Pressure vessel made of composition materials

FIELD: mechanical engineering.

SUBSTANCE: pressure vessel comprises metallic flanges mounted in its pole ports. The bearing surface of the shank of the metallic flange is made of two sections. The first section is conical and located at the base of the metallic flange, and the second section is convex and is located at the top of the flange. The length of the generatrix of the cone is no less than the width of the reinforcing belt made of cords and threads plus the shift of the plastic due to its deformation.

EFFECT: reduced sizes and enhanced reliability.

2 dwg

 

The invention relates to the field of engineering, namely, cylinder pressure, izgotovliaemye of composite material, and can be used to create solid-propellant rocket engines, chemical engineering and other industries.

From the patent literature is widely known construction telemechanic plastic pressure cylinders made of composite materials containing plastic casing and installed in the pin holes of the metal flanges. See, for example, SU 1089344. Known technical solution according to the patent of Russian Federation №2037735, CL F 17 C 1/00 92 was selected as a prototype. The flange includes a support shaft, which rests against the plastic power of the shell, and butting, to which are attached other design elements, such as cover. The disadvantages of this cylinder is elevated levels of the stress-strain state (SSS) of reinforcing layers at the edge of the pin hole, which reduces the carrying capacity of the container. The destruction of the cylinders in most cases occurs on the plastic cover in areas of pin holes. Therefore, in the calculations of shell this effect is taken into account by the introduction in the calculation formula of the coefficient of stress concentration, which is the value of 1.1 to 1.2. To compensate for the reduction in the bearing capacity of the membrane wound on the additional layers of plastic, which leads to an increase in the thickness of the plastic on 15-20% and a corresponding increase in weight of the container.

The main reason for the decline in the carrying capacity of the cylinder pressure with a curved-convex bearing surface of the shank is offset plastic generatrix of the shank due to the increase of the radius of the pin hole while turning the cross-section of the shank flange when the loading pressure, which leads to wrinkling of the plastic and increase the tensile stress in reinforcing the threads at the edge of the pin hole. In addition, the annular zone from pin holes with radius r0to the circumference, located at a distance of the width of the reinforcing tape along with radius rlthe number of reinforcing threads depends on the radius. The maximum thickness of the reinforcing material hmaxin the unloaded state is achieved on the circle with radius rl. In this section, the rigidity of the plastic maximum. On the edge of the pin hole, the thickness of the reinforcing material minimum (theoretically zero). So near the pole hole is a "loose" structure of plastic, which consists mainly of a binder. This leads to the additional effect of reducing the carrying capacity of the tank: the cracking of the binder with the damage of reinforcing filaments at the edge of the pin hole is participation.

Figure 1 shows the known structure of the cylinder pressure in the area of location of the flange. The shank flange 1 with a maximum radius b rests in contact with it plastic composite shell 2. When loading cylinder pressure due to the deformation of all points of the longitudinal section of plastic 2 move with increasing radius in the u-value. At the same time there is a rotation of the shank flange 1 on the corner θ. The center of rotation of the shank is at point O1where is the section with the maximum stiffness of the plastic after its offset relative to the shank. The dashed line shows the contour of the plastic, the dash-dotted contour flange when moved relative to each other. The contact surface of the shank and plastic are not the same and is "punching" (crushing) plastic shank whose value is maximum at the edge of the pin hole with a "loose" structure of the plastic.

Completely eliminates the wrinkling of the plastic shank flange in the case of a curved-concave bearing surface made in accordance with the technical solution according to the patent of Russian Federation №2187747. However, this increases the axial dimension of the cylinder, which for a number of structures is unacceptable, for example, when the cylinder pressure is building a rocket engine solid fuel.

Technical the second task is to reduce the mass of the cylinder pressure without increasing the axial dimensions by reducing the size of the plastic collapse on the edge of the pin hole.

The technical result is achieved in that the cylinder pressure of a composite material containing celimontana shell, pin holes which have metal flanges having a shank, which laid the plastic shell, the base surface of the shank consists of two parts: cone at the base of the shank and a curved-convex in the area of the peaks smoothly mating among themselves, with the radius of the transition cone area in a curved-convex should be not less than the value

rl+u,

where

rl- the radius of the circle at a distance of the width of the reinforcing tape from the pin holes;

u is the radial component of the displacement of the plastic in the area of the pin holes.

The technical result is ensured by the fact that the supporting surface of the metal shank flange consists of two parts, smoothly mating among themselves, which reduces the degree of discrepancy between contact surfaces under the action of pressure without increasing the axial dimension of the cylinder pressure and thereby reduces the amount of shear plastic shank on the edge of the pin hole.

From the diagram of deformation presented in figure 1, it follows that the total depth of the plastic collapse is determined by two components:

1. Crushing from radial displacement of the plastic relative to x is ostovich.

2. The collapse of the turning shank flange.

The first component depends on the shape of the contact surface. The magnitude of the collapse can be defined graphically (figure 1). At this point, contour plastic with maximum rigidity with initial radius rl) moves along the surface of the shank at the point O1. The magnitude of the radial component of u under the action of the pressure in the cylinder is determined by the radius of the pin holes r0and annular plastic deformation due to the closeness of the trajectories of reinforcing threads in the area of the pin hole to the tangents to the circles may be taken equal to the tensile strain of reinforcing threads ε

u=ε·r0.

The greater the change in the meridional curvature in the area from pin hole to the circumference with radius rlthe more the depth of the collapse. Therefore, the introduction of a conic section (meridional curvature equal to zero) on the support surface of the shank eliminates wrinkling from plastic displacement relative to the shank. To provide a "slip" throughout an annular zone of plastic between the circles with radii r0and rlon the conical surface of the shank, the radius of the transition cone rtoin the curved-convex surface, which is located at the top of the shank should be not less than the value

rto=r l+u.

The second component of the plastic collapse does not depend on the shape of the contact surface and is determined by the angle of rotation of the shank θ about a point of the contour Of1with radius rl+u, the corresponding maximum rigidity of the plastic. Given that the radial component of the plastic displacement u is the same for all points of the plastic, and the small value of the angle of rotation θdepth shear along the z axis to the point of the contact surface of the plastic with an initial radius R is determined by the formula

Δzθ=θ·(rl-r).

The calculated estimates of the number of large solid rocket motor casings showed that for a curved-convex contact surface of the first component of the plastic collapse (from offset) is in the range of 20-50% of the total collapse, so the introduction of a tapered area on the support surface of the shank allows to reduce the amount of plastic collapse by the specified value.

Figure 2 shows the proposed design of the contact zone of the shank 1 with 2 plastic. Part of the support surface of the shank 1 has a conical section from point To point Of1. The dashed line shows the outline presented earlier in figure 1, the curved-convex support surface. From the point O1to the top of the shank with radius b is curved, issue CLY plot. The angle of the tangent to the contact surface at the radius b is left unchanged, since it is determined by the equilibrium profile of the rest of the bottom is not in contact with the shank. From figure 1 it is seen that the proposed bearing surface of the shank does not increase the axial dimension of the cylinder pressure.

Thus, the use of tapered contact surface at the base of the shank decreases the collapse of the inner reinforcing layers shank flange in the area of the pin holes and eventually reduces the mass of the cylinder pressure and increase reliability without increasing the axial dimension.

The cylinder pressure of a composite material containing celimontana shell, pin holes which have metal flanges having a shank, which laid the plastic shell, characterized in that the bearing surface of the shank consists of two parts: cone at the base of the shank and a curved-convex in the area of the peaks smoothly mating among themselves, with the radius of the transition cone area in a curved-convex should be not less than the value

rl+u,

where rl- the radius of the circle at a distance of the width of the reinforcing tape from the pin holes;

u is the radial component of the displacement of the plastic in the area of the pole is TVersity.



 

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