CN115307052B - Optimal design method for winding reinforcing layer of composite gas cylinder and application thereof - Google Patents
Optimal design method for winding reinforcing layer of composite gas cylinder and application thereof Download PDFInfo
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- CN115307052B CN115307052B CN202210973199.0A CN202210973199A CN115307052B CN 115307052 B CN115307052 B CN 115307052B CN 202210973199 A CN202210973199 A CN 202210973199A CN 115307052 B CN115307052 B CN 115307052B
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- 238000004804 winding Methods 0.000 title claims abstract description 125
- 238000013461 design Methods 0.000 title claims abstract description 59
- 238000000034 method Methods 0.000 title claims abstract description 50
- 239000002131 composite material Substances 0.000 title claims abstract description 15
- 230000003014 reinforcing effect Effects 0.000 title claims abstract description 6
- 239000000835 fiber Substances 0.000 claims abstract description 57
- 239000010410 layer Substances 0.000 claims description 106
- 239000007789 gas Substances 0.000 claims description 34
- 238000004364 calculation method Methods 0.000 claims description 16
- UFHFLCQGNIYNRP-UHFFFAOYSA-N Hydrogen Chemical compound [H][H] UFHFLCQGNIYNRP-UHFFFAOYSA-N 0.000 claims description 9
- 239000001257 hydrogen Substances 0.000 claims description 9
- 229910052739 hydrogen Inorganic materials 0.000 claims description 9
- 239000002356 single layer Substances 0.000 claims description 5
- 238000003860 storage Methods 0.000 claims description 5
- 230000009172 bursting Effects 0.000 claims description 4
- 230000000694 effects Effects 0.000 claims description 4
- 238000004519 manufacturing process Methods 0.000 claims description 2
- 230000002787 reinforcement Effects 0.000 abstract description 4
- 238000012795 verification Methods 0.000 description 5
- 239000012528 membrane Substances 0.000 description 3
- 238000009825 accumulation Methods 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 2
- 238000005516 engineering process Methods 0.000 description 2
- 235000021197 fiber intake Nutrition 0.000 description 2
- 239000002184 metal Substances 0.000 description 2
- 238000007789 sealing Methods 0.000 description 2
- 238000004458 analytical method Methods 0.000 description 1
- 230000000903 blocking effect Effects 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000005457 optimization Methods 0.000 description 1
- 238000011160 research Methods 0.000 description 1
- 239000011347 resin Substances 0.000 description 1
- 229920005989 resin Polymers 0.000 description 1
- 239000007787 solid Substances 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F17—STORING OR DISTRIBUTING GASES OR LIQUIDS
- F17C—VESSELS FOR CONTAINING OR STORING COMPRESSED, LIQUEFIED OR SOLIDIFIED GASES; FIXED-CAPACITY GAS-HOLDERS; FILLING VESSELS WITH, OR DISCHARGING FROM VESSELS, COMPRESSED, LIQUEFIED, OR SOLIDIFIED GASES
- F17C1/00—Pressure vessels, e.g. gas cylinder, gas tank, replaceable cartridge
- F17C1/02—Pressure vessels, e.g. gas cylinder, gas tank, replaceable cartridge involving reinforcing arrangements
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F17—STORING OR DISTRIBUTING GASES OR LIQUIDS
- F17C—VESSELS FOR CONTAINING OR STORING COMPRESSED, LIQUEFIED OR SOLIDIFIED GASES; FIXED-CAPACITY GAS-HOLDERS; FILLING VESSELS WITH, OR DISCHARGING FROM VESSELS, COMPRESSED, LIQUEFIED, OR SOLIDIFIED GASES
- F17C2221/00—Handled fluid, in particular type of fluid
- F17C2221/01—Pure fluids
- F17C2221/012—Hydrogen
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E60/00—Enabling technologies; Technologies with a potential or indirect contribution to GHG emissions mitigation
- Y02E60/30—Hydrogen technology
- Y02E60/32—Hydrogen storage
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Moulding By Coating Moulds (AREA)
Abstract
The invention relates to an optimal design method for a winding enhancement layer of a composite gas cylinder and application thereof. Firstly, calculating and designing the stress of each point of the lower end socket and the cylinder body of the burst pressure through a series of formulas; then, based on a seal head winding design method, designing a first fiber winding layer according to the stress of the root of the pole hole; then, comparing the strength of the first fiber winding layer with the stress of the end socket, positioning the stress weak point below the winding layer, and performing first reaming winding based on the point to realize the reinforcement of the point; reaming and winding the spiral winding layer for a plurality of times based on the method, calculating the circumferential bearing strength of the spiral layer on the cylinder body and the difference value of the circumferential design strength of the spiral layer with the cylinder body according to the winding angle and the layer number of the spiral winding layer, and designing the circumferential winding layer according to the difference value; finally, a fiber winding layer weight calculating method is designed according to different winding schemes, and the optimal design of the gas cylinder winding layer is realized. The method avoids repeated iterative correction, improves the design efficiency, and realizes the optimized design of the IV-type gas cylinder winding reinforcing layer.
Description
Technical Field
The invention relates to the technical field of pressure vessels and hydrogen energy sources, in particular to an optimal design method for a winding enhancement layer of a composite gas cylinder and application thereof.
Background
The hydrogen storage technology is a key for developing hydrogen energy automobiles. The development and application technology of the traditional III-type gas cylinder with the metal lining are mature in China, but the gas cylinder has the defects of obvious hydrogen embrittlement effect, poor fatigue performance and the like, and has great obstruction when being used as a vehicle-mounted hydrogen storage gas cylinder. In recent years, an IV-type gas cylinder with a plastic lining is gradually developed, and a feasible thought is provided for improving the hydrogen storage density, fatigue performance and hydrogen blocking performance of the vehicle-mounted gas cylinder.
The traditional III-type gas cylinder winding layer with the metal lining is mostly analyzed and designed based on barrel stress, the winding design of the end socket part is often estimated according to experience, and then the limited element is utilized for repeated iteration verification. The safety design specification of the high-pressure IV-type gas cylinder (working pressure is not lower than 70 MPa) requires that the gas cylinder is firstly damaged at the cylinder body, however, the stress condition of the sealing head part of the gas cylinder structure obtained according to the existing design method based on the stress of the cylinder body is not clear, so that the pre-failure part of the gas cylinder cannot be accurately designed, and the requirements of related standards and specifications are not met.
The search finds that Chinese patent CN103672388A discloses a design method of a head-barrel integrated fiber winding composite gas cylinder, which is based on a grid design theory to rapidly design a winding layer of the composite gas cylinder. Analysis shows that under the working condition of single winding angle, the weak point of the strength of the winding layer of the end socket section of the high-pressure IV-type gas cylinder is at the root part of the polar hole, so that the primary reaming winding design is particularly important. Chinese patent CN103672388a discloses a design method of a head-barrel integrated fiber winding composite gas cylinder, the scheme cannot meet the design requirement of a high-pressure IV gas cylinder, especially the first reaming winding design method, and the number of winding layers is selected arbitrarily by experience. In addition, the method also needs repeated iteration verification and modification, and the rapid and efficient design of the gas cylinder cannot be realized.
Therefore, the invention provides a brand new method for optimizing the design of the winding reinforcing layer of the composite gas cylinder, which rapidly and accurately designs the winding mode of the fiber and the number of the winding layers according to the strength of the winding fiber and the film stress of the gas cylinder, and finally realizes the efficient and reliable optimization design of the gas cylinder structure.
Disclosure of Invention
The invention aims to provide an optimal design method for a winding enhancement layer of a composite gas cylinder, which comprises the following steps: (a) establishing an elliptical coordinate expression of the end socket; (b) Calculating the curvature radius of different positions of the seal head according to the elliptic coordinate expression of the seal head; (c) Calculating the stress state of each point of the end socket according to the designed bursting pressure; (d) Calculating the angle and thickness of the first spiral winding layer fiber according to the variable angle and variable thickness formula; (e) Calculating the number of layers of the first winding layer according to the film stress of the polar hole position and the single-layer bearing capacity of the first winding layer; (f) According to the result of the step (e), comparing the stress state and the bearing capacity of each position, calculating the reaming winding position and performing reaming winding layer calculation; (g) And (3) carrying out circumferential winding layer design on the cylinder body according to the circumferential bearing capacity of the spiral winding layer on the cylinder body section.
Further, the head ellipse coordinate expression established in the step (a) is as follows:
wherein z represents the vertical distance from the parallel circle to the equator in mm; r represents the radius of a parallel circle of the sealing head, and the unit is mm; a represents the length of the major axis of the ellipse in mm; b represents the minor axis length of the ellipse in mm.
Further, a is more than or equal to 80 and less than or equal to 800, and preferably a is more than or equal to 160 and less than or equal to 400; b is more than or equal to 50 and less than or equal to 600, preferably more than or equal to 100 and less than or equal to 300.
Further, in the step (b), the curvature radius expression of different positions of the seal head is calculated as follows:
Wherein the method comprises the steps of Represents the principal radius of curvature of the warp threads in mm; r θ represents the main radius of curvature of the parallel circular lines, and the unit is mm; r represents the radius of the parallel circles of the seal heads, and z represents the vertical distance from the parallel circles to the equator, and is in mm.
Further, the method for calculating the film stress at different positions of the seal head in the step (c) comprises the following steps:
Wherein the method comprises the steps of Representing the film stress in the warp direction, and the unit N; n θ represents film stress in the direction of parallel circular lines, unit N; p is the design burst pressure in N.
Further, in the step (d), the calculation method of the angle and thickness of the head first spiral winding layer fiber is as follows:
αr＝arcsin(r0/r) (7)
Wherein alpha r represents the included angle (namely winding angle) between the fiber direction of each point of the seal head and the meridian, and the unit degree; t represents the thickness of each point fiber of the seal head, and the unit is mm; r represents the radius of the cylinder body, and the unit is mm; r 0 represents the pole hole radius in mm; t fα represents the thickness of the winding layer barrel section with the winding angle alpha, and the unit is mm.
Further, in step (d), the pole bore radius R 0 is less than the barrel radius R 0, preferably R 0＜0.5R0.
Further, in the step (e), a reference point is selected at a certain distance from the root of the polar hole, and based on the head winding design method, the reference point fiber layer is subjected to internal forces in the warp and parallel circular directions respectivelyAnd N θi, calculating the angle and thickness of the first winding layer fiber according to the stress in the warp and parallel round line directions according to the film stress under the condition that the strength of the fiber layer just meets the design internal pressure according to the optimal design basis of the first layer fiber thickness, and selecting/>The specific calculation method is as follows:
tfθi＝Nθi/σisin2αi (10)
where the index i indicates the current position, Representing the thickness of the fiber at the point calculated according to the warp direction stress, and the unit mm; t fθi represents the thickness of the fiber in mm according to the stress calculation in the parallel circle direction; /(I)Representing the radial bearing internal force of the fiber layer at the point, and the unit N; n θi represents the unit N that the fiber layer of the point bears the internal force in the weft direction; σ i represents the fiber stress at this point in MPa; alpha i represents the angle (i.e., winding angle) of the fiber direction from the meridian at this point.
Further, the angle α r of the fibers of the first winding layer in step (e) has a value in the range of 5 ° to 30 °, preferably 10 ° to 20 °.
Furthermore, in the step (e), a point position which is not more than 5 bandwidths from the root of the polar hole is selected as a reference point, and preferably 0.5-3 bandwidths are selected.
Further, in the step (f), the radial strength of each point of the winding layer is calculated according to the angles and the thicknesses of the fibers at different positions of the first winding layerAnd the parallel circular strength T θi, comparing the radial film stress/>, of each point of the seal headAnd parallel circular film stress N θi, starting from the root point of the polar hole along meridian line, positioning the first/>, under the winding layer to the position of the cylinder bodyOr T θi≤Nθi, reaming and winding at the point, wherein the winding layer is 2n (n is a positive integer); based on the same principle and method, the superposition effect is considered, and reaming and winding are sequentially carried out for a plurality of times until the warp-weft strength of the end socket section reaches the design requirement, wherein the specific calculation method is as follows:
Tθi＝∑σftfisin2αi (12)
where the index i indicates the current position, Representing the unit N of bearing resultant force according to the warp direction; t θi represents the load-bearing resultant force according to the parallel circular direction, unit N; σ f represents the fiber playing strength in MPa.
Further, the number of winding layers in step (f) is 2 to 20, preferably 2 to 10; the number of reaming is not more than 8, preferably 2-5.
Further, the number of layers of the annular reinforcement in step (g) is greater than the calculated number of layers, preferably greater than 2-6 calculated number of layers.
Further, for different winding schemes, a calculation method of the weight of the fiber winding layer is designed, and further the fiber and resin consumption is evaluated, wherein the specific calculation formula is as follows:
Wherein M represents the whole mass of the winding layer, and the unit g; t fα represents the single-layer thickness of the winding layer of the barrel section, and the unit is mm; ρ f represents the 60% fiber mass fraction composite density, the unit g/mm 2;zi represents the height of the spiral wound layer at the head, the unit mm; r i represents the reaming radius in mm; r represents the diameter of the cylinder body, and the unit is mm; l represents the length of the barrel in mm.
It is another object of the present invention to provide the use of the above method in designing and manufacturing a high pressure hydrogen storage cylinder.
The method comprises the steps of firstly calculating stress of each point of a lower seal head and a cylinder body of the designed bursting pressure, and then designing a first fiber winding layer according to the stress of the root of a pole hole based on a seal head winding design method; then, comparing the strength of the first fiber winding layer with the stress of the end socket, positioning the stress weak point below the winding layer, and performing first reaming winding based on the point to realize the reinforcement design of the point; then carrying out multiple reaming winding based on the method, and carrying out circumferential winding strength reinforcement design on the cylinder body according to reaming winding strength accumulation; finally, a fiber winding layer weight calculating method is designed according to different winding schemes, and the optimal design of the gas cylinder winding layer is realized. The high-pressure IV type gas cylinder designed by the method can realize the aim of minimum fiber consumption on the premise of meeting the design requirement of burst pressure, and simultaneously avoid repeated iteration verification in the design stage and realize the efficient design of a winding layer.
Compared with the prior art, the invention has the beneficial effects that:
(1) The inventor researches and analyzes the first fiber winding layer calculation method based on the root reference point of the polar hole, so that the design of the whole winding layer of the gas cylinder is enriched and perfected, and the design reliability of the whole gas cylinder is effectively improved;
(2) Compared with the previous existing design method, the design method of the winding layer provided by the invention has the advantages that the complexity is greatly reduced, the problems of repeated iteration verification and the like caused by the fact that the first layer design depends on experience selection are overcome, and the design efficiency of the high-pressure IV type gas cylinder is greatly improved;
(3) Based on the winding thickness and the winding angle, the invention provides a calculation method of the weight of the fiber winding layer, realizes the rapid estimation of the whole quality of the gas cylinder, and provides a theoretical basis for the later experimental verification of the gas cylinder;
(4) The whole design method is scientific and efficient, has been proved to be effective by other methods, and has good application prospect.
Drawings
FIG. 1 is a schematic diagram of a closure head according to the present invention;
FIG. 2 is a schematic view of reaming in accordance with the present invention;
FIG. 3 is a graph of bearing capacity versus different positions of the reamer design of the present invention;
fig. 4 is a graph of a cross-sectional stress cloud of a wound layer under burst pressure calculated using finite elements.
Detailed Description
In order to make the technical scheme and the beneficial effects of the present invention fully understood by those skilled in the art, the following description is further made with reference to specific embodiments and drawings.
Example 1
A design method for a winding layer of an IV-type gas cylinder with the capacity of 9L comprises the following specific processes:
(1) The geometry, fiber and design parameters of the cylinders are shown in table 1.
Table 1 type IV gas cylinder parameters table
(2) Referring to the schematic geometric outline of the seal head shown in fig. 1, the direction parallel to the equator is the weft direction, and the direction perpendicular to the equator is the radial direction. And (3) sequentially calculating an elliptical coordinate expression of the end socket, the curvature radius of each point of the end socket and the film stress of each point of the end socket under burst pressure, and obtaining the winding angle and the layer number of the first winding layer which are 13 degrees and 10 layers respectively according to the stress state of the reference point and the bearing capacity of the first winding layer.
TABLE 2 calculation results of winding angle and number of layers of first layer fiber winding layer
(3) Referring to FIG. 2, r 0 is the pole bore radius, r 1 is the 1 st reaming radius, and r j is the j-th reaming radius. Reaming calculation starts from the root point of the polar hole along meridian line and positions the first winding layer below the cylinder bodyOr a point T θi≤Nθi, then reaming and winding the winding layer at the point, wherein if the arc length interval between two reamers is smaller than the set reaming interval KD, the number of winding layer layers is recalculated according to the reaming interval. Based on the principle and the method, the superposition effect is considered to sequentially perform reaming and winding for 5 times until the warp-weft strength of the end socket section reaches the design requirement.
The warp and weft direction fiber stress and the corresponding film stress relationship are shown in figure 3. In the figure, the horizontal axis is the radius of the cross section of the end socket, the vertical axis is the bearing capacity, the left graph is the comparison of the membrane stress in the warp direction at different positions and the bearing capacity of the winding layer after reaming, the right graph is the comparison of the membrane stress in the weft direction at different positions and the bearing capacity of the winding layer after reaming, the broken line represents the membrane stress, and the solid line represents the accumulated bearing capacity after the first layer/reaming. As can be seen from fig. 3, after multiple reaming, the fiber bearing capacities in both directions meet the film stress at the corresponding points, which indicates that the winding structure is reasonable in design. The corresponding reaming angles and layers are shown in table 3.
TABLE 3 reaming angles and layers
(4) According to the information of the spiral winding layers in Table 3, the bearing capacity of the spiral layers in the circumferential direction of the section of the cylinder body is calculated, the circumferential winding strength of the cylinder body is reinforced, and the number of layers of the circumferential winding layers is 28.
(5) According to the winding scheme and the fiber winding layer weight calculating method, the fiber consumption is evaluated, and the winding layer quality is 5.184kg according to calculation.
TABLE 4 fiber usage calculation table
| Layer classification | Hoop layer | First layer | Reaming for 1 time | 2 Times of reaming | 3 Times of reaming | 4 Times of reaming | 5 Times of reaming | Totals to |
| Single layer quality (kg) | 0.08175 | 0.115 | 0.113 | 0.1107 | 0.10965 | 0.1049 | 0.1011 | |
| Layer number | 28 | 10 | 4 | 4 | 4 | 2 | 2 | 54 |
| Quality (kg) | 2.289 | 1.15 | 0.452 | 0.4428 | 0.4386 | 0.2098 | 0.2022 | 5.184 |
In order to understand the feasibility of the method for optimizing the design of the winding enhancement layer of the composite gas cylinder, the method is verified by using a finite element method according to a winding design scheme. A WCM plug-in of the ABAQUS software is used for establishing a 1/4 solid model of a gas cylinder winding layer, the phenomenon of fiber accumulation attached to a pole hole cannot be reflected due to the limitation of the WCM plug-in, the thickness near the pole hole of the model is only about 2/3 of the actual winding thickness, and a larger error can be generated when a calculation result is near the pole hole, but no larger error is generated at other positions. An internal pressure of 210MPa was applied to the inside of the wound layer to obtain a stress cloud image of the wound layer as shown in FIG. 4.
As can be seen from fig. 4, when subjected to 210MPa, the composite fiber direction stress did not reach the composite fiber direction tensile failure strength (2520 MPa) except near the polar holes, and the average fiber direction stress near the polar holes was 4200MPa, consistent with the increase in stress due to thickness distortion. The wrapping layer stress substantially matches the calculated results in the design, thereby confirming the effectiveness and accuracy of the design of the present invention.
Claims (7)
1. The method for optimally designing the winding reinforcing layer of the composite gas cylinder is characterized by comprising the following steps of:
(a) Establishing an elliptical coordinate expression of the end socket
Wherein z represents the vertical distance from the parallel circle to the equator, r represents the radius of the parallel circle of the seal head, a represents the length of the major axis of the ellipse, and b represents the length of the minor axis of the ellipse;
(b) Calculating the curvature radius of different positions of the seal head according to the elliptic coordinate expression of the seal head
Wherein the method comprises the steps ofRepresenting the principal radius of curvature of the warp, R θ represents the principal radius of curvature of the parallel circular line, R represents the parallel circular radius of the seal head, and z represents the vertical distance from the parallel circular to the equator;
(c) According to the designed bursting pressure, calculating the stress state of each point of the end socket
Wherein the method comprises the steps ofRepresenting the film stress in the warp direction, N θ representing the film stress in the parallel circular line direction, and P being the design bursting pressure;
(d) Calculating the angle and thickness of the first spiral winding layer fiber according to the variable angle and variable thickness formula
αr＝arcsin(r0/r) (7)
Wherein alpha r represents a winding angle, t represents the thickness of fibers at each point of the seal head, R represents the radius of the cylinder body, R 0 represents the radius of a polar hole, and t fα represents the thickness of a section of the cylinder body of the winding layer with the winding angle alpha;
(e) According to the film stress of the polar hole position and the single-layer bearing capacity of the first winding layer, the number of the first winding layer is calculated, and the specific process is as follows: the point position which is not more than 5 bandwidths away from the root of the polar hole is selected as a reference point, and based on the head winding design method, the reference point fiber layer warp and parallel circular directions bear internal forces respectively as follows And N θi, calculating the angle and thickness of the first winding layer fiber according to the stress in the warp and parallel round line directions according to the film stress under the condition that the strength of the fiber layer just meets the design internal pressure according to the optimal design basis of the first layer fiber thickness, and selecting/>The specific calculation method is as follows:
tfθi＝Nθi/σisin2αi (10)
where the index i indicates the current position, Represents the thickness of the fiber at the point calculated according to the force applied in the warp direction, t fθi represents the thickness of the fiber at the point calculated according to the force applied in the parallel circular direction,/>Represents the radial internal force born by the fiber layer of the point, N θi represents the latitudinal internal force born by the fiber layer of the point, sigma i represents the fiber stress of the point, and alpha i represents the winding angle of the point;
(f) And (e) comparing the stress state and the bearing capacity of each position according to the result of the step (e), calculating the reaming winding position and calculating a reaming winding layer, wherein the specific process is as follows: according to the angles and thicknesses of fibers at different positions of the first winding layer, calculating the radial strength of each point of the winding layer And the parallel circular strength T θi, comparing the radial film stress/>, of each point of the seal headAnd parallel circular film stress N θi, starting from the root point of the polar hole along meridian line, positioning the first/>, under the winding layer to the position of the cylinder bodyOr a point T θi≤Nθi, at which hole reaming winding is performed; based on the same principle and method, the superposition effect is considered, and reaming and winding are sequentially carried out for a plurality of times until the warp-weft strength of the end socket section reaches the design requirement, wherein the specific calculation method is as follows:
Tθi＝∑σftfisin2αi (12)
where the index i indicates the current position, Representing the resultant force according to the warp direction, T θi representing the resultant force according to the parallel circular direction, sigma f representing the fiber playing strength;
(g) And (3) carrying out circumferential winding layer design on the cylinder body according to the circumferential bearing capacity of the spiral winding layer on the cylinder body section.
2. The method of claim 1, wherein: in the step (a), a is more than or equal to 80mm and less than or equal to 800mm, b is more than or equal to 50mm and less than or equal to 600mm.
3. The method of claim 1, wherein: step (e)
The angle alpha r of the middle first winding layer fiber ranges from 5 degrees to 30 degrees.
4. The method of claim 1, wherein: the first of step (f)Or the winding layer at the T θi≤Nθi point is 2-20, and the reaming times are not more than 8.
5. The method of claim 1, wherein: the number of the annular reinforcing layers in the step (g) is 2-6 greater than the calculated number of layers.
6. The method of claim 1, wherein: the weight of the filament wound layer is calculated as follows:
Wherein M represents the overall mass of the winding layer, t fα represents the single-layer thickness of the winding layer of the barrel section, ρ f represents the 60% fiber mass ratio composite density, z i represents the height of the spiral winding layer at the end socket, R i represents the reaming radius, R represents the barrel diameter, and L represents the barrel length.
7. Use of the method according to any one of claims 1-6 for designing, manufacturing a high pressure hydrogen storage cylinder.
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