JPH0811992B2 - Flange joint structure - Google Patents

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a flange joint structure for general industrial piping equipment and the like excluding automobile exhaust pipe systems, and in particular, facing flanges and a spiral gasket between the facing flange sealing surfaces. The present invention relates to a flange joint structure in which a plurality of bolts are fastened in a state in which is clamped.

[0002]

2. Description of the Related Art Generally, in this type of flange joint structure, generally, a flange sealing surface, which is a gasket pressing surface of a facing flange, is parallel to each other. As the spiral gasket to be loaded between the flange sealing surfaces, a spirally polymerized metal hoop bent in a V-shaped or W-shaped cross section and an inorganic filler such as expanded graphite tape are used. ing. Thus, according to such a flange joint structure (hereinafter referred to as "conventional joint structure"), the spiral gasket is loaded between the flange seal faces, and the flanges are tightened to sandwich the spiral gasket between the flange seal faces. By pressing, the flange can be connected in a sealed state.

[0003]

However, in the conventional joint structure, it is not possible to secure the sealing performance at a low tightening surface pressure. That is, in the spiral gasket (hereinafter referred to as "conventional gasket") used in the conventional joint structure, the overlapping annular layers of the hoop and the filler are engaged with each other in a corrugated form. Although the hoop is compressed and deformed in the axial direction, the filler does not flow smoothly to the bent portion, so that a gap is created between the hoop and the filler, and a so-called leak path is likely to occur.

Further, since the flange sealing surface has a parallel plane shape, when vibration is applied to the flange, relative movement is likely to occur between the conventional gasket and the sealing surface.
As a result, the filler wears and the sealing performance deteriorates, resulting in a problem in durability. Also, when the parallelism between the sealing surfaces is impaired by vibration, the conventional gasket is difficult to deform in the axial direction, so it is not possible to follow such changes in parallelism, and the contact between the sealing surface and the gasket becomes insufficient, The sealing performance is reduced. Therefore, it cannot be used in a device or place where vibration is applied, and its use is greatly limited.

An object of the present invention is to provide a flange joint structure capable of exhibiting a good sealing function at a low tightening surface pressure without causing such a problem.

[0006]

In order to achieve the above object, in the flange joint structure of the present invention, in particular, a conical surface, a hemispherical surface, etc., which intersects both flange sealing surfaces with respect to the axis of the flange in an inclined manner, is used. Constructed in parallel with the inclined intersection plane
At the same time , it is proposed that the spiral gasket is formed by superimposing a flat band plate-shaped metal hoop and a tape-shaped filler in a spiral shape that is relatively slidable in the axial direction.

[0007]

[Function] Both the hoop and the filler are formed into a flat plate shape that is straight in the axial direction, and are relatively slidable in the axial direction.
Since Tei Ru, when an external force is applied in the axial direction, and slip between them, telescoping axially gasket
Can be transformed into And the gasket is the axis
By transforming it in the direction of telescope,
End face in the axial direction (hereinafter "gasket end face")
Can be freely transformed into any non-planar shape such as a conical surface.
Can be made. At this time, the hoop and filler should be flat.
Since the plate shape is maintained, one gasket end surface expands.
If you grab it, the end face of the other gasket will be dented.
The shape of the end face of the sket is the same. That is, one of the
Make the end face of the sket a convex (or concave) non-planar shape
And the other gasket end face is concave (or convex) and has the same shape.
Become a state . Therefore, the gasket should be conical, hemispherical, etc.
Load the space between both parallel flange seals in the shape of an inclined cross surface , and tighten the bolts .
The seal surface contact surface conforms to the corresponding flange seal surface and is deformed, so that each seal surface contact surface can properly contact each flange seal surface. At this time, since the hoop and the filler do not have the bent portion unlike the conventional gasket, the filler flows smoothly during the axial deformation, that is, the telescopic deformation, so that the hoop and the filler do not flow. There is no gap between and. Moreover, when the telescope shape is deformed in this manner , the hoop is reduced in diameter with it, that is, the hoop is reduced in diameter so as to compress the filler in the radial direction. Adhesion and eventually gasket density are increased. In particular, when the flange sealing surface has a shape that inclines toward the center, such as a conical surface or a hemispherical surface, tightening the gasket causes a component force to compress the gasket end toward the center. , The hoop will fall toward the center. As a result, the filler is further compressed, and the adhesion between the hoop and the filler or the gasket density is significantly increased.

Therefore, the sealing between the flange sealing surfaces can be satisfactorily performed with a low tightening surface pressure. Moreover, since the spiral gasket is sandwiched between the flange seal surfaces having a conical surface shape or a hemispherical surface shape with the gasket end surface having a shape corresponding to the seal surface, vibration acts on the flange. Even in such a case, relative movement between the gasket and the sealing surface is unlikely to occur, and there is almost no risk of the filler wearing. Further, even if the parallelism between both flange seal surfaces is impaired by vibration, the gasket is likely to be deformed in the axial direction as described above, or the parallelism between the seal surfaces is easily changed. Then, the contact with the sealing surface is appropriately maintained, and there is no fear that the sealing performance will deteriorate.

[0009]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS The structure of the present invention will be specifically described below with reference to the embodiments shown in FIGS.

The flange joint structure of this embodiment is provided in a general piping line, and as shown in FIG. 1, annular flanges 6 and 7 welded to the ends of the pipes 4 and 5 are spirally wound between them. It is fastened with a plurality of bolts 8 with the gasket 1 interposed.

The flanges 6 and 7 are formed in a conical shape and are parallel to each other.
a and 7a are formed. That is, an annular protrusion 6'is provided on one of the flanges 6, and the end face of the protrusion 6'is formed as a sealing surface 6a which is a concave conical surface.
The other flange 7 is provided with an annular groove 7'to which the projection 6'can be fitted. The bottom surface of the groove is the sealing surface 6a.
It is formed on the sealing surface 7a forming a convex conical surface parallel to . Therefore, with the spiral gasket 1 loaded in the annular groove 7'and the protrusion 6'fitted in the groove 7 ',
By tightening the bolts 8 between the flanges 4 and 5, the spiral gasket 1 can be pinched by the parallel flange sealing surfaces 6a and 7a.

The spiral gasket 1 is, as shown in FIG.
The flat hoop-shaped metal hoop 2 and the tape-shaped filler 3 are combined.
Both are slidable and superposed in a spiral shape, and by applying an external force in the axial direction, both
It is configured so that a slip occurs between the three and the telescope can be deformed in the axial direction.

The hoop 2 is made of a thin metal plate material such as stainless steel. The hoop 2 is longer than the filler 3, and includes a winding start portion 2a and a winding end portion 2b.
As shown in FIG. 2, it is wound a plurality of times and spot-welded at a plurality of places. In addition, the hoop end portions 2a and 2b
The number of windings is mainly that the rigidity of the gasket 1 in the axial direction is sufficiently obtained in relation to the tightening surface pressure, and the filler 3 is compressed when it is deformed in a telescopic shape in the axial direction as described later. It is appropriately set on condition that the diameter can be reduced and deformed as much as possible.

The filler 3 is composed of one or a plurality of sheet materials selected from inorganic paper, expanded graphite sheets in which expanded graphite particles are aggregated, and porous tetrafluoroethylene resin sheet made porous by stretching. There is. In particular, as the above-mentioned inorganic paper, 36.5% by weight or more of fibrous substance (ceramic fiber 5 to 20% by weight, sepiolite (about 0.2 μm)
Α type having a fiber diameter of 13.5 to 2) is preferable.
5% by weight, organic fiber hemp such as pulp 1 to 10% by weight),
59 wt% or less (more preferably 45.5 to 59 wt%) talc mineral, inorganic powder such as calcium carbonate, clay, barium sulfate, etc., and 1 to 10 wt% natural rubber latex, synthetic rubber latex, resin emulsion Those composed of a binder such as

The constituent materials and thicknesses of the hoop 2 and the filler 3 are appropriately selected according to the conditions such as the gasket diameter and the properties of the sealed fluid.

The width a of the filler 3 is set so that the hoop 2 is not exposed on the seal surface contact surfaces 1a and 1b, which are the gasket end surfaces, even when the filler 3 is deformed into a telescope shape according to the flange seal surface shape. It is set to be slightly wider than the width b of 2 (see FIG. 2). If the amount of protrusion (fluff amount) of the filler 3 from the hoop 2 is too small, the hoop 2 may come into contact with the flange sealing surface, and the hoop contact portion may form a leak path. If the amount of protrusion is too large, the fluffing portion of the filler 3 may fall off due to the sealed fluid pressure, high-temperature vibration, or the like, and in any case a good sealing function cannot be expected. It is necessary to determine the dimensions of both a and b in consideration of such a point, and generally, in the range of 1 <a / b ≦ 1.5, it is determined according to sealing conditions such as the shape of the flange sealing surface. Preferably.

In the flange joint structure constructed as described above, the spiral type gasket 1 manufactured flat.
Is inserted between the seal surfaces 6a and 7a and the flanges 6 and 7 are tightened, the tightening force causes the gasket 1 to slide and deform in the axial direction in a telescopic manner, so that the seal surface contact surfaces 1a and 1b are The shape is changed to a conical surface corresponding to the sealing surfaces 6a and 7a, and finally, as shown in FIG. 2, the sealing surfaces 6a and 7a are entirely brought into contact with each other. That is, one sealing surface contact surface 1a is concave
Full contact with the conical flange sealing surface 6a
It is transformed into a convex conical surface shape, and the other sealing surface is contacted.
The contact surface 1b is entirely on the flange seal surface 7a which forms a convex conical surface.
It will be deformed into a concave conical surface shape that makes surface contact.
Therefore, the deformability and familiarity of the seal surface contact surfaces 1a and 1b to the seal surfaces 6a and 7a are extremely high. Moreover, when the gasket 1 is deformed in the axial direction, the hoop 2 is contracted and deformed to compress the filler 3 in the radial direction, so that no gap is generated between the hoop 2 and the filler 3. , The gasket density is improved.

Therefore, the space between the flanges 6 and 7 can be satisfactorily sealed by the spiral gasket 1 with a low tightening pressure. Further, the flange sealing surface 6 having a conical surface shape
Since the spiral gasket 1 is loaded between a and 7a in a state of being deformable in the axial direction, even if the parallelism of the flange sealing surfaces 6a and 7a changes in the case where vibration occurs in the flange, Further, the spiral gasket 1 is deformed following the deformation, and it is possible to avoid the deterioration of the sealing performance. In addition, the gasket 1 and the flange sealing surfaces 6a and 7a
Since and form a conical surface and are in contact with each other, relative movement between them is unlikely to occur, and there is almost no fear that the filler 3 will wear due to vibration, and durability is significantly improved.

As described above, the spiral gasket 1 can be used in the flat form at the time of manufacture,
If necessary, the sealing surface contact surfaces 1a, 1b are preformed artificially or by an appropriate pressure molding machine into an inclined intersecting surface shape (for example, the shape shown in FIG. 2) corresponding to the flange sealing surfaces 6a, 7a. Therefore, it may be used. The conditions for winding the hoop 2 and the filler 3 (winding tightening degree, etc.) are appropriately set according to the shape of the sealing surface, the presence or absence of preforming, etc., but further improvement of the sealing property is expected depending on the conditions. It

According to experiments conducted by the present inventor, it was confirmed that the flange joint structure according to the present invention exhibits good sealing performance at a low tightening surface pressure as compared with the conventional joint structure. It was In this experiment, no particular difference was observed in compression characteristics and sealability depending on the presence / absence of preforming.
It has been found that the easiness of accommodating a and 7a and the sealing characteristics at the time of low tightening can be further improved.

That is, in Experimental Example 1, 4 with respect to the axis.
A spiral gasket was sandwiched between parallel conical surfaces forming an angle of 5 °, and 0.3 Kgf / cm ² was applied to the inner peripheral area of the gasket.
Was supplied to measure the amount of leakage into the outer peripheral region of the gasket 1. As a spiral gasket, the width is 6 mm
Of SUS304 made of flat strip plate, and a flat band-shaped filler of 8 mm width made of ceramic mixed sheet (inorganic fiber containing sepiolite and inorganic paper containing talc as a main component), an inner diameter of 43.8 mm, an outer diameter of 54 A flat spiral shape having a diameter of 0.2 mm and a radial thickness of 8 mm was superposed and integrated.

In Experimental Example 2, a spiral gasket having the same structure as that of the spiral gasket used in Experimental Example 1 except that an expanded graphite sheet was used as a filler (inner diameter 4
A flat shape having a diameter of 3.8 mm, an outer diameter of 54.1 mm and a radial thickness of 8 mm) was used to measure the amount of leakage under the same conditions as in Experimental Example 1.

In Experimental Example 3, the spiral gasket used in Experimental Example 1 was preformed (molded with a molding pressure of 250 Kgf / cm ² ) so that both end surfaces thereof had a conical surface of 45 °. Example 1 using a gasket
The leakage amount was measured under the same conditions as above.

Further, as a comparative example, the same experiment was conducted for the conventional joint structure. That is, in this experiment,
A conventional gasket was sandwiched between parallel planes, and 0.3 kgf / cm ² of nitrogen gas was supplied to the inner peripheral area of the gasket to measure the amount of leakage of the gasket 1 to the outer peripheral area.
The gasket used is a traditional spiral gasket (inner diameter 43.5 mm,
The outer diameter is 57 mm, and the radial thickness is 4.85 mm).

The results of these experiments are as shown in FIG. 4, and in the flange joint structure according to the present invention, regardless of whether the spiral gasket is preformed or not, it has a lower tightening than the conventional joint structure. It was confirmed that a very good sealing property was exhibited by the contact pressure. It was also confirmed that pre-molding of the spiral wound gasket can further improve the ease of fitting to the sealing surface and the sealing characteristics at the time of low tightening. In FIG. 4, ◯ indicates the experimental result, Δ indicates the experimental example 2, ● indicates the experimental example 3, and ■ indicates the measured result in the comparative example. Further, the tightening load in FIG. 4 is the axial load applied to the spiral gasket to clamp it.

The present invention is not limited to the above-mentioned embodiments, but can be appropriately improved or modified within the range not departing from the basic principle of the present invention. In particular, the flange sealing surfaces 6a and 7a may have any inclined crossing surface shape that intersects the flange axis obliquely, and may have a hemispherical surface shape or the like in addition to the conical surface shape described above. For example, as shown in FIG. 3, the flange sealing surface 6a,
7a may be formed in a hemispherical shape, and the flat spiral gasket 1 or the spiral gasket 1 preformed so that both end surfaces become hemispherical surfaces may be pressure-loaded into both sealing surfaces 6a, 7a. In such a flange joint structure, of course, the above-described operational effects can be obtained, and further, by tightening between the flanges 6 and 7, the spiral gasket 1 slides on the hemispherical surface, so that the flanges 6 and 7 can be connected. The effect that the misalignment is corrected is also exhibited.

[0027]

As can be easily understood from the above description, according to the flange joint structure of the present invention, a good sealing function can be exhibited with a low tightening surface pressure. Moreover,
Even when applied to equipment and places that are affected by vibration, the sealing performance does not deteriorate, and durability can be improved and applications can be greatly expanded.

[Brief description of drawings]

FIG. 1 is a vertical sectional side view showing an embodiment of a flange joint structure according to the present invention.

FIG. 2 is a detailed view showing an enlarged main part of FIG.

FIG. 3 is a vertical sectional side view of a flange joint structure showing a modified example.

FIG. 4 is a graph showing experimental results.

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 1 ... Spiral type gasket, 1a, 1b ... Sealing surface contact surface (gasket end surface), 2 ... Hoop, 3 ... Filler, 6,
7 ... Flange, 6a, 7a ... Flange sealing surface, 8 ... Bolt.

Claims (1)

[Claims] 1. A flange joint structure in which opposing flanges are fastened together by a plurality of bolts in a state where a spiral gasket is sandwiched between the opposing flange sealing surfaces, and both flange sealing surfaces have flange axis lines. inclined conical surface which intersects the like, to parallel surfaces der such an inclined cross-sectional shape of the semi-spherical surface such as is, spiral gasket, axial and flat band plate-shaped metal hoop and the tape-like filler with respect to Relative to
A flange joint structure, characterized in that it is formed by superimposing in a spiral shape capable of sliding deformation.