Sealing element stiffness for pressure vessel, reinforced filament winding fiber material

 

(57) Abstract:

Use: in the manufacture of pressure vessels. The essence: a first fixing groove made in the form of a swallow's tail, the outer surface of the annular flange, the second fixing groove, made in the form of a dovetail, in the inner surface of the annular flange, and the shell separated in the annular flange with the outer part outside the annular flange and the inner part inside the annular flange, the first made in the form of a dovetail, a protrusion on the outer part of the casing for fixing in the first fixing groove in the outer surface of the annular flange, and the second, made in the form of a dovetail, the protrusion on the inner part of the casing for fixing the second fixing groove in the inner surface of the annular flange. 2 C. and 8 C.p. f-crystals, 3 ill.

The invention relates to an improved design of the sealing element of rigidity in the form of lugs neck for strengthening (hardening) at the interfaces between the outer skin (i.e. body) of winding a fibrous composite material and non-metallic SS="ptx2">

In many cases the design of the apparatus or pressure vessels is very important to provide the combination of low weight of the device with its high strength and high corrosion resistance. For many years these criteria when designing such high pressure apparatus was able to observe through the manufacture of pressure vessels made of composite materials, for example from a large number of winding layers of fiberglass or synthetic fibers of various types, bonded with thermosetting epoxy resin. When this lining or elastic cylinder of elastomer or other non-metallic elastic material is suspended inside the case of winding a fibrous composite material so as to ensure a reliable sealing of the pressure vessel and to prevent the possibility of contact inside the vessel environment (e.g., gas or liquid) from a composite material.

Made of winding a fibrous composite material pressure vessels often have a spherical or cylindrical shape, and the ends or end faces are, as a rule, svasti as having a mouth (or the Central intake of the working environment) the so-called boss (or thickened in its Central part of the insert) is used to secure a tight connection of the inner linings made from the filament winding of composite material outer skin in the locations of the inlet ports, executed in the past, to create a high pressure in the vessel. This sealing element must connect the lining with the outer skin of the vessel so that the working environment could not penetrate into the area between the lining and the outer casing of the pressure vessel. In practice, for example, in the aerospace industry that you want made of composite materials the pressure vessels could reliably create and maintain ultra-high working pressure, such pressure as 25,000 pounds/inch2. This means that with the increase of the internal pressure, i.e. the pressure in the vessel to the above values, the structural elements of the pressure vessel, and the first areas of mutual coupling of the sealing element stiffness of the lining and the outer skin are exposed to extreme loads.

And more specifically this means that if you increase the pressure inside the vessel to high values in the area between the sealing element of rigidity and made of a composite material outer skin creates a voltage collapse, resulting in dramatically changing Grady is what occurs in the outer surface of the outer skin of the voltage. Shear stress is created in the area between the sealing element stiffness and internal lining due to the occurrence of jumps or breaks in the relative displacement, which is caused by the load variation during the creation of a high pressure vessel. In addition, radially spaced supporting part of the sealing element stiffness exposed to excessive bending stresses, which can lead to the destruction of the sealing element stiffness.

It is extremely important that in the process of creating high pressure in the vessel lining and the outer skin remained strongly connected with the sealing element stiffness, despite the fact that they're lining and panelling, exposed to extremely adverse loads.

The invention aims at eliminating the above drawbacks associated with uneven acting on the structural elements of the pressure vessel loads and the complexity of its seal, through the creation of an original design of the sealing element of rigidity in the form of having the neck portion of the boss for pressure vessel above type, the implementation is Lorena task is to develop a new improved version of the design of the sealing element of rigidity in the form of having the neck portion of the boss for hardening plot pairing between made of winding a fibrous composite material outer skin and a non-metallic inner shell in a spherical part of the pressure vessel.

According to one variant of the practical implementation of the invention the sealing element of rigidity in the form of having the neck portion of the boss is placed in the hole in the spherical part of the pressure vessel, having made of winding a fibrous composite material outer casing (housing) and non-metallic inner lining. According to the present invention, the sealing element stiffness has a tubular neck protruding outwards from the inner cavity of the pressure vessel, and an annular supporting flange located radially in the direction from the inner end of the cap and serves as a bearing support for the peripheral part of the zone pairing exterior cladding and internal lining around the center hole. Radially to the support flange posted by a connecting flange, which is shifted slightly relative to the supporting flange. In this embodiment of the invention the outer surface of the connecting flange is offset by some distance inward relative to the outer surface of the support flange and the inner surface of the connecting flange is offset by some distance outward relative to the inner surface of the support flange. This offset is coy, which includes the corresponding shape of the cross section of the protrusion is present on the inner shell.

This embodiment of the present invention the locking grooves made on each of two opposite axial surfaces of the connecting flange. When this is performed on the outer surface of the connecting flange and the retaining groove with its open side facing outwards, and the locking groove is made on the inner surface of the connecting flange, with its open side facing the inside. The bottom wall of each of the locking grooves is located between the respective two mutually beveled side walls, providing a more reliable fixation protrusions lining in the corresponding fixing grooves (grooves) of the connecting flange. Due to the fact that the inner and outer surface of the connecting flange is displaced above with respect to the outer and accordingly relative to the inner surface of the support flange, and through the above deployment and implementation of the locking grooves in the connecting flange can significantly reduce likely the COP rigidity and, therefore, there is a leak of fluid or gas through the Assembly thus a plot of coupling the outer casing with the inner lining.

In order to reduce the shear stress or shear stress occurring at the site mate o golovinskogo element stiffness liners are in the process of creating a high operating pressure in the cavity of the vessel, between the outer surface of the annular support flange and the inner surface of the outer sheathing posted reducing tangential stresses the layer of non-metallic material. This intermediate layer may be made of any plastic, elastomeric or other non-metallic material and can be applied by molding or manufacture by cutting a sheet of the required size of the sheet.

Proposed according to the present invention the original design implementation sealing element stiffness allows, in addition, to reduce the likelihood of damage to structural elements of the pressure vessel in the process of creating a high voltage in it. In one preferred main plating in the process of creating high working pressure in the vessel. Simultaneously, the mounting flange has a relatively large thickness, which eliminates the risk of excessive bending stresses in the bearing and the connecting flanges. Proposed according to the invention the sealing Golovinsky element stiffness can be made of alloys of aluminum, Nickel, titanium, steel or other metals.

According to another possible variant of implementation of the present invention the inner shell or lining may be made of the received pneumoperitoneum, that is blow molded, high density polyethylene (abbreviated as HDPE). In this embodiment of the invention near the inlet opening through which the vessel creates a high working pressure, for sealing halloweenabaloo element stiffness attached axisymmetric fastening element pair, which can be conveniently and securely fasten the inner lining. This fastening element pair is made, preferably, obtained by injection molding of high density polyethylene, which is in the process of hardening shrinks exactly the form o golovinskogo ale is connected in the same way as is the case for plastic molding directly to the item pair. Then lock the nut is screwed through the Central hole in the neck of the sealing element stiffness up until the plastic element pair is securely fixed in the right place.

Other objectives, features and advantages of the present invention will become clearer from the subsequent detailed description of specific examples of its implementation with reference to the accompanying drawings.

In Fig. 1 shows a partial section of the spherical end of the axisymmetric pressure vessel, equipped with a sealing golovanovsky element stiffness, according to the present invention; Fig.2 same as in Fig.1, and the proposed sealing Golovinsky element stiffness is connected to the pressure vessel only along one side of the vessel, and the inner lining his boss comes only in one of the locking grooves made in the radial posted by the flange; and Fig.3 is a partial longitudinal section of the spherical end of the axisymmetric pressure vessel containing another option o Golovinskoye openlogo, preferably, the spherical end of the axisymmetric vessel 10 high pressure. The vessel 10 consists of a fiber reinforced casing 12 and non-metallic inner lining 14. The sealing element 16 of the stiffener as having the neck portion of the boss, in accordance with the present invention, sticking out from the vessel 10 through a high pressure Central hole 18 made in the outer casing 12. In o girlofyourdream the stiffening element 16 has a Central inlet opening 20 to create a high operating pressure in the vessel 10 by supplying fluid (e.g. gas or liquid) under high pressure into the internal cavity of the vessel 10 high pressure. It should be noted, however, that the idea of the present invention can also be successfully used in pressure vessels with the so-called nonpolar inlets. In particular, according to the present invention, the sealing Golovinsky element stiffness can be placed in the inlet hole made in a completely spherical pressure vessel. Between the case 12 (the outer shell), o golovanovsky element 16 of the stiffening and lining 14 posted by a thin intermediate layer 22, PR is asdah their mutual coupling and, therefore, to prevent damage to the housing 12 or the inner lining 14 in the process of creating a high operating pressure in the inner cavity of the vessel 10. About constructive implementation of this protective layer 22 will be discussed in more detail in the further description of the invention.

The housing 12 is made in the form of a single, well-known reinforced construction unit made of a composite material, namely of the fibrous reinforcing material embedded in the binder material in the form of synthetic, for example, polymeric resins. The fibrous material may be a glass fiber, aramid fibers (i.e. fibers of aromatic polyamide, carbon, graphite fiber, or any other known fibrous reinforcing material. As the binder resin (polymer) can be used epoxy resin, polyester resin, vinyl polymer, thermoplastic or any other suitable material containing a resin, which is able to provide high fracture resistance, which is necessary for reliable operation of the pressure vessel in the specified operating mode.

cation, pneumoperitoneum, injection molding or any other known method. O Golovinsky the stiffening element 16 is made preferably of aluminum alloy, steel, Nickel or titanium, although, as it is obvious, for the manufacture of the element 16 and other suitable metals and non-metallic materials, such as composite materials. A thin layer 22 may be made of plastic or other nonmetallic material by molding or simply cut a sheet of the desired dimensions of the sheet.

As shown in Fig.1 proposed according to the present invention, the sealing Golovinsky element stiffness 16 is protruding out from the pressure vessel neck 24 with tapering down on the cone neck 26, passing through the Central hole 18 made in the housing 12. The taper of the narrow neck 26 is selected so that the neck 26 formed concave peripheral (ring) groove in the form of a trough, which includes a body 12 made of a fibrous material embedded in a binder resin. Such coupling of the housing 12 with the neck 26 and, consequently, with the sealing golovanovsky element 16 gestkoe out of the vessel 10.

Right inside of the pressure vessel 10 radial neck 24 posted by annular bearing flange 28 with the outer surface 30, which enables you to evenly distribute the load arising from the creation of high working pressure in the cavity of the vessel 10, the perimeter of the Central hole 18 made in made of composite material of the housing 12. Width W1support flange 28 is selected so that the overall diameter of the flange 28 was large enough to prevent possible damage to the housing 12 when creating a high operating pressure in the cavity of the vessel 10.

In addition, a thin protective layer 22 is partially laid between the support flange 28, the liner 14 and the casing 12 in order to even more reduce the risk of possible damage to the vessel 10 when the latter create a high working pressure. It should be noted that the creation of a high operating pressure in the inner cavity of the vessel 10 high pressure leads to considerable deformation of the fillet (approximately spherical) end of the vessel 10 high pressure, which may occur relative sliding between the inner surface of the housing 12 and the above relative sliding, as well as to mitigate the influence of shear stresses, or otherwise arising on the above areas of mutual coupling of the housing 12, the liner 14 and the abutment flange 28, the intermediate protective layer 22 is laid inside the rounded end of the vessel 10 high pressure (on the plane mutual coupling assemblies 12, 14, and 28) at the site, the length of which is approximately equal to the diameter D1ring, or rather the cylindrical part of the vessel 10 high pressure.

The annular flange 32 protrudes radially outward beyond the support flange 28 at a distance of W2. While the outer surface 34 of the connecting flange 32 is shifted inward relative to the outer surface 30 of the support flange 28 at a distance of T1and the inner surface 36 of the connecting flange 32 is displaced outward relative to the inner surface 38 of the support flange 28 at a distance of T2. This means in other words that the thickness T3support flange 28 sufficient to limit the bending stresses in the sealing element stiffness 16 to an acceptable level in the process of creating high working pressure in the vessel.

The sealing element 16 ill the and groove, namely 40, made on the outer surface 34 of the connecting flange 32 and the second groove 42 is made on the inner surface 36 of the flange 32. The lining 14 is equipped with ledges 44 and 46 that are fixed in the fixing grooves 40 and 42, respectively.

The locking groove 40 to its open part facing outwards, and its bottom wall 48 is located between two mutually sloped side walls 50. In other words, this means that the groove 40 has a cross section in the form of a dovetail. It is obvious that in accordance with the object of the present invention can be provided, and other possible forms of cross-sectional profile of the locking grooves or slots, providing a reliable mechanical fixing of the inner shell to the sealing element stiffness.

The locking groove 42 is made on the inner surface 36 of the connecting flange 32 and the bottom wall 52 of the groove 42 is located between two mutually sloped side walls 54. The cross-section of the locking groove 42 is, thus, also dovetail (i.e. trapezoidal shape). Due to the fact that the cross-sectional profile is made on the lining 14 of the projections 44 and 46 meet ROFILE cross-section of the grooves 40 and 42 is determined by the inclination of the oblique side walls 50 and 54, respectively), provided reliable engagement and reliable fixation of the lining 14 on the sealing element 16 of rigidity, which in turn prevents the possibility that will leak under pressure medium through the gap between the liner 14 and the casing 12.

Since the connecting flange 32 is made with offset support flange 28, namely the outer surface 34 of the connecting flange 32 is shifted inward relative to the outer surface 30 of the support flange 28 at a distance of T1and the inner surface 36 of the connecting flange 32 is displaced outward relative to the inner surface 38 of the support flange 28 at a distance of T2decreases the likelihood that the lining 14 will be pushed out of engagement with the sealing element 16 of rigidity under high working pressure in the vessel 10. The risk of shell 14 from engagement with the sealing element 16 stiffness is reduced, in particular due to the fact that due to the above displacement of the inner and outer surfaces of the connecting flange 32 provides a large enough surface area mutual sealed mates lining 14 with soedinitelnye from the vessel 10 during a high pressure.

In Fig.2 shows another embodiment of a sealing element stiffness according to the present invention. In this embodiment, the liner 14 is fixed in only one annular locking groove 40, is made on the outer surface 34 of the connecting flange 32. In shown in Fig.2 embodiment of the invention the inner shell 14 with only one annular ledge 44 that interacts with the sealing element 16 of rigidity.

In Fig. 3 shows another embodiment of a sealing element of rigidity, namely element 56, intended for placement in the vessel 58 high pressure, made of winding a fibrous composite material. The pressure vessel 58 has a housing 60 made of a reinforcing fibrous composite material, and the lining 62 of non-metallic material. The inner shell 62 is preferably made from a received pneumoperitoneum (i.e. moulding) high density polyethylene (abbreviated as HDPE). Sealing element 56 rigidity has a tubular neck 64 extending axially outward from the vessel 58 high pressure through the Central hole 66, done the wow section, through which the working medium (gas or liquid) can be introduced under high pressure into the internal cavity of the vessel 58.

Radially on the outside of the cap 64 is placed directly inside the vessel 58 annular bearing flange 70 of the inclined outer surface 72 and having the opposite inclination of the inner surface 74. This means that the surfaces 72 and 74 of the flange 70 converge with each other at the peripheral part of the flange 70. The outer surface 72 provides the load distribution caused by the creation of high working pressure in the cavity of the vessel 58, the perimeter of the center hole 66, made in made of composite fibrous material housing 60, in order to prevent possible damage when the vessel 58 create a high pressure. The inner surface 74 has a notch 75, located near the inlet 68 and the groove 77, facing its open part of the axially inside of the vessel 58. On the appointment of the notches 75 and groove 77 will say a few more below.

Between the housing 60, the sealing element stiffness 56 and the inner shell 62 is placed a thin layer 76 that is designed to limit the influence of tangential stresses the working pressure in the vessel 58. Structurally, this protective or compensatory layer 76 is made in the form of two mutually diverging sheet strips 78 and 80, from which the gasket 78 is laid between the outer surface 72 of the support flange 70 and the inner surface of the lining 60, sheet and strip 80 is placed between the inner surface 74 of the support flange 70 and the outer side of the inner shell 62. Layer 76 to compensate for the influence of shear stresses is made, preferably, of a material capable of diminish the effect of shear stresses caused by the relative sliding and emerging, or otherwise, in areas of mutual coupling support flange 70, lining 62 and the housing 60 when the vessel 58 create a high pressure. It was found that for the manufacture of layer 76 with the desired characteristics to compensate for the tangential stresses are best obtained by injection molding of thermoplastic elastomers, such as Thermoelastoplastic (thermoplastic rubber).

Lining 62 is attached to the sealing element 56 rigidity using axisymmetric fastener 82 mates, which is made preferably from the obtained injection-molded polyethylene you the NTA 56 rigidity, as shown in Fig.3. More precisely, such a high-density polyethylene, solidify, forming an elongated sleeve 84 that is located in the inlet hole 68, and a radially directed flange or shoulder 86, which is the recess 75 on the inner surface 74 of the support flange 70. High-density polyethylene flows into the groove 77 and, thus, forms a clamping or locking protrusion 88, whose shape follows the shape of the cross section of the groove 77, thus ensuring reliable mutual fixation of the fastening element 82 and a centrally located sealing element 56 rigidity. In cases of practical application, when you want a more durable fastening element 82 mates to the sealing element 56 rigidity, prior to molding of high density polyethylene on the sealing element 56 is pre-applied coating of binder material. After a reliable attachment of the fastening element 82 mates to the sealing element 56 of the stiffness of the connection is made lining 62 with the mounting element 82 by a common connecting weld seam 90. For reliable connection of the lining 62 of the high-density polyethylene with the fastening element 82 mates can successfully ispair> Reliable fixation of the fastening element 82 pairing can be improved by means of nuts 92, which is injected through the inlet 68 of the sealing element 56 rigidity and tighten to ensure a reliable fixing of the peripheral end of the elongated sleeve 84 has an internal stepped side wall 93 of the cap 64. When this sealing ring 94 is clamped between the nut 92 and the fixing element 82.

Made according to Fig. 3 sealing element 56 rigidity very effectively reduces the possibility of leakage of the medium from the inner shell 62 due to the fact that the main path of possible leakage, that is, the region of the coupling on which the peripheral end of the sleeve 84 of the fastening element 82 rests against the sealing element 56 rigidity (in the boss 56), in this embodiment of the invention as would be moved to the mouth of the pressure vessel and then into the area behind the nut 92. This means that the above area mates are not exposed to high pressure generated in the vessel 58, thereby minimizing the possibility of leakage of the medium from the vessel 58. Moreover, as shown in Fig.option 3 implementation of the present invention provides isolation will condense is no possibility of contamination of the contents in the vessel 58 by impurities and corrosion of the element 56.

It is obvious that the present invention can be implemented in other ways that do not violate its fundamental principles. The above examples of the practical implementation of the invention should, therefore, be considered in all respects as employees for purposes of illustration and not as limiting the possible scope of the invention. In addition, the present invention should not be limited to use only those parts and structural elements that are specified in this description.

1. Sealing element stiffness for a pressure vessel having an outer casing of the winding of fibrous material and an inner shell of non-metallic material, and the system comprises a boss having a tubular neck protruding out through a hole in the outer shell, and an annular flange located radially in the direction of the end cap inside the vessel, while the annular flange has an outer surface to enhance the perimeter of the hole in the shell, wherein there is a first locking groove made in the form of a swallow's tail, the outer surface of the annular flange, the second fixing Kanata disconnected in the annular flange with the outer part outside the annular flange and the inner part of the inside annular flange, the first, made in the form of a dovetail, a protrusion on the outer part of the casing for fixing in the first fixing groove in the outer surface of the annular flange, and the second, made in the form of a dovetail, the protrusion on the inner part of the casing for fixing the second fixing groove in the inner surface of the annular flange.

2. Item under item 1, characterized in that between the outer surface of the annular flange and the inner surface of the outer shell is a layer for reducing shear stresses, separate from the shell, to reduce the relative displacement between them during the creation of a high pressure vessel.

3. Item under item 1, characterized in that it includes a layer for reducing shear stresses, located between the outer surface of the annular flange and the inner surface of the outer shell to reduce the relative displacement between them during the creation of a high pressure vessel.

4. Item under item 2 or 3, characterized in that the layer for reducing shear stresses, made of a thermosetting elastomer.

5. Element according to any one of paragraphs.1 to 4, characterized t is within the outer surface, spaced from the outer shell, and the first made in the form of a dovetail, the locking groove is in the outer surface of the connecting flange.

6. Item under item 5, wherein the flange has an inner surface which is offset from the inner surface of the annular flange.

7. Item under item 6, characterized in that the second, made in the form of a dovetail, the locking groove is in the inner surface of the connecting flange.

8. Element according to any one of paragraphs.5 to 7, characterized in that the outer surface of the connecting flange is offset from the outer surface of the annular flange.

9. Element according to any one of paragraphs.1 to 8, characterized in that the lug is made of a material selected from the group including aluminum alloys, steel, Nickel and titanium or composite materials.

10. Sealing element stiffness for pressure vessel containing a tubular neck and an annular flange located radially outwards from the lateral wall of the filler neck inside the vessel, with a tubular neck sticking out through the hole in the round end of the outer shell the participation is on the side of the outer surface of the annular flange, and from the side coaxially last inner surface in the annular flange is made of the fixing groove, and the inner shell of the pressure vessel is made of non-metallic material and provided with a protrusion located in the locking groove, and the cross-sectional shape of the protrusion corresponds to the cross-sectional shape of the fixing groove, and the inner surface of the outer shell in the area of its rounded end posted by ensuring the reduction of stress, the shear layer, characterized in that the annular flange is provided with an additional locking groove located on the side of its outer surface and the inner jacket are made with extra protrusion located in the additional locking groove, moreover, the cross-section of the additional protrusion shape corresponds to the cross section of the additional locking grooves.

 

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