Search

EP-3942217-B1 - PRESSURE VESSEL WITH CIRCUMFERENTIAL REINFORCING ELEMENTS

EP3942217B1EP 3942217 B1EP3942217 B1EP 3942217B1EP-3942217-B1

Inventors

  • DUPIN, Victor
  • Teixeira, David
  • SAEEDI, Navid

Dates

Publication Date
20260513
Application Date
20200318

Claims (13)

  1. Pressure vessel, comprising a tubular part and two bottoms (5), said two bottoms (5) being positioned at the ends of said tubular part, said tubular part comprising a cylindrical wall (1) and at least one first ply of circumferential reinforcing elements (2), said first ply of circumferential reinforcing elements (2) being wound around said cylindrical wall (1), characterized in that the modulus of elasticity of the material of the cylindrical wall (1) is lower than the modulus of elasticity of the material of said first ply of circumferential reinforcing elements (2), in that the material of said circumferential reinforcing members (2) of said first ply is a polymer, preferably an aramid fibre, a nylon polyamide, a polypropylene, or a polyethylene, and even more preferably a high-strength polyethylene and in that the vessel comprises at least one sliding connection (J) between said cylindrical wall (1) and at least one of said two bottoms (5), said sliding connection (J) allowing a relative axial movement between a bottom (5) and said tubular part.
  2. Vessel according to Claim 1, wherein the modulus of elasticity of the material of the cylindrical wall (1) is at least 10%, preferably at least 30%, lower than the modulus of elasticity of the material of said first ply of circumferential reinforcing elements (2).
  3. Vessel according to either of the preceding claims, wherein at least one of said two bottoms (5) is a convex, preferably spherical or hemispherical, bottom.
  4. Vessel according to one of the preceding claims, wherein the vessel comprises at least one second ply of axial reinforcing elements (10), said axial reinforcing elements (10) extending in the axial direction.
  5. Vessel according to Claims 3 and 4, wherein said axial reinforcing elements (10) of said second ply continue at the convex bottom in the direction of the axial end of said convex bottom (25), forming a star € on said convex bottom.
  6. Vessel according to Claim 4, wherein said second ply of axial reinforcing elements (10a) is positioned inside the inner cylinder defined by said cylindrical wall, said axial reinforcing elements (10a) of said second ply being regularly distributed around the circumference of said cylindrical wall.
  7. Vessel according to Claim 4 or 6, wherein said second ply of axial reinforcing elements (10b) is positioned outside said tubular part, said axial reinforcing elements (10b) of said second ply being regularly distributed around the circumference of said tubular part.
  8. Vessel according to one of the preceding claims, wherein the material of said cylindrical wall (1) is a metallic material, preferably a steel, or a polymer.
  9. Vessel according to one of the preceding claims, wherein said circumferential reinforcing elements (2) of said first ply are embedded in a protective layer (3).
  10. Vessel according to one of the preceding claims, wherein said circumferential reinforcing elements (2) of said first ply and/or said axial reinforcing elements (10) of said second ply have a circular, substantially circular (2c) or rectangular (2r) section.
  11. Vessel according to one of the preceding claims, wherein said sliding connection (J) is positioned between the outer diameter of said cylindrical wall (1) and the inner diameter of said bottom (5).
  12. Vessel according to one of the preceding claims, wherein said sliding connection (J) is positioned between the outer diameter of said bottom (5) and the inner diameter of said cylindrical wall (1).
  13. System for storing and recovering energy, comprising at least one compression means, at least one expansion means, at least one heat storage means and at least one compressed air vessel according to one of the preceding claims.

Description

technical field The present invention relates primarily to the field of compressed air energy storage but could be applied to other pressure vessel systems. Electricity production from renewable energy sources, such as solar panels or onshore and offshore wind turbines, is booming. The main drawbacks of these production methods are their intermittent nature and the potential mismatch between production and consumption periods. Therefore, it is important to have a means of storing energy during production to release it during periods of consumption. There are many technologies that allow this balance. Among them, the best known is the Pumped Storage Water Transfer Station (PSW), which uses two water reservoirs at different altitudes. Water is pumped from the lower reservoir to the upper reservoir during the charging phase. The water is then sent to a turbine, towards the lower reservoir, during the discharge phase. The use of different types of batteries (lithium, nickel, sodium-sulfur, lead-acid...) can also meet this need for energy storage. Another technology, flywheel energy storage (FES), involves accelerating a rotor (flywheel) to a very high speed and maintaining the energy within the system as kinetic energy. When energy is extracted from this FES system, the flywheel's rotational speed is reduced, according to the principle of conservation of energy. Adding energy to the FES system consequently increases the flywheel's speed. Energy storage technology using compressed gas (often compressed air) is promising. The energy produced but not consumed is used to compress air to pressures between 40 bar and 200 bar using compressors (which can be multi-stage). During compression, the air temperature increases. To limit the cost of storage tanks and minimize the compressor's electricity consumption, the air can be cooled between each compression stage. The compressed air is then stored under pressure, either in natural cavities (caves) or in artificial reservoirs. During the electricity production phase, the stored air is then sent to turbines to generate electricity. During expansion, the air cools. To avoid... Because temperatures are too low (-50°C) and can damage the turbines, the air can be reheated before expansion. Such installations have been operating for several years, such as the Huntorf unit in Germany, which has been operating since 1978, or the Macintosh unit in Alabama, USA, which has been operating since 1991. These two installations share the characteristic of using stored compressed air to power gas turbines. These gas turbines burn natural gas in the presence of pressurized air to generate very hot (550°C and 825°C) and high-pressure (40 bar and 11 bar) combustion gases before expanding them in turbines that generate electricity. This type of process emits carbon dioxide. A variant is under development. It is an adiabatic process in which the heat from air compression is recovered, stored, and released back into the air before it is expanded. This is the AACAES technology (from the English "Advanced Adiabatic Compressed Air Energy Storage"). In an AACAES system, compressed air is stored in a tank independently of heat storage. In such a system, the air is stored at a temperature close to ambient temperature (ideally below 50°C). Previous technique A reservoir conforming to the preamble of claim 1 is known to EP2990714 A1 . To date, compressed air tanks, and more broadly, pressure vessels, are closed containers consisting of at least two ends, also called "ends," and possibly connected by an intermediate part such as on the Fig 1 where P represents the internal pressure. In this figure, the tank is represented, without limitation, by a cylindrical section (the r direction being the radial direction and the z direction the axial direction of a cylindrical coordinate system associated with the tank – this coordinate system is used in the other figures and will not be detailed in each figure) of internal diameter Di. Thus, this type of tank can be, for example, a sphere made up of two hemispheres or a cylindrical container made up of two ends connected by a cylindrical section. The connections between the different parts are rigid, of the fixed type. Furthermore, these tanks are most often made of steel to withstand high pressures. Given the large storage volumes and high pressures, the cost of constructing these large-volume pressure tanks is very high, primarily due to the amount of steel required. In a closed cylindrical tank, bottom effects, resulting from the application of internal pressure on the tank bottom, generate tensile forces in the longitudinal direction and therefore axial stresses σll, as illustrated in the Fig. 1 Regardless of the shape of the bottom (flat, domed, hemispherical, etc.), the bottom effects of this type of tank generate the following average longitudinal stress in the main part of the tank: σll=PDi24tDi+t Where P is the pressure applied in the reservoirDi : the