Vertical low-temperature high-pressure heat insulation storage tank device and method

Abstract

The invention discloses a vertical low-temperature high-pressure heat insulation storage tank device and method, and belongs to the technical field of low-temperature fluid storage. The storage tank device comprises a supporting piece, a pressure-bearing inner container, an outer tank barrel, fins and a heat insulation support. The pressure-bearing inner container is coaxially arranged in an inner cavity of the outer tank barrel. An inner container wall thickening layer is arranged on the outer side of the pressure-bearing inner container, and an inner cavity is divided into a gas phase area and a liquid phase area; the inner container wall thickening layer is arranged on the outer side of the interface of the gas phase area and the liquid phase area of the pressure-bearing inner container and extends from the interface to the top and the bottom of the pressure-bearing inner container. A plurality of fins are arranged at the bottom of the pressure-bearing liner; a composite heat insulation layer and a vacuum heat insulation layer are arranged between the pressure-bearing inner container and the outer tank barrel from inside to outside. The inner container wall thickening layer promotes heat transfer between gas and liquid wall surfaces and inhibits heating expansion of a gas phase region. In addition, natural convection of fluid at the bottom is enhanced through the fins, the temperature uniformity of a liquid phase area is improved, and pressure rise caused by expansion of the liquid phase area is slowed down. Through the optimization measures, the lossless storage time of the low-temperature fluid in the storage tank can be remarkably prolonged.

Description

Technical Field

[0001] The present invention belongs to the technical field of cryogenic fluid storage, and particularly relates to a vertical cryogenic high-pressure adiabatic storage tank device and method. Background Art

[0002] In order to meet the demand for higher volume density, energy media such as hydrogen energy, natural gas, and oxygen are usually stored on a large scale and transported over long distances in the form of cryogenic liquids. However, due to the large temperature difference between the cryogenic fluid and the environment, heat leakage inevitably occurs during the storage process. The heat leakage causes the fluid to gradually form thermal stratification under the action of natural convection: the liquid-phase fluid expands due to heat, and at the same time, the gas-phase fluid has a small heat capacity and rapidly heats up and expands after being heated. The liquid phase and the gas phase interact with each other, ultimately leading to a rapid increase in the internal pressure of the storage tank. When the pressure of the storage system reaches the safety threshold, the system is forced to discharge to ensure safety, resulting in the loss of cryogenic fluid. Therefore, improving the lossless storage time of cryogenic fluids is of great significance for realizing efficient, safe, and environmentally friendly energy storage and transportation, and is also one of the key technologies to promote the energy transformation in China.

[0003] Currently, the methods for improving the lossless storage time in the field of cryogenic fluid storage are divided into active methods and passive methods. The active methods include external energy input or additional cooling systems to suppress the heat leakage and evaporation loss of cryogenic fluids. For example, an additional cooling system is added to cool the cryogenic fluid inside the storage tank or other cryogenic fluids are used for purging and cooling. The active method is disclosed in a patent application with the publication number CN116972340A, which discloses an additional cooling system to recover the excess cold energy of high-pressure liquid hydrogen to cool the liquid hydrogen storage tank. However, this makes the system equipment complex, energy consumption high, and cost high. The passive method is disclosed in a patent application with the publication number CN118602274A, which reduces heat leakage by designing a non-contact supported suspended liquid hydrogen storage tank, thereby extending the liquid hydrogen storage time. However, the energy supply, precise control, external anti-interference ability, etc. of the suspended system will cause problems such as increased cost, complex system, and safety issues. Therefore, how to store cryogenic fluids in a low-energy-consumption, low-cost, long-time lossless and safe manner is one of the key problems to be solved urgently. Summary of the Invention

[0004] The purpose of the present invention is to solve the deficiencies in the prior art and provide a vertical cryogenic high-pressure adiabatic storage tank device and method.

[0005] The specific technical solutions adopted by the present invention are as follows:

[0006] In the first aspect, the present invention provides a vertical cryogenic high-pressure adiabatic storage tank device, including a support member, a pressure-bearing inner tank, an outer tank cylinder, fins, and an adiabatic support;

[0007] An adiabatic support for support is provided at the bottom of the outer cylinder; the pressure-bearing inner liner is coaxially arranged in the inner cavity of the outer cylinder, and the pressure-bearing inner liner and the outer cylinder are fixedly connected through a support member; an inner liner wall thickening layer is arranged outside the pressure-bearing inner liner; the inner cavity of the pressure-bearing inner liner is divided into an upper gas phase area and a lower liquid phase area; the inner liner wall thickening layer is arranged outside the interface between the gas phase area and the liquid phase area of the pressure-bearing inner liner, and extends from the interface towards the top and bottom directions of the pressure-bearing inner liner; a plurality of fins for promoting bottom fluid convection are arranged at the bottom of the liquid phase area of the pressure-bearing inner liner; a composite adiabatic layer and a vacuum adiabatic layer are arranged between the pressure-bearing inner liner and the outer cylinder from the inside to the outside.

[0008] Preferably, the inner liner wall thickening layer is made of a material with good thermal conductivity and low density, and is made of carbon fiber, aluminum alloy or stainless steel.

[0009] Preferably, the inner liner wall thickening layer adopts an equal-thickness structure, that is, the thickness of the inner liner wall thickening layer is equal from top to bottom.

[0010] Preferably, the inner liner wall thickening layer adopts a non-equal-thickness structure, and in the vertical direction, the thickness of the inner liner wall thickening layer decreases towards both ends with the interface between the gas phase area and the liquid phase area as the symmetry center.

[0011] Preferably, the setting width of the inner liner wall thickening layer is 10% - 100% of the height of the pressure-bearing inner liner; the average thickness of the inner liner wall thickening layer is more than 10% of the thickness of the composite adiabatic layer.

[0012] Preferably, the fins adopt fins with a cross-sectional shape of rectangle, trapezoid, circle, triangle or needle shape.

[0013] Preferably, the arrangement of the fins adopts one or a combination of radial arrangement, circumferential arrangement, grid arrangement or fan-shaped arrangement.

[0014] Preferably, the composite adiabatic layer adopts a composite arrangement of one or more of foam, aerogel, glass bubbles, air glass microspheres or spray foam insulation materials.

[0015] In a second aspect, the present invention provides a method for increasing the non-destructive storage time of cryogenic fluids. Cryogenic fluids are introduced into the pressure-bearing inner liner of the vertical cryogenic high-pressure adiabatic storage tank device described in the first aspect for storage; by setting the inner liner wall thickening layer and the fins, the pressure rise rate inside the pressure-bearing inner liner is alleviated, and the non-destructive storage time of cryogenic fluids is increased.

[0016] Preferably, the cryogenic fluid is liquid hydrogen, supercritical hydrogen, liquid nitrogen, liquid oxygen, liquid helium, liquefied natural gas or liquefied petroleum gas.

[0017] The present invention has the following beneficial effects compared with the prior art:

[0018] (1) The present invention utilizes the thickened layer on the inner tank wall to promote heat transfer from the gas-phase wall to the liquid-phase wall, reduce the heat leakage into the gas phase region, thereby weakening the temperature rise and expansion in the gas phase region, and thus increasing the non-destructive storage time of the low-temperature fluid in the storage tank.

[0019] (2) The present invention adopts a series of fins to promote the natural convection of the bottom fluid, enhance the mixing of the fluid inside the liquid phase region, and improve the temperature uniformity in the liquid phase region, thereby weakening the pressure increase in the gas phase region caused by the expansion of the liquid phase region; at the same time, the decrease in the average temperature of the liquid phase region can enhance the heat transfer from the gas phase region inside the storage tank to the liquid phase region through the gas-liquid interface, reduce the actual heat absorption in the gas phase region, thereby weakening the temperature rise and expansion in the gas phase region; thus increasing the non-destructive storage time of the low-temperature fluid in the storage tank.

[0020] (3) The storage tank device provided by the present invention has a simple structure. The thickened layer on the inner tank wall and the fins both adopt materials with relatively low density, which can reduce the system weight and facilitate the installation, maintenance, and transportation of the storage system. The present invention provides a passive method for increasing the non-destructive storage time, which has low energy consumption and low cost. Description of the Drawings

[0021] Figure 1 is a schematic diagram of the vertical low-temperature high-pressure adiabatic storage tank device provided by the present invention;

[0022] Figure 2 is the curve of the gas-phase temperature inside the storage tank changing with time before and after setting the thickened layer on the inner tank wall in Example 1;

[0023] Figure 3 is the curve of the pressure inside the storage tank changing with time before and after setting the thickened layer on the inner tank wall in Example 1;

[0024] In the figure: support member 1, gas phase region 2, pressure-bearing inner tank 3, liquid phase region 4, composite insulation layer 5, thickened layer on the inner tank wall 6, vacuum insulation layer 7, outer tank cylinder 8, fins 9, insulation support 10. Detailed Embodiments

[0025] The following further elaborates and explains the present invention in conjunction with the drawings and specific embodiments. The technical features of each embodiment in the present invention can be combined accordingly without conflict.

[0026] As Figure 1 shown, the present invention provides a vertical low-temperature high-pressure adiabatic storage tank device, including a support member 1, a pressure-bearing inner tank 3, an outer tank cylinder 8, fins 9, and an insulation support 10;

[0027] An adiabatic support 10 for support is provided at the bottom of the outer cylinder 8; the pressure-bearing inner cylinder 3 is coaxially arranged in the inner cavity of the outer cylinder 8, and the pressure-bearing inner cylinder 3 and the outer cylinder 8 are fixedly connected by two sets of support members 1, upper and lower; an inner cylinder wall thickening layer 6 is arranged outside the pressure-bearing inner cylinder 3, and an adiabatic layer is formed between the pressure-bearing inner cylinder 3 and the outer cylinder 8. The inner cavity of the pressure-bearing inner cylinder 3 is divided into a gas phase region 2 in the upper part and a liquid phase region 4 in the lower part.

[0028] In order to promote the heat transfer between the gas phase wall surface and the liquid phase wall surface in the pressure-bearing inner cylinder 3, reduce the heat leakage in the gas phase region, and inhibit the temperature rise and expansion in the gas phase region. The inner cylinder wall thickening layer 6 in the present invention is specifically arranged as follows: the inner cylinder wall thickening layer 6 is arranged outside the interface between the gas phase region 2 and the liquid phase region 4 of the pressure-bearing inner cylinder 3, and extends from the interface towards the top and bottom directions of the pressure-bearing inner cylinder 3. The inner cylinder wall thickening layer 6 in the present invention can be arranged in an equal-thickness structure or a non-equal-thickness structure. The equal-thickness structure means that the inner cylinder wall thickening layer 6 has the same thickness from top to bottom. The non-equal-thickness structure means that in the vertical direction, the thickness of the inner cylinder wall thickening layer 6 takes the interface between the gas phase region 2 and the liquid phase region 4 as the symmetry center and decreases towards both ends. Specifically, in the vertical direction, the cross-section of the inner cylinder wall thickening layer 6 is a curved trapezoid, the upper base and the lower base of the curved trapezoid are straight edges, and the side away from the outer wall of the pressure-bearing inner cylinder is a curved edge, ensuring that the thickness of the inner cylinder wall thickening layer 6 at the interface between the gas phase region 2 and the liquid phase region 4 is greater than the thickness at both ends of the inner cylinder wall thickening layer 6. The cross-sectional shapes of the non-equal-thickness structure include, but are not limited to, shapes such as ellipse, trapezoid, and partial arc.

[0029] In the device provided by the present invention, the set width of the inner cylinder wall thickening layer 6 is 10% - 100% of the height of the pressure-bearing inner cylinder 3; the thickness of the inner cylinder wall thickening layer 6 is more than 10% of the thickness of the composite adiabatic layer 5. The inner cylinder wall thickening layer 6 is made of a material with good thermal conductivity and low density, such as carbon fiber, aluminum alloy, or stainless steel.

[0030] In the device provided by the present invention, a plurality of fins 9 for promoting bottom fluid convection are arranged at the bottom of the liquid phase region 4 of the pressure-bearing inner cylinder 3. The fins 9 are rectangular fins with a rectangular cross-section, circular fins with a circular cross-section, trapezoidal fins with a trapezoidal cross-section, or triangular fins with a triangular cross-section. The fins 9 can also be fins with a needle-shaped cross-section. Pin fins are usually slender needle-shaped and can increase the heat dissipation area, which is suitable for occasions where high-efficiency heat dissipation is required.

[0031] In the device provided by the present invention, the fins 9 are arranged in one or a combination of radial arrangement, circumferential arrangement, grid arrangement or sector arrangement. Specifically, the radial arrangement means that the fins radiate outward from the central axis of the pressure-bearing inner tank of the storage tank and are evenly distributed along the radial direction. The radially arranged fins can effectively guide the fluid to flow from the center to the periphery, promote the convection and mixing of the fluid, and at the same time can evenly disperse the stress at the bottom of the storage tank and enhance the structural stability. The circumferential arrangement means that the fins are evenly distributed in the circumferential direction of the pressure-bearing inner tank to form an annular fin band. The circumferentially arranged fins can enhance the circumferential stiffness of the storage tank, resist the circumferential stress, and at the same time help to guide the fluid to flow in the circumferential direction, promote the uniform distribution and convection of the fluid. The fins arranged in a grid pattern intersect with each other to form a grid-like structure. The grid-arranged fins can not only provide a large support area and enhance the overall strength of the bottom of the storage tank, but also provide multi-directional channels for the flow of the fluid, promote the convection and mixing of the fluid in all directions, and improve the heat exchange efficiency. The sector-arranged fins are distributed in a sector shape outward from the center of the pressure-bearing inner tank of the storage tank. This arrangement is similar to an unfolded fan, and each fin unfolds outward from the center at a certain angle to form a sector arrangement. The sector-arranged fins can concentrate on promoting the convection of the fluid in a specific area and are suitable for situations where it is necessary to strengthen the fluid flow and heat exchange in a specific area at the bottom of the storage tank. Those skilled in the art can select one or more fins of different shapes according to actual needs and arrange the fins in one or a combination of radial arrangement, circumferential arrangement, grid arrangement or sector arrangement.

[0032] In the device provided by the present invention, the insulating layer formed between the pressure-bearing inner tank 3 and the outer tank cylinder 8 includes a composite insulating layer 5 and a vacuum insulating layer 7 arranged from the inside out. The composite insulating layer 5 is arranged by combining one or more of foam, aerogel, glass bubbles, air glass microspheres or spray foam insulation materials. The glass bubble material has a hollow structure inside, the internal gas has a low thermal conductivity, and the glass bubbles themselves have good chemical stability and high temperature resistance. The air glass microsphere is a hollow microsphere containing air and also has the characteristics of low thermal conductivity, low density and light weight. The spray foam insulation material forms a continuous and uniform insulating layer between the pressure-bearing inner tank 3 and the outer tank cylinder 8 by spraying, effectively reducing the heat transfer. In summary, those skilled in the art can make full use of the insulation performance advantages of different materials and arrange one or more of the above materials in combination according to actual needs.

[0033] During the storage of cryogenic fluids, due to the huge temperature difference between the cryogenic fluid and the environment, it is impossible to completely avoid heat leakage in the storage tank. Heat leakage causes the fluid to gradually form thermal stratification under the action of natural convection: the liquid phase expands due to heat; the gas phase has a small heat capacity and quickly heats up and expands due to heat. The two together cause the pressure in the gas phase to rise rapidly. When the pressure of the storage tank reaches the safety threshold, it is forced to release to ensure safety, thus causing the loss of cryogenic fluid.

[0034] A method for increasing the lossless storage time of cryogenic fluids is carried out by using the vertical low-temperature high-pressure insulated storage tank device provided by the present invention, which is specifically as follows: a cryogenic fluid is introduced into the pressure-bearing liner 3 for storage. The cryogenic fluid is liquid hydrogen, supercritical hydrogen, liquid nitrogen, liquid oxygen, liquid helium, liquefied natural gas or liquefied petroleum gas. Since a thickened liner wall layer 6 with good thermal conductivity is arranged on the outside of the pressure-bearing liner 3 in the device provided by the present invention, the thickened liner wall layer 6 promotes heat transfer between the gas phase wall and the liquid phase wall, reduces heat leakage in the gas phase region 2, and inhibits the temperature rise and expansion of the gas phase region 2. The ribs 9 arranged at the bottom of the pressure-bearing liner 3 can promote the natural convection of the bottom fluid, enhance the mixing of the fluid inside the liquid phase region 4, and improve the uniform temperature of the liquid phase region 4, thereby slowing down the pressure rise of the gas phase region 2 caused by the expansion of the liquid phase region. In addition, the ribs 9 can also reduce the average temperature of the liquid phase region, enhance the heat transfer between the gas phase region 2 and the liquid phase region 4 inside the storage tank, reduce the actual heat absorption of the gas phase region 2, and further inhibit the temperature rise and expansion of the gas phase region 2. The combined effect of the above measures effectively slows down the rate of pressure rise inside the storage tank, thereby achieving the goal of increasing the lossless storage time of cryogenic fluids.

[0035] The specific application and technical effect of the vertical vacuum insulated cryogenic storage tank device and method are further explained below in conjunction with specific embodiments. It should be noted that the following embodiments are only used to illustrate the present invention and are not used to limit the scope of the present invention.

[0036] Example 1

[0037] In this embodiment, a 4.89m 3 Take a spherical liquid hydrogen storage tank with an inner diameter of 1.056m as an example. The filling rate of the liquid hydrogen storage tank is 49%, and the boundary leakage heat flux density is 3.5W / m 2 , evenly distributed on the outer wall of the tank. When there is no thickening layer on the outer side of the pressure tank, the hydrogen temperature of the internal gas-liquid two-phase measuring point and the gas-liquid two-phase tank wall temperature are measured using a resistance temperature sensor, and the pressure inside the tank is measured using a pressure sensor, and the following can be obtained: Figure 2 and Figure 3 The solid lines show the time variation curves of the gas phase temperature and the pressure inside the tank.

[0038] When a stainless steel wire mesh is spirally wound in the area 0.75 m above and below the gas-liquid interface on the outer side of the pressure-bearing inner tank of the storage tank to form an inner tank wall thickening layer with a thickness of 10 mm, assuming that the inner wall temperatures of the gas and liquid phases remain unchanged, the heat input from the gas phase to the liquid phase can be calculated after the inner tank wall thickening layer is set. The calculation formula is as follows:

[0039] q w =KA(T w1 -T w2 ) (1)

[0040] Among them, q w represents the additional heat input from the gas-phase wall to the liquid-phase wall through the inner tank wall thickening layer, that is, the reduced heat leakage of the gas phase and the increased heat leakage of the liquid phase; A represents the cross-sectional area of the inner tank wall thickening layer at the height of the gas-liquid interface; K represents the heat transfer coefficient of the inner tank wall thickening layer; T w1 represents the average temperature of the gas-phase inner tank wall thickening area, and T w2 represents the average temperature of the liquid-phase inner tank wall thickening area.

[0041] Assume that all the reduced heat leakage through the inner tank wall thickening layer is used for the temperature improvement in the gas phase area, and all the increased heat leakage in the liquid phase area is used for the evaporation in the liquid phase area. Given the temperatures of the gas and liquid phases and the wall temperatures of the gas and liquid phases per hour, the improvement values of the gas-phase temperature and density after passing through the inner tank wall thickening layer per hour can be calculated. By referring to the hydrogen physical property table, the improvement value of the storage tank pressure per hour can be obtained after setting the inner tank wall thickening layer. The improved gas-phase temperature obtained is as Figure 2 shown by the dotted line, and the improved value of the tank internal pressure obtained is as Figure 3 shown by the dotted line. The calculation formula is as follows:

[0042] q w τ=m v C p (T v1 -T v2 ) (2)

[0043] Δρ v =Δm / V v (3)

[0044] Among them, τ represents time, C p represents the specific heat capacity of gaseous hydrogen, T v1 represents the initial average temperature of the gas phase area, T v2 represents the temperature after improvement in the gas phase area, Δm represents the evaporation amount in the liquid phase area, Δρ v represents the density increment in the gas phase area, and V v represents the gas phase volume.

[0045] From Figure 2The results show that when there is no thickening layer on the inner tank wall, the temperature of the gas phase rises relatively fast; after adding the thickening layer on the inner tank wall, the overall rising rate of the gas phase temperature decreases, indicating that the thickening layer on the inner tank wall can significantly reduce the temperature in the gas phase region. From Figure 3 the results, when there is no thickening layer on the inner tank wall, the pressure in the storage tank increases by about 70 kPa after storing for 12 h, while after adding the thickening layer on the inner tank wall, the pressure in the storage tank increases by about 40 kPa after storing for 12 h, indicating that the thickening layer on the inner tank wall effectively slows down the rising rate of the internal pressure of the storage tank and can achieve the goal of increasing the non-destructive storage time of cryogenic fluids.

[0046] In the storage tank device provided by the present invention, the use of fin design can enhance the natural convection of the fluid at the bottom, promote the uniform mixing of the fluid inside the liquid phase region, improve the temperature uniformity of the liquid phase region, and thus slow down the pressure rise in the gas phase region caused by the expansion of the liquid phase region. In addition, the fin design reduces the average temperature of the liquid phase region, further enhances the heat transfer between the gas phase region and the liquid phase region inside the container, reduces the actual heat absorption in the gas phase region, effectively inhibits the temperature rise and expansion in the gas phase region, and thus can slow down the rising rate of the internal pressure of the storage tank and further increase the non-destructive storage time. Compared with the prior art, the present system has the remarkable advantages of simple structure, low energy consumption, and low cost.

[0047] It is not intended to limit the present invention. Those of ordinary skill in the relevant technical field can also make various changes and modifications without departing from the spirit and scope of the present invention. Therefore, all technical solutions obtained by means of equivalent replacement or equivalent transformation fall within the protection scope of the present invention.

Claims

1. A vertical low-temperature and high-pressure insulated storage tank device, characterized in that: It comprises a support member (1), a pressure-bearing inner liner (3), an outer tank (8), fins (9) and a heat-insulating support (10); An insulating support (10) for support is arranged at the bottom of the outer barrel (8); the pressure-bearing inner liner (3) is coaxially arranged in the inner cavity of the outer barrel (8), and the pressure-bearing inner liner (3) and the outer barrel (8) are fixedly connected via a support member (1); an inner liner wall thickening layer (6) is arranged on the outer side of the pressure-bearing inner liner (3); the inner cavity of the pressure-bearing inner liner (3) is divided into an upper gas phase region (2) and a lower liquid phase region (4); the inner liner wall thickening layer (6) is arranged on the outer side of the interface between the gas phase region (2) and the liquid phase region (4) of the pressure-bearing inner liner (3), and extends from the interface toward the top and bottom of the pressure-bearing inner liner (3); a plurality of fins (9) for promoting bottom fluid convection are arranged at the bottom of the liquid phase region (4) of the pressure-bearing inner liner (3); a composite insulation layer (5) and a vacuum insulation layer (7) are arranged from the inside to the outside between the pressure-bearing inner liner (3) and the outer barrel (8).

2. The vertical low-temperature and high-pressure insulated storage tank device according to claim 1 is characterized in that: The inner liner wall thickening layer (6) is made of a material with good thermal conductivity and low density, such as carbon fiber, aluminum alloy or stainless steel.

3. The vertical low-temperature and high-pressure insulated storage tank device according to claim 1 is characterized in that: The inner liner wall thickening layer (6) adopts an equal thickness structure, that is, the inner liner wall thickening layer (6) has the same thickness from top to bottom.

4. The vertical low-temperature and high-pressure insulated storage tank device according to claim 1 is characterized in that: The inner liner wall thickening layer (6) adopts a non-uniform thickness structure, and the thickness of the inner liner wall thickening layer (6) in the vertical direction is symmetrically centered at the interface between the gas phase region (2) and the liquid phase region (4), and decreases toward both ends.

5. The vertical low-temperature and high-pressure insulated storage tank device according to claim 1 is characterized in that: The width of the inner liner wall thickening layer (6) is 10% to 100% of the height of the pressure-bearing inner liner (3); the average thickness of the inner liner wall thickening layer (6) is more than 10% of the thickness of the composite insulation layer (5).

6. The vertical low-temperature and high-pressure insulated storage tank device according to claim 1 is characterized in that: The fins (9) are fins with a cross-sectional shape of rectangle, trapezoid, circle, triangle or needle.

7. The vertical low-temperature and high-pressure insulated storage tank device according to claim 1 is characterized in that: The fins (9) are arranged in a radial arrangement, annular arrangement, grid arrangement or fan-shaped arrangement or a combination thereof.

8. The vertical low-temperature and high-pressure insulated storage tank device according to claim 1 is characterized in that: The composite heat insulating layer (5) is a composite arrangement of one or more of foam, aerogel, glass bubbles, air glass microspheres or spray foam insulation materials.

9. A method for increasing the lossless storage time of a cryogenic fluid, characterized in that: A cryogenic fluid is introduced into the pressure liner (3) of the vertical low-temperature and high-pressure insulated storage tank device according to any one of claims 1 to 8 for storage; the pressure rise rate inside the pressure liner (3) is alleviated by the provision of a thickened layer (6) on the liner wall and fins (9), thereby increasing the lossless storage time of the cryogenic fluid.

10. The method for increasing the lossless storage time of a cryogenic fluid according to claim 9, characterized in that: The cryogenic fluid is liquid hydrogen, supercritical hydrogen, liquid nitrogen, liquid oxygen, liquid helium, liquefied natural gas or liquefied petroleum gas.

Images