavity 2 together, forming a sealed pressure vessel chamber. Compared with the vertical lifting and lowering method of the lower cavity 2 in the prior art, this invention adopts a horizontal lateral movement method, which eliminates the need for large lifting cylinders and guide components, as well as scapegoat safety limit mechanisms, resulting in a simpler structure and lower cost.

[0025] The beneficial effects of this invention are as follows: First, by using a lateral movement method instead of a lifting method, the need for accessories such as large air cylinders, guide components, and compressed air tanks is eliminated, reducing equipment costs and energy consumption. Second, since no clearance space is required for lifting movements, more space is saved in the vertical direction. Third, since there is no lifting movement of the lower cavity 2, there is no need to set up a scapegoat safety limit mechanism, further reducing costs and eliminating the risk of personal injury due to program malfunctions.

[0026] In one specific embodiment, refer to Figure 4 The upper cavity 1 has an upper flange 11 at its bottom, and the lower cavity 2 has a lower flange 21 at its top. Multiple latches of the locking assembly 6 are arranged circumferentially along the upper flange 11 and the lower flange 21. When the lower cavity 2 moves to the second position 4, the upper flange 11 and the lower flange 21 are positioned opposite each other and aligned, and the multiple latches lock the upper flange 11 and the lower flange 21. By setting latches on the flanges of the upper and lower cavities 2, a reliable connection between the cavities is achieved. Flanges can be of various forms, such as flat flanges, raised face flanges, or concave-convex face flanges. Flat flanges have a simple structure, are easy to process, and their sealing performance is ensured by a gasket. Raised face flanges or concave-convex face flanges improve alignment accuracy and sealing effect through the mating of the flange faces.

[0027] In this embodiment, the latches are evenly distributed along the circumference of the flange, providing uniform locking force and avoiding localized stress concentration. The number of latches can be determined based on the cavity size and working pressure; generally, the larger the cavity circumference and the higher the working pressure, the more latches are required. For example, for a rectangular cavity, four latches can be placed on each of the four sides. For a circular cavity, the latches can be evenly distributed along the circumference, for example, with six, eight, or twelve latches. By rationally setting the number and position of the latches, sufficient locking force is ensured throughout the entire circumference of the upper flange 11 and lower flange 21, guaranteeing sealing performance and structural strength.

[0028] Furthermore, referring to Figure 4The locking assembly includes a first locking buckle 61 fixed to the upper flange 11 and a second locking buckle 62 fixed to the lower flange 21. Both the first locking buckle 61 and the second locking buckle 62 have concave cross-sections, and each locking buckle includes a fixed end 63 and an outwardly extending snap-fit ​​end 64. This concave cross-section locking buckle has good tensile strength, and when pressure is generated inside the pressure vessel, the concave locking buckle can effectively resist the flange separation tendency.

[0029] The first latch 61 has its fixed end 63 fixed to the upper flange 11 and its snap-fit ​​end 64 facing the lower flange 21. The first latch 61 is located on both sides of the moving path of the lower cavity 2 and at the moving end point. The second latch 62 has its fixed end 63 fixed to the lower flange 21 and its snap-fit ​​end 64 facing the upper flange 11. The second latch 62 is located on the side of the lower cavity facing away from the second position 4. When the lower cavity 2 moves to the second position 4, the snap-fit ​​end 64 of the first latch 61 engages with the lower flange 21, and the snap-fit ​​end 64 of the second latch 62 engages with the upper flange 11, thereby achieving automatic locking of the upper and lower cavities 2.

[0030] The advantages of this locking arrangement are as follows: Since the first locking buckle 61 is positioned on both sides and at the end of the movement path, it will not interfere with the lower cavity 2 when it moves laterally into position 4, allowing the lower cavity 2 to move smoothly to the second position 4. Similarly, the second locking buckle 62, positioned on the side of the lower cavity facing away from the second position 4, will not obstruct the movement of the lower cavity 2. Once the lower cavity 2 is in position, the first locking buckle 61 engages the lower flange 21 from both sides and the front, while the second locking buckle 62 engages the upper flange 11 from the rear. The four locking buckles work together to achieve automatic locking of the upper and lower cavities 2, eliminating the need for an additional locking drive device. This structure allows the locking buckles and flanges to be made as a single, seamless unit. Compared to the existing technology that uses a toothed ring misalignment structure to avoid lifting movements, the locking buckles and flanges of this invention have better load-bearing capacity, allowing for thinner walls and lower cavity costs.

[0031] Reference Figure 4 The latch has a slender strip structure, and its length is parallel to the edge of the upper cavity 1 or the lower cavity 2. One end of the latch has a fixed end 63, which is used to fix it to the flange edge of the upper cavity 1 or the lower cavity 2. The fixed end 63 can be fixed by means of bolts, riveting or welding.

[0032] The end of the latch furthest from the fixed end 63 is the snap-fit ​​end 64. The snap-fit ​​end 64 is bent inward to form a locking protrusion. The locking protrusion has a hook-shaped or claw-shaped structure, and its inner surface forms a snap-fit ​​surface. When the upper cavity 1 and the lower cavity 2 are closed, the locking protrusion is inserted into the flange edge of the corresponding cavity. The snap-fit ​​surface of the locking protrusion and the flange edge form a snap-fit ​​engagement, realizing a reliable connection between the two cavities.

[0033] For the upper cavity 1 and lower cavity 2 with rectangular structures, four latches are preferably set and arranged on the four sides of the rectangle. Since the long and short sides of the rectangle are of different lengths, the corresponding latch lengths are also adapted.

[0034] All latches use the same working principle and installation method, differing only in length, which simplifies the manufacturing process, reduces production costs, and facilitates mass production and on-site installation.

[0035] The locking mechanism can be made of high-strength steel, stainless steel, or alloy steel to meet strength and corrosion resistance requirements. The locking surface can be heat-treated, plated, or surface-hardened to improve wear resistance and service life. The snap-fit ​​end 64 can be equipped with a guide chamfer to facilitate the engagement of the locking mechanism with the flange. The fit between the snap-fit ​​end 64 and the flange can be a clearance fit or a transition fit. A clearance fit is easier to assemble but requires less locking force, while a transition fit requires more locking force but necessitates a certain assembly force.

[0036] Specifically, both the upper cavity 1 and the lower cavity 2 have rectangular horizontal cross-sections, and their movement paths are parallel to a pair of sides of the rectangle. The first locking buckle 61 is located on the distal end of the upper flange 11 along the movement direction and on both sides perpendicular to the movement direction, while the second locking buckle 62 is located on the proximal end of the lower flange 21 along the movement direction. When the lower cavity 2 moves to the second position 4, the engaging end 64 of the first locking buckle 61 engages with the distal end of the lower flange 21 along the movement direction and on both sides perpendicular to the movement direction, while the engaging end 64 of the second locking buckle 62 engages with the proximal end of the upper flange 11 along the movement direction. This arrangement ensures that the four locking buckles lock the four sides of the rectangular flange, creating a uniform locking force and guaranteeing the sealing performance of the cavities.

[0037] In this embodiment, the rectangular cross-section cavity has the advantage of high space utilization, making it particularly suitable for processing square or rectangular workpieces. (Refer to...) Figure 4 The four sides of the rectangular flange can be easily fitted with latches to achieve reliable locking. The first latch 61 on the distal side along the direction of movement is located at the endpoint of the lower cavity 2's movement. Once the lower cavity 2 is in position, the engaging end 64 of the first latch 61 naturally aligns and engages with the corresponding side of the lower flange 21. The first latches 61 on both sides perpendicular to the direction of movement are located on either side of the movement path during the movement of the lower cavity 2, without interfering with it. Once the lower cavity 2 is in position, the engaging ends 64 of the first latches 61 on both sides engage with the corresponding sides of the lower flange 21. The second latch 62 on the proximal side along the direction of movement is fixed to the lower flange 21 and moves with the lower cavity 2. Once the lower cavity 2 is in position, the engaging end 64 of the second latch 62 engages with the corresponding side of the upper flange 11. Thus, the distal side, proximal side along the direction of movement, and the two sides perpendicular to the direction of movement together form a four-directional locking system, providing sufficient locking force.

[0038] Besides rectangular cross-sections, cavities can also have circular, elliptical, or other polygonal cross-sections. For circular cross-section cavities, the latches can be evenly distributed along the circumference, for example, one latch every 60, 45, or 30 degrees. For elliptical cross-sections, the latches can be strategically placed along the major and minor axes to improve locking effectiveness. For other polygonal cross-sections, the latches can be placed at each edge or vertex. Regardless of the cross-sectional shape, the principle for latch placement is to ensure even distribution of locking force and avoid localized stress concentration.

[0039] Regarding the sealing structure, refer to Figure 4 At least one of the upper flange 11 and the lower flange 21 is provided with an annular sealing groove 7, and a sealing ring is disposed in the sealing groove. When the lower cavity 2 moves to the second position 4, the sealing ring is pressed between the upper flange 11 and the lower flange 21 to form a seal. By setting the sealing ring, gas or liquid leakage in the pressure vessel can be effectively prevented, ensuring the safety and effectiveness of the process.

[0040] The sealing groove can be located on the upper flange 11, the lower flange 21, or both. When the sealing groove is on the upper flange 11, the surface of the lower flange 21 is flat, and the sealing ring is installed in the sealing groove of the upper flange 11. When the upper flange 11 and the lower flange 21 are mated, the sealing ring is compressed by the lower flange 21 to form a seal. When the sealing groove is on the lower flange 21, the working principle is similar; the sealing ring is compressed by the upper flange 11 to form a seal. When sealing grooves are provided on both the upper flange 11 and the lower flange 21, if the two sealing grooves are located at different radial positions (i.e., the radii of the two sealing grooves are different), the two sealing rings are arranged radially staggered, forming a double seal inside and out, improving sealing reliability. Furthermore, different types of sealing rings can be installed in the two sealing grooves respectively to achieve graded sealing.

[0041] Various types of sealing rings can be used. For example, O-rings are the most common type, offering advantages such as simple structure, good sealing performance, and low cost. Square or rectangular sealing rings can also be used, maintaining good sealing performance even under high compression. V-rings or Y-rings can further be employed, exhibiting self-sealing properties where the sealing effect improves with increasing pressure.

[0042] The material of the sealing ring can be selected according to the working medium and temperature.

[0043] More specifically, due to the use of a lateral movement opening and closing mechanism, only a gap of about 2mm is needed between the upper cavity 1 and the lower cavity 2 when the cavity is open to meet the space requirements for lateral movement. Compared with the traditional upper and lower separation opening and closing mechanism, this significantly saves space in the height direction. Based on this compact gap design, this embodiment preferably uses an expansion sealing ring 71 as the sealing element. The expansion sealing ring 71 is installed in the sealing groove of the upper flange 11 or the lower flange 21, maintaining a relatively flat cross-sectional shape in the uninflated state. Its radial dimension is less than the lateral movement gap of 2mm, which will not interfere with the lateral movement of the lower cavity 2.

[0044] After the lower cavity 2 moves laterally from the first position 3 to the second position 4 and aligns with the upper cavity 1, multiple latches lock sequentially, fixing the upper and lower cavities 2 in the closed position. At this time, compressed air or inert gas is injected into the sealing ring 71 through the inflation pipeline connected to the expansion sealing ring 71. Under the action of internal air pressure, the expansion sealing ring 71 expands radially, and its outer surface tightly fits the sealing surfaces of the upper flange 11 and the lower flange 21, forming a continuous and reliable annular seal between them. The inflation pressure of the expansion sealing ring 71 can be adjusted according to the vacuum degree or process gas pressure inside the process cavity.

[0045] In contrast, if ordinary O-rings or rectangular seals are used, the seals need to be compressed and deformed to achieve an effective seal. However, in scenarios where the lower cavity 2 needs to move laterally, this compression and deformation presents a dilemma: if the compression deformation is small, the sealing effect is poor and cannot meet the sealing requirements of the pressure vessel; if the compression deformation is large, the resistance to lateral movement of the lower cavity 2 increases, making movement difficult, and the compressed seal is easily driven laterally by lateral friction, thus being squeezed out of the sealing groove, causing seal failure. The expansion seal 71, however, achieves active control of the sealing state through inflation and deflation. When sealing is needed, it inflates to generate sufficient compression to ensure sealing performance. When the cavity is opened, the gas is released, restoring it to its unexpanded, flat state. At this point, the seal does not contact the opposite flange, and the lower cavity 2 can smoothly move laterally out. This avoids the risk of the seal being carried laterally out of the sealing groove and eliminates the contradiction between sealing effect and smooth movement, significantly improving the maintainability of the equipment and the service life of the seal.

[0046] The expansion seal 71 is typically made of an elastomeric material and has an internal inflation chamber. Inflation of the expansion seal 71 is achieved through an inflation port located on the flange, which is connected to a compressed air source or gas cylinder via a pipeline. The inflation process can be manually controlled or automatically controlled by a solenoid valve, automatically inflating after the latch is engaged and automatically deflating before unlocking.

[0047] The expansion seal ring 71 can have an annular airbag structure, with the entire seal ring forming a continuous inflation chamber. Alternatively, it can have a segmented airbag structure, with the seal ring divided into several independent inflation sections, each of which can be inflated independently, improving sealing reliability. Even if one section leaks, the other sections can still maintain a seal. A protective layer can be applied to the outer surface of the expansion seal ring 71 to prevent damage during friction with the flange surface. When the expansion seal ring 71 is installed in the sealing groove, it can be fixed by adhesive, snap-fit, or mechanical fastening to prevent the seal ring from detaching from the groove during inflation.

[0048] The advantages of the expansion sealing ring 71 compared to ordinary sealing rings are as follows: First, the sealing force is adjustable, allowing for adjustment of the inflation pressure according to process requirements to achieve different sealing effects. Second, it has lower requirements for flange surface precision; even with minor unevenness on the flange surface, the expansion sealing ring 71 can achieve a seal by expanding and filling the gap. Third, it facilitates cavity opening; after venting, the sealing ring contracts, significantly reducing friction with the flange, allowing the lower cavity 2 to be easily removed. Finally, it is highly adaptable, able to accommodate changes in flange clearance, and maintains good sealing performance even under conditions of thermal expansion and contraction or structural deformation.

[0049] Regarding the structure of the lateral drive component 5, refer to... Figure 2 , 3 The lateral movement drive assembly 5 includes a linear guide rail 51, a slider 52, an adapter plate 53, and a drive component 54. The linear guide rail 51 is positioned along the moving direction of the lower cavity 2, providing precise guidance for the lateral movement of the lower cavity 2. The slider 52 is slidably mounted on the linear guide rail 51, enabling smooth movement along it. The adapter plate 53 is fixed to the slider 52, and the lower cavity 2 is mounted on the slider 52 via the adapter plate 53, thus connecting the lower cavity 2 and the slider 52. The drive component 54 drives the adapter plate 53 to move along the linear guide rail 51, thereby causing the lower cavity 2 to move laterally.

[0050] The linear guide 51 can be of various types. For example, a ball linear guide 51 can be used, with circulating balls inside the slider 52. The balls roll between the guide and the slider 52, offering advantages such as low friction, smooth movement, and high precision, making it suitable for precision positioning applications. Another example is a roller linear guide 51, with rollers inside the slider 52. Compared to ball guides, it has a higher load-bearing capacity and is suitable for heavy-duty applications. Yet another example is a sliding linear guide 51, where sliding friction exists between the slider 52 and the guide. This structure is simple and low-cost, but it has higher friction and lower precision, making it suitable for applications where high precision is not required.

[0051] The number and arrangement of linear guides 51 can be determined based on the size and weight of the lower cavity 2. For small, lightweight cavities, one linear guide 51 can be used. For medium-sized cavities, two parallel linear guides 51 are typically used, located on both sides of the cavity, providing stable support and guidance. For large, heavy-duty cavities, three or four linear guides 51 can be used to form a more stable support platform. The linear guides 51 can be fixed to the base or frame. The base needs to have sufficient rigidity to prevent deformation under load, which could affect the guiding accuracy.

[0052] The slider 52 works in conjunction with the linear guide rail 51, and each linear guide rail 51 can be equipped with one or more sliders 52. Multiple sliders 52 can increase the bearing area, improve load-bearing capacity and smoothness of movement. The slider 52 is fixed to the adapter plate 53 by bolts, and the adapter plate 53 is then connected to the lower cavity 2 to realize load transfer. The preload of the slider 52 is adjustable. Appropriate preload can eliminate gaps and improve rigidity and accuracy, but excessive preload will increase frictional resistance. The slider 52 requires regular lubrication, which can be achieved by grease lubrication or oil lubrication. Maintaining good lubrication can extend its service life.

[0053] Reference Figure 3 The adapter plate 53 is an intermediate component connecting the slider 52 and the lower cavity 2. It is typically made of steel plate or cast iron and needs to have sufficient strength and rigidity. The shape and size of the adapter plate 53 are determined by the shape of the bottom of the lower cavity 2, and can be a rectangular plate, a circular plate, or an irregularly shaped plate. The adapter plate 53 has mounting holes for connecting to the slider 52 and the lower cavity 2. The thickness of the adapter plate 53 needs to be designed according to the load-bearing requirements; insufficient thickness will lead to deformation, affecting guiding accuracy and sealing effect.

[0054] The driving component 54 can take various forms. For example, it can be driven by a motor, which can be a servo motor, a stepper motor, or a regular AC motor. Servo motors have the advantages of precise position control and fast response speed, stepper motors are less expensive but have limited load-bearing capacity, and regular AC motors have a simple structure but lower control precision. Alternatively, it can be driven by a cylinder, where compressed air pushes the cylinder piston, moving the slider 52. Cylinder drives have a simple structure, but their speed and position control precision is not as good as that of a motor.

[0055] In one embodiment, refer to Figure 3The driving component 54 is a motor, and the lateral drive assembly 5 also includes a rack mounting plate 55 and an adapter rod 551. The rack mounting plate 55 has a rack 552 extending along the linear guide rail 51, and the rack mounting plate 55 is connected to an adapter plate 53 via the adapter rod 551. A gear is mounted on the output shaft of the motor, and the gear meshes with the rack 552. When the motor drives the gear to rotate, the gear drives the rack 552 to move along the linear guide rail 51, the rack 552 drives the rack mounting plate 55 to move, and the rack mounting plate 55 drives the adapter plate 53 to move via the adapter rod 551, thereby driving the lower cavity 2 mounted on the adapter plate 53 to move laterally. This rack and pinion transmission method achieves position control and stable transmission performance.

[0056] Rack and pinion drives offer advantages such as high transmission efficiency, large load capacity, and stable transmission ratio. Gears can be spur gears, helical gears, or herringbone gears. Spur gears have a simple structure and are easy to manufacture, but they produce impact and relatively high noise during transmission. Helical gears provide smooth transmission, low noise, and high load capacity, but they generate axial force. Herringbone gears can counteract axial force and provide smooth transmission, but their structure is complex and their cost is high.

[0057] The rack 552's teeth mesh with gears. The rack 552 can be a single long rack or composed of multiple rack segments. Long racks 552 are suitable for shorter strokes, while multi-segment racks are suitable for longer strokes. When splicing, it's crucial to ensure accurate tooth pitch at the joints to avoid transmission errors. The rack 552 is fixed to the rack mounting plate 55, either by bolts or welding. Bolt fixing facilitates adjustment and replacement, while welding provides high strength but is less convenient for adjustment. A linear guide rail 51 and a slider 52 can also be installed below the rack mounting plate 55 to allow for smooth movement, or the rack mounting plate 55 can be guided by other guiding mechanisms.

[0058] Reference Figure 3 The adapter rod 551 connects the rack mounting plate 55 and the adapter plate 53 to transmit power. The adapter rod 551 can be round, square, or have other cross-sectional shapes, requiring sufficient strength and rigidity to prevent bending deformation during transmission. The connection between the adapter rod 551 and the rack mounting plate 55 and adapter plate 53 can be achieved through threaded connection, pin connection, or welding. Threaded connections allow for length adjustment, facilitating installation and debugging. Pin connections allow for hinged joints, permitting a certain angular deviation. Welded connections offer high strength but are not detachable.

[0059] In rack and pinion drives, the selection of the motor needs to be determined based on load, speed, and acceleration requirements. The load includes the weight of the lower cavity 2 and its internal materials, as well as frictional resistance and inertial forces during acceleration. Speed ​​is determined by the process cycle time; a faster cycle time requires a higher moving speed. Acceleration affects start-up and stop times; greater acceleration results in faster start-up and stop, but also places higher demands on the motor and mechanical structure. Motor power can be calculated using load, speed, and efficiency, and a safety factor is usually also considered.

[0060] To accommodate the positional adjustment requirements during the docking of the upper and lower cavities 2, refer to Figure 4 The lower cavity 2 is connected to the adapter plate 53 via an elastic support 56, allowing the lower cavity 2 to float vertically relative to the adapter plate 53. Vertical guide holes 22 are provided around the lower cavity 2, and guide posts 531 that mate with the vertical guide holes 22 are provided on the adapter plate 53. The guide posts 531 are inserted into the vertical guide holes 22 to limit the horizontal displacement of the lower cavity 2 relative to the adapter plate 53.

[0061] The function of the elastic support 56 is to provide support while allowing vertical displacement. When the lower cavity 2 moves to the second position 4 and aligns with the upper cavity 1, if there is a slight deviation in the height direction, the elastic support 56 allows the lower cavity 2 to float vertically to adapt to the position of the upper cavity 1, ensuring accurate alignment of the upper flange 11 and the lower flange 21. This floating capability is crucial for improving assembly success rate and sealing quality, especially when the cavity size is large or installation accuracy is limited.

[0062] The elastic support 56 can take various forms. For example, it can be an airbag, filled with compressed air, which provides support and buoyancy through the elasticity of the gas. The stiffness of the airbag can be changed by adjusting the inflation pressure; the higher the inflation pressure, the greater the stiffness and the smaller the buoyancy, and the lower the inflation pressure, the smaller the stiffness and the greater the buoyancy. Airbags have the advantages of high load-bearing capacity and adjustable buoyancy range, but require an air source and control valve. Alternatively, a spring can be used, which can be a helical compression spring, a disc spring, or a leaf spring. Helical compression springs are simple in structure and low in cost, but they occupy a large height. Disc springs have high stiffness and occupy little height; their stiffness and stroke can be adjusted by connecting them in series or parallel.

[0063] The elastic support members 56 can be arranged in a multi-point support manner, for example, four or more elastic support members 56 can be set on the adapter plate 53 and distributed around the bottom of the lower cavity 2 to provide uniform support force. Alternatively, they can be arranged in a ring shape, with a ring-shaped airbag or spring assembly set on the adapter plate 53 to form a continuous support surface. Multi-point support facilitates adjustment of the support force at each point, achieving levelness adjustment, while ring support provides more uniform support but has lower adjustment flexibility.

[0064] The selection of the stiffness of the elastic support 56 needs to comprehensively consider both load-bearing and floating requirements. If the stiffness is too high, the floating amount is small, the alignment accuracy requirement is high, and it may lead to difficulties in docking. If the stiffness is too low, the floating amount is large, the alignment is easy, but the stability of the lower cavity 2 is poor, and it may generate large vibrations.

[0065] Reference Figure 4 The cooperation between the guide post 531 and the vertical guide hole 22 restricts the horizontal displacement of the lower cavity 2, ensuring the accuracy of its movement. The guide post 531 is inserted into the guide hole 22 with a certain gap between them, allowing relative vertical movement but restricting horizontal displacement. The length of the guide post 531 should be greater than the vertical float of the lower cavity 2 to ensure that the guide post 531 remains inserted within the guide hole 22 throughout the entire float range, maintaining its guiding function.

[0066] The guide post 531 can be cylindrical, fitting into the circular guide hole 22. This is the most common form, simple to manufacture, and provides reliable guidance. It can also be square or other cross-sectional shapes, fitting into guide holes 22 of corresponding shapes, simultaneously restricting rotation. Typically, there are four guide posts 531, located at the four corners or four sides of the bottom of the lower cavity 2, providing stable guidance. More guide posts 531 can also be used to increase guiding rigidity.

[0067] The fit clearance between the guide post 531 and the guide hole 22 needs to be properly selected. If the clearance is too small, the frictional resistance will be high, which may cause jamming and affect the vertical floating direction. If the clearance is too large, the guiding accuracy will be low, and the lower cavity 2 may experience significant horizontal shaking. The surface of the guide post 531 can be surface treated, such as chrome plating, nitriding, or coating, to improve wear resistance and reduce the coefficient of friction. A wear-resistant bushing, such as a copper bushing or a polymer bushing, can be installed inside the guide hole 22 to reduce wear and extend service life.

[0068] The fit between the guide post 531 and the guide hole 22 can also be designed as a damping structure. A sealing ring and a liquid-filling space are set inside the guide hole 22. When the guide post 531 moves within the guide hole 22, the liquid is squeezed, generating a damping force, which can suppress vibration and improve stability. This structure is suitable for applications with large vibrations, but it increases the structural complexity.

[0069] In one specific embodiment, refer to Figure 4 The guide post 531 and the vertical guide hole 22 can be fitted together using a sliding bearing and a sliding post. Specifically, a sliding bearing is installed in the vertical guide hole 22, and the sliding post 531 is inserted into the sliding bearing as the guide post. A sliding fit is formed between the sliding post and the sliding bearing, realizing relative movement in the vertical direction and guiding restriction in the horizontal direction.

[0070] In a preferred embodiment, refer to Figure 1The second position 4 comprises two chambers, located on either side of the first position 3. In this arrangement, an upper chamber 1 is positioned at each of the two second positions 4. After material loading and unloading occurs at the middle first position 3, the lower chamber 2 can move to either side of the second position 4 to dock with the corresponding upper chamber 1, forming a sealed pressure vessel chamber for processing. By setting up two lower chambers 2, which can alternately move to the two sides of the second position 4, while one lower chamber 2 is performing processes such as inflation and deflation at one side of the second position 4, the other lower chamber 2 can be used for material loading and unloading at the first position 3, thereby improving production efficiency and making full use of equipment space.

[0071] The advantages of a dual-station layout are as follows: First, it increases production efficiency. The two lower cavities 2 work alternately, reducing waiting time and improving equipment utilization. Assuming a single process processing time is T1 and material loading / unloading time is T2, completing one cycle in a single-station setup requires T1 + T2. However, in a dual-station setup, since loading / unloading and processing occur concurrently, the time to complete one cycle is close to max(T1, T2). When T1 ≈ T2, production efficiency almost doubles. Second, it optimizes space utilization. The upper cavity 1 is located in the middle, with the lower cavities 2 arranged on either side, forming a compact layout. Compared to a single-station setup that requires reserved space on the sides for loading / unloading, the dual-station setup offers higher space utilization. Third, it improves operational continuity. Operators can perform loading / unloading on one side while processing is underway on the other, ensuring a smooth work rhythm and reducing waiting time.

[0072] In a dual-station layout, the lateral movement of the two lower cavities 2 can be driven by independent drive systems, controlled separately without interference. Alternatively, a shared drive system can be used, with a switching mechanism driving the two lower cavities 2 separately. This method is less expensive but more complex to control. The advantage of an independent drive system is its flexible control, enabling asynchronous movement of the two lower cavities 2 to adapt to different process cycles, but it is more expensive and occupies more space. A shared drive system requires a reliable switching mechanism to ensure accurate transmission of driving force to the target lower cavity 2 and to avoid malfunctions.

[0073] The lateral movement paths of the two lower cavities 2 can be completely independent, each equipped with a separate complete guide rail system that does not intersect. Alternatively, they can share a portion of the guide rails, merging near the second position 4 to form a shared section. This method saves space and cost, but requires the design of an obstacle avoidance mechanism or interlock control to prevent the two lower cavities 2 from colliding when simultaneously entering the shared section. The advantage of completely independent paths is that their movements do not affect each other, resulting in high safety, but they occupy more space. Shared paths require precise position control and reliable safety interlocks to ensure operational safety.

[0074] The linear guide rail 51 and slider 52 in the transverse drive assembly 5 can also be replaced by a combination of linear bearings and linear bearing guide shafts. The linear bearings are mounted on the guide shaft, which is positioned along the moving direction of the lower cavity 2. The linear bearings can slide on the guide shaft, achieving the same guiding and supporting functions as the linear guide rail 51 and slider 52. The adapter plate 53 is fixed on the linear bearings, and the adapter plate 53 is driven to move along the guide shaft by the drive component 54, thereby causing the lower cavity 2 to move laterally.

[0075] Linear bearings can be either ball linear bearings or sliding linear bearings. Ball linear bearings have internal circulating balls that roll between the guide shaft and the bearing, resulting in low friction and smooth movement, but they are more expensive and require high surface quality from the guide shaft. Sliding linear bearings have internal sliding bushings that directly slide in contact with the guide shaft. They are simple in structure, low in cost, and have a high load-bearing capacity, but they have higher frictional resistance and require lubrication, making them suitable for low-speed applications.

[0076] Guide shafts can be made of solid or hollow circular shafts. Solid shafts have high rigidity and strong load-bearing capacity, but are heavier. Hollow shafts are lighter, reducing inertia and improving start-stop response speed, but have relatively lower rigidity and are suitable for medium to small load applications. Guide shafts are typically made of high-quality carbon steel or alloy steel, and their surfaces are hardened, ground, and polished to achieve high hardness and a smooth surface, reducing wear and improving guiding accuracy.

[0077] The fit between the linear bearing and the guide shaft is similar to that between the linear guide rail 51 and the slider 52. A reasonable clearance or preload needs to be set. Eliminating the clearance can improve rigidity and accuracy, but it will increase frictional resistance. Linear bearings require lubrication; either grease or oil lubrication can be used. The choice of lubricant needs to consider the load, speed, and working environment. Grease lubrication is simple to maintain and suitable for low- to medium-speed applications, while oil lubrication has good heat dissipation performance and is suitable for high-speed or heavy-load applications, but it requires an oil supply system.

[0078] The linear bearing can be connected to the adapter plate 53 using a bearing housing, which is fixed to the adapter plate 53, and the linear bearing is installed inside the bearing housing. The bearing housing can be either split or integral; a split type facilitates bearing installation and replacement, while an integral type offers higher rigidity. The connection between the bearing housing and the adapter plate 53 is secured with bolts, ensuring a reliable connection and preventing loosening.

[0079] This alternative solution can also achieve smooth lateral movement of the lower cavity 2. Compared to linear guides 51 and sliders 52, linear bearings and guide shafts have a simpler structure and may be less expensive, especially for long-stroke applications, where guide shafts are significantly cheaper than linear guides 51. However, linear guides 51 and sliders 52 generally offer better guiding accuracy and rigidity than linear bearings and guide shafts, particularly in heavy-duty and high-precision applications where linear guides 51 are more advantageous. Therefore, the specific choice of which solution to use depends on a comprehensive consideration of application requirements, cost budget, and space constraints.

[0080] The entire operation of the pressure vessel opening and closing structure is as follows: In the initial state, the lower chamber 2 is located at the first position 3, which is to the side of the upper chamber 1. Operators or automated equipment load the material to be processed into the lower chamber 2. During the loading process, the upper chamber 1 does not participate and does not affect the loading operation. After loading is completed, the motor is started. The motor drives the lower chamber 2 to move laterally from the first position 3 to the second position 4 along the linear guide rail 51 via a gear and rack mechanism. The lateral movement speed can be set according to process requirements, generally adopting a motion curve of first accelerating, then maintaining a constant speed, and finally decelerating to reduce impact and improve motion stability.

[0081] When the lower cavity 2 approaches the second position 4, the position sensor can detect the position and decelerate in advance to achieve precise stopping. When the lower cavity 2 moves to the second position 4, the lower cavity 2 is directly below the upper cavity 1, and the upper flange 11 and lower flange 21 are aligned in the horizontal direction. At this time, if there is a slight height deviation between the upper flange 11 and the lower flange 21, the elastic support 56 allows the lower cavity 2 to float vertically. Through its own weight or by applying a certain upward force, the lower flange 21 gradually approaches the upper flange 11, achieving accurate alignment. During the alignment process, the guide post 531 guides within the guide hole 22 to prevent horizontal deviation.

[0082] After alignment, the first latch 61 on the upper flange 11 and the second latch 62 on the lower flange 21 automatically engage, locking the upper and lower cavities 2. The first latch 61 is located on both sides and at the end of the movement path, while the second latch 62 is located at the starting point. When the lower cavity 2 is in position, the latch's engaging end 64 naturally aligns with and engages with the flange, requiring no additional driving device. The engagement process is completed automatically, relying on the movement of the lower cavity 2, simplifying the structure and improving reliability.

[0083] After locking is complete, the sealing ring is inflated, causing it to expand and seal. The inflation pressure is set according to the working pressure inside the container to ensure a reliable seal. Inflation can be completed automatically by the control system. The inflation valve is automatically activated after the locking mechanism is detected to be fully engaged, and closed after inflation is complete.

[0084] After sealing, a closed pressure vessel chamber is formed, which can be used for processes such as filling and venting. For example, a vacuum pump can be used to evacuate the chamber, removing the air inside, and then an inert gas such as nitrogen or argon can be introduced, or a process gas such as electrolyte vapor can be introduced, maintaining a certain pressure and time to complete the process. During the process, the pressure vessel needs to withstand the internal pressure, and the locking force provided by the latch and the sealing performance provided by the sealing ring ensure the sealing and safety of the chamber.

[0085] After the process is completed, the pressure is first released to expel or recover the gas in the chamber, restoring the pressure inside the chamber to normal. The sealing ring is then vented to cause it to contract, reducing the sealing force and facilitating chamber separation. The motor is then started to drive the lower chamber 2 in reverse, moving it laterally from the second position 4 back to the first position 3, thus completing the unlocking process. The lateral movement is the reverse of the entry process, employing a deceleration, constant speed, and acceleration motion curve for a smooth return.

[0086] After returning to position 3, the processed materials can be unloaded and new materials to be processed can be loaded, starting the next work cycle. Unloading and loading can be done manually or by automated equipment such as robotic arms and conveyor belts, achieving unmanned operation and further improving production efficiency.

[0087] In a dual-station layout, the two lower cavities 2 operate alternately in their work cycles. For example, initially, the left lower cavity 2 completes loading and moves laterally to the second position 4 for processing, while the right lower cavity 2 is loaded at the first position 3. When the left lower cavity 2 finishes processing and returns to the first position 3, the right lower cavity 2 completes loading and moves laterally to the second position 4 for processing, while the left lower cavity 2 simultaneously unloads and loads. This alternation ensures continuous production and maximizes equipment utilization.

[0088] The entire system can be configured with a control system for automatic control. The control system includes a programmable logic controller (PLC), a touchscreen human-machine interface (HMI), position sensors, and pressure sensors. The PLC is programmed according to the process flow to automatically control the motor's start and stop, the locking and unlocking of the latches, the inflation and deflation of the sealing rings, and the switching of the vacuum pump and gas source. Position sensors detect the position of the lower chamber 2 to ensure accurate positioning. Pressure sensors detect the pressure within the chamber, monitoring the process and ensuring safety. The touchscreen HMI provides an operating interface, displays equipment status, and allows operators to set parameters, start and stop equipment, and view alarm information.

[0089] The entire pressure vessel opening and closing structure is practical, economical, and reliable. The use of a horizontal sliding mechanism instead of a lifting mechanism simplifies the structure, reduces costs, and improves space utilization. Automatic locking is achieved through the locking assembly 6, eliminating the need for an additional drive device and further simplifying the structure. The dual-station layout makes full use of equipment space, improves production efficiency, and meets the high-efficiency requirements of industrial production.

[0090] The above is a detailed description of the preferred embodiments of the present invention. However, the present invention is not limited to the embodiments described. Those skilled in the art can make various equivalent modifications or substitutions without departing from the spirit of the present invention. All such equivalent modifications or substitutions are included within the scope defined by the claims of this application.

Claims

1. A pressure vessel opening and closing structure characterized by comprising: include: Upper cavity, fixed setting; The lower cavity can move horizontally and can move laterally between a first position and a second position. In the first position, the lower cavity is located to the side of the upper cavity, and in the second position, the lower cavity is located directly below the upper cavity and forms a sealed pressure vessel chamber with the upper cavity. A lateral drive assembly is used to drive the lower cavity to move between a first position and a second position; The locking assembly includes multiple latches that lock the upper and lower cavities when the lower cavity is in the second position.

2. The pressure vessel opening and closing structure according to claim 1, characterized in that, The upper cavity is provided with an upper flange at its bottom and the lower cavity is provided with a lower flange at its top. Multiple latches of the locking assembly are arranged circumferentially along the upper flange and the lower flange. When the lower cavity moves to the second position, the upper flange and the lower flange are positioned opposite each other and aligned, and the multiple latches lock the upper flange and the lower flange.

3. The pressure vessel opening and closing structure according to claim 2, characterized in that, The locking assembly includes a first locking buckle fixed on the upper flange and a second locking buckle fixed on the lower flange. The cross-sections of the first locking buckle and the second locking buckle are both concave. Each locking buckle includes a fixed end and an outwardly extending snap-fit ​​end. The fixed end of the first latch is fixed to the upper flange, and the snap-fit ​​end faces the lower flange. The first latch is located on both sides of the lower cavity's moving path and at the moving end point. The fixing end of the second latch is fixed to the lower flange, the snap-fit ​​end faces the upper flange, and the second latch is located on the side of the lower cavity opposite to the second position; When the lower cavity moves to the second position, the snap-fit ​​end of the first latch engages with the lower flange, and the snap-fit ​​end of the second latch engages with the upper flange.

4. The pressure vessel opening and closing structure according to claim 3, characterized in that, Both the upper cavity and the lower cavity have rectangular horizontal cross-sections, and the moving path is parallel to a pair of sides of the rectangle. The first latch is located on the distal end of the upper flange along the moving direction and on both sides perpendicular to the moving direction, and the second latch is located on the proximal end of the lower flange along the moving direction. When the lower cavity moves to the second position, the locking end of the first latch engages with the distal end of the lower flange along the moving direction and on both sides perpendicular to the moving direction, and the locking end of the second latch engages with the proximal end of the upper flange along the moving direction.

5. The pressure vessel opening and closing structure according to claim 2, characterized in that, At least one of the upper flange and the lower flange is provided with an annular sealing groove, and a sealing ring is provided in the sealing groove; when the lower cavity moves to the second position, the sealing ring is pressed between the upper flange and the lower flange to form a seal.

6. The pressure vessel opening and closing structure according to claim 5, characterized in that, The sealing ring is an expansion sealing ring; When the lower cavity moves to the second position and the locking assembly is engaged, the expansion sealing ring is inflated by inflating it, thereby forming a seal between the upper flange and the lower flange.

7. The pressure vessel opening and closing structure according to claim 1, wherein The lateral movement drive component includes: A linear guide rail is provided along the moving direction of the lower cavity; A slider is slidably mounted on the linear guide rail; An adapter plate is fixed on the slider, and the lower cavity is mounted on the slider via the adapter plate; A driving component is used to drive the slider to move along the linear guide rail.

8. The pressure vessel opening and closing structure according to claim 7, characterized in that, The driving component is a motor. The transverse drive assembly also includes a rack mounting plate and an adapter rod. The rack mounting plate is provided with a rack extending along the linear guide rail. The rack mounting plate is connected to the adapter plate through the adapter rod. The motor drives the rack, which in turn moves the rack mounting plate and the adapter rod, thereby driving the adapter plate to move.

9. The pressure vessel opening and closing structure according to claim 7, characterized in that, The lower cavity is connected to the adapter plate via an elastic support member, and the lower cavity can float vertically relative to the adapter plate. The lower cavity is provided with vertical guide holes around its perimeter, and the adapter plate is provided with guide posts that cooperate with the vertical guide holes. The guide posts are inserted into the vertical guide holes to limit the horizontal displacement of the lower cavity relative to the adapter plate.

10. The pressure vessel opening and closing structure according to any one of claims 1-9, characterized in that, The second position includes two locations, located on either side of the first position, with one upper cavity corresponding to each second position.

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