JP5560141B2 - Sealed body for fittings - Google Patents

Description

  The present invention relates to a seal body used for a pipe joint applied in an exhaust pipe or the like of an automobile, that is, a seal body for a pipe joint.

  As examples of a pipe joint seal body and pipe joints using the same, those disclosed in Patent Document 1 and Patent Document 2 are known. That is, for a pipe joint that is interposed between flange surfaces of a pair of fluid transfer pipes arranged opposite to each other, and is formed in an annular shape so as to form a pipe joint portion that seals and joins both the fluid transfer pipes. This is a seal body, and a pipe joint portion (pipe joint structure) is configured by the seal body and the pair of fluid transfer pipes.

  In Patent Document 1, a seal ring is provided between the flange member (34) of the upstream exhaust pipe (32) and the flange part (42) [concave spherical surface part (41)] of the downstream exhaust pipe (44). A structure in which a certain spherical belt-like sealing body (1) is interposed is shown. The band-shaped sealing body (1) is formed by compressing and mixing a heat-resistant material containing expanded graphite and a reinforcing material made of a wire mesh. And in patent document 2, it is a seal ring between the flange (19) of an upstream exhaust pipe (15), and the flange (21) [spherical seat (25)] of a downstream exhaust pipe (7). A structure with a spherical gasket (23) interposed is shown.

  In other words, the structure in which one flange and the seal ring are always pressed and urged by a spring while making spherical contact with each other allows the fluid transfer pipes arranged opposite to each other to be bent and displaced to some extent. Therefore, it is a favorable configuration for an exhaust pipe of an automobile in which vibration, thermal expansion and contraction are repeated, and good sealing performance can be maintained.

  As described above, the conventional pipe joint structure and its seal structure are relatively resistant to vibration. However, depending on the unfavorable conditions such as strong vibration and frequency, abnormal noise may be generated from the pipe joint structure. was there. Therefore, as described in Patent Document 1 described above, by forming the sealing body using a composite material instead of a simple material, the vibration is attenuated to avoid the generation of abnormal noise. Means are known.

  However, even in a pipe joint structure using a sealing body made of a composite material, the above-described abnormal noise generation may be slightly reduced, but the level is not sufficiently improved. Therefore, there is still room for improvement in order to eliminate abnormal noise.

JP 2003-097713 A JP 2008-303828 A

  It is an object of the present invention to be formed in an annular shape so as to form a pipe joint portion interposed between flange surfaces of a pair of fluid transfer pipes arranged opposite to each other and sealingly joining the two fluid transfer pipes. By further improving the seal for pipe joints, it is possible to avoid the generation of abnormal noise in the pipe joint structure.

The invention according to claim 1 is interposed between the flange surfaces 5a and 9a of a pair of fluid transfer pipes 1 and 2 arranged opposite to each other, and seals and joins both the fluid transfer pipes 1 and 2 together. In a pipe joint seal body that is formed in an annular shape to form a pipe joint portion T,
A sliding surface 10 that makes spherical contact with one of the flange surfaces 5a and an axial center of the other flange surface 9a and the sliding surface 11 so that the pair of fluid transfer tubes 1 and 2 can be angularly displaced. A side end face 11 that abuts in the Z direction, and a recess B capable of holding the lubricant j is formed in the side end face 11.
The concave portion B is constituted by a plurality of independent concave portions 20 that are not opened on either the inner diameter side or the outer diameter side of the side end surface 11 and are intermittently distributed in the circumferential direction. It is.

Invention is the use pipe joint sealing member according to claim 1, wherein with independent depressions 20 are arranged equally angular each with respect to the axis Z, each of the independent depressions 20 the axis Z according to claim 2 It is characterized by a circular shape when viewed from the direction.

The invention according to claim 3 is interposed between the flange surfaces 5a and 9a of a pair of fluid transfer pipes 1 and 2 arranged opposite to each other, and seals and joins both the fluid transfer pipes 1 and 2 together. In a pipe joint seal body that is formed in an annular shape to form a pipe joint portion T,
A sliding surface 10 that makes spherical contact with one of the flange surfaces 5a and an axial center of the other flange surface 9a and the sliding surface 11 so that the pair of fluid transfer tubes 1 and 2 can be angularly displaced. A side end face 11 that abuts in the Z direction, and a recess B capable of holding the lubricant j is formed in the side end face 11.
The recess B is formed by a single or a plurality of grooves m penetrating the side end surface 11 in and out of the diameter.

According to the first to third aspects of the present invention, details will be described in the section of the embodiment, but it is understood that abnormal noise is generated from the contact portion between the side end surface and the corresponding flange surface. A concave portion capable of holding the material was formed on the side end face. By interposing the lubricant between the side end face and the flange face, sliding friction is reduced, noise is eliminated or suppressed, and the lubricant held in the recess can be continuously supplied. The sound canceling or suppressing effect is exhibited over a long period of time. As a result, a pipe joint that is interposed between the flange surfaces of a pair of fluid transfer pipes that are arranged to face each other and is formed in an annular shape so as to form a pipe joint portion that seals and joins both the fluid transfer pipes. Due to the further improvement of the sealing body for use, it is possible to avoid the generation of abnormal noise in the pipe joint structure.

The form of the recess, as in claim 1, takes the means for configuring by arranging a plurality of independent recess in the circumferential direction, as claimed in claim 2, take steps to deploy evenly angle each their separate depressions as circular Get . Further , as in claim 3 , the side end surface may be constituted by a single or a plurality of grooves penetrating inward and outward.

Sectional view showing the outer sliding type pipe joint The sealing body for pipe joints by Example 1 is shown, (a) is a side view, (b) is an enlarged view of the Z section of Fig.2 (a). The manufacturing method of the sealing body for pipe joints is shown, (a) is a composite tape preparation process, (b) is a winding process, (c) is a perspective view of a winding roll body. Referential Example 1 and Examples 2 and 3 of the recess are shown, (a) is an annular circumferential groove, (b) is a radial opening groove, (c) is an oblique opening groove. Characteristics table for abnormal noise generation by seal body Sectional view showing inner sliding type pipe joint FIG. 6 shows the pipe joint seal body of FIG. 6, (a) is a cross-sectional view, and (b) is a side view.

  Embodiments of a pipe joint seal body according to the present invention and a pipe joint portion using the pipe joint seal body will be described below with reference to the drawings. 4A, 4B, and 4C are diagrams corresponding to a Q portion surrounded by a broken line in FIG.

[Example 1]
A pipe joint seal body (hereinafter simply referred to as “seal body”) A according to Embodiment 1 is used for a pipe joint portion T in an automobile exhaust system, as shown in FIG. The pipe joint portion T is made of a steel pipe and is formed with a first flange 1F formed on a downstream first exhaust pipe (an example of a fluid transfer pipe) 1 and a steel pipe made of an upstream second exhaust pipe (fluid transfer pipe). An example of the pressure contact mechanism 3 that presses the second flange 2F formed in 2 and the first flange 1F and the second flange 2F in a state where the annular seal body A is interposed between the flanges 1F and 2F. The first exhaust pipe 1 and the second exhaust pipe 2 disposed opposite to the first exhaust pipe 1 are hermetically joined (sealed joint) so as to be capable of relative angular displacement (relative bending displacement).

  A first flange portion 1F made of a sheet metal material includes a base end tubular portion 4 that is fitted and fixed to the distal end portion of the first exhaust pipe 1 in an airtight manner by welding or the like, and a diameter-expanded curved portion 5 that follows the base end tubular portion 4. The flange portion 6 is formed by being bent outward from the diameter expansion curved portion 5. The 2nd exhaust pipe 2 consists of a straight pipe round pipe, and the 2nd flange 2F is adhering to the base end part. The second flange 2F made of a sheet metal material has a body portion 7 that is fitted and fixed in an airtight manner to the tip portion of the second exhaust pipe 2 by welding or the like, and a radially outer side from the body portion 7 toward the first exhaust pipe 1 side. It has a contact peripheral portion 9 that is curved so as to be convex, and a flange portion 8 that rises from the contact peripheral portion 9.

  The enlarged-diameter curved portion 5 is a spherical surface having a radius R centered on a first point X at which the inner peripheral surface (an example of a flange surface) 5a is disposed at a position where the inner peripheral surface 5a enters the second exhaust pipe 2 side of the pipe axis P. It is formed so as to be a (concave spherical surface), and is set so as to penetrate into the second exhaust pipe 2 side in the assembled state (the state shown in FIG. 1). The inner peripheral surface 5a is a part that functions as a contact surface with the seal body A (described later), and the outer peripheral surface (an example of a flange surface) 9a of the contact peripheral portion 9 is also a seal member A (described later). It is set at a location that functions as a contact surface. The tube axis P of the first exhaust pipe 1 and the tube axis Z of the second exhaust pipe 2 coincide with each other in the state shown in FIG. 1 in which both the exhaust pipes 1 and 2 are aligned (P = Z). Therefore, hereinafter, the tube axis P is basically used as a representative.

  As shown in FIG. 1, the seal body A is a ring-shaped member that has an outer peripheral shape that tapers toward the first exhaust pipe 1 and is fitted on the front end 2 a of the second exhaust pipe 2. A curved outer peripheral sliding surface 10 that contacts the inner peripheral surface 5a of the enlarged diameter curved portion 5, an annular side end surface 11 that contacts the outer peripheral surface 9a of the contact peripheral portion 9, and the distal end portion 2a. And an inner peripheral surface 12 to be externally fitted. That is, the sliding surface 11 that makes spherical contact with the inner peripheral surface 5a, which is one flange surface, and the outer peripheral surface 9a, which is the other flange surface, to enable angular displacement between the first and second exhaust pipes 1 and 2. And a side end surface 11 that abuts in the direction of the axis P of the sliding surface, and a recess B that allows the lubricant 17 to be held is formed in the side end surface 11.

  The sliding surface 10 is centered on a second point Y that is closer to the first exhaust pipe 1 at a distance a from the first point X and closer to the outer diameter of the pipe axis P at a distance b from the first point X. A cross-sectional shape in a direction along the tube axis P with a radius r is formed on a spherical surface as a rotating body formed by rotating around the tube axis P. In this case, r <R and the inner circumferential surface 5a and the sliding surface 10 are in line contact (circular line contact). The planar side end surface 11 and the curved outer peripheral surface 9a are also in line contact.

  As shown in FIG. 1, the press-contact mechanism 3 has a step having a flange 13a inserted through holes 1k and 2k formed in the first and second flanges 1F and 2F, an intermediate flange 13b, and a root large-diameter portion 13c. The auxiliary bolt 13, the nut 14, and the coil spring 15 fitted to the stepped bolt 13 are assembled as shown in the figure. The nut 14 may be welded to the first flange portion 1F. A pipe joint that allows relative angular displacement between the first exhaust pipe 1 and the second exhaust pipe 2 by constantly pressing and urging the first and second flanges 1F, 2F toward each other by the elastic force of the coil spring 15. Part T is formed and maintained.

  By pressing the stepped bolt 13 and the nut 14, the set length of the coil spring 15 can be changed to adjust and set the pressing biasing force of the first and second flanges 1F, 2F. The press contact mechanism 3 is provided at a plurality of locations, for example, a plurality of locations (2 to 4 locations, etc.) at equal angles on the circumference centered on the tube axes P and Z. The sliding surface 10 of the seal body A and the inner peripheral surface 5a of the first flange portion 1F are pressed and urged by the pressure contact mechanism 3, and the side end surface 11 of the seal body A and the outer peripheral surface 9a of the second flange 2F are Is pressed.

  That is, the sliding surface 10 that makes spherical contact with one flange surface 5a to enable angular displacement between the pair of fluid transfer pipes 1 and 2, and the other flange surface 9a in the axial center P direction of the sliding surface 10 And a side end face 11 that abuts on the side end face 11, and a recess B that can hold the lubricant j is a pipe joint portion T having a seal body A formed on the side end face 11. The sliding surface 10 of the sealing body A and the inner peripheral surface 5a of the enlarged diameter curved portion 5 can be angularly displaced while maintaining an airtight state in line contact with each other. And when the stress which changes relative angle between the 2nd exhaust pipes 1 and 2 arises, the stress can be absorbed by the above-mentioned relative angular displacement in the pipe joint part T. In this way, a structure in which the outer peripheral surface of the seal body A is the sliding surface 11 in the seal structure is defined as an “outer sliding type”.

  Next, the recess B of the seal body A will be described in detail. As shown in FIGS. 2 (a) and 2 (b), the recess B formed in the side end surface 11 has a large number (in plural) of independent recesses (dimples) 20 that do not open to either the inner diameter side or the outer diameter side of the side end surface. ) Is intermittently distributed in the circumferential direction. In the first embodiment, 24 independent dents 20 are arranged at equal angles with respect to the axis Z (every 15 degrees), and each independent dent 20 has a circular shape when viewed in the direction of the axis P. The cross-sectional shape of the independent recess 20 may be a curved shape such as a spherical surface, a rectangular shape having a certain depth, or the like. Each independent recess 20 is filled with a heat-resistant lubricant j. 2B is an enlarged view of a Q portion surrounded by a broken line in FIG.

  A method for manufacturing the seal body A will be described. First, as shown in FIG. 3A, a composite tape is formed by knit knitting around an expanded graphite tape (width 47 mm, thickness t = 0.38 mm) 16a with a stainless wire (an example of a stainless steel filament) 16b. 16 [see FIG. 3 (b)] is prepared, and a composite tape making process of cutting to a length of 670 mm, for example, is performed. Next, as shown in FIG. 3 (b), a separately prepared expanded graphite sheet (width 60 mm, length 310 mm, thickness t = 0.38 mm) 18 and composite tape 16 are overlapped and wound. The winding process which produces the winding roll body 19 shown to (c) is performed. And the sealing body A (refer FIG. 2) is created by throwing the winding roll body 19 into a metal mold | die (illustration omitted) and performing a formation process. By performing processing (projection forming processing, embossing, etc.) on the portion corresponding to the side end surface 11 in the mold, the recess B can be formed on the side end surface 11 of the seal body A in the molding process.

  When the seal body A is created, an application process for applying the lubricant j is performed. The application process is a process in which the heat-resistant lubricant j is applied to the sliding surface 10 and the side end surface 11 and dried, and the seal body A having (holding) the lubricant on the sliding surface 10 and the side end surface 11 is provided. Created. Note that it is sufficient to apply and fill the lubricant j only to the 24 independent recesses 20 on the side end face 11, but it may be applied to the entire side end face 11. The heat-resistant lubricant j is preferably made of a mixture of a fluororesin and boron nitride, but may be other than that. The method of making the lubricant j will be described next.

  A boron nitride suspension is prepared by dispersing 30% by weight of boron nitride having an average particle diameter of 7 μm and 70% by weight of ion-exchanged water with a ball mill. Next, the heat-resistant lubricant j is obtained by stirring and mixing while adding 70% by weight of the boron nitride suspension to 30% by weight of the tetrafluoroethylene resin dispersion having a solid content of 30% by weight. Produced. The weight ratio of the heat-resistant lubricant j after drying is set such that the weight ratio of boron nitride is 60 to 90% and the weight ratio of the fluororesin is 10 to 40%. In Example 1, boron nitride is 70% by weight and tetrafluoroethylene resin is 30% by weight. The reinforcing material is 15 to 80% by weight, the lubricant and the expanded graphite are 20 to 85% by weight, the density of the expanded graphite is 1.2 to 2.0 g / cm 3, and the lubricant applied to the side end face 11 is slid. The lubricant applied to the moving surface 10 is set to 30% by weight or less, and the depth of the lubricant is set to 0.1 to 1 mm.

[ Reference Example 1 ]
As shown in FIG. 4A, the sealing body A according to Reference Example 1 has two inner and outer annular grooves (m1, m2) in which the recesses B are concentric with each other and also with the side end face 11. The seal body A is the same as the seal body A according to the first embodiment except for the recess B. The side end face 11 is divided into an inner annular face 11a, an intermediate annular face 11b, and an outer annular face 11c by the inner annular groove m1 and the outer annular groove m2. Although not shown, the concave portion B formed of a single annular groove may be used.

[Example 2 ]
In the sealing body A according to the second embodiment, as shown in FIG. 4B, the recess B is constituted by a plurality of grooves m that open the side end face 11 in and out of the diameter. The grooves m in this case are radially formed around the axis Z (see FIG. 2) and are arranged on the side end face 11 at equal angles, and the radial grooves m include a lubricant. j is filled.

[Example 3 ]
Seal body A according to Example 3, as shown in FIG. 4 (c), the recess B is, is constituted by a plurality of oblique grooves m3 to open the side end face 11 in the radially inward out, a derived structure of Example 2 is there. The inner opening 21 and the outer opening 22 of the groove m3 are displaced from each other in the circumferential direction with respect to the axis Z (see FIG. 2), and are formed so as to cross the side end face 11 obliquely. The oblique groove m3 is filled with a lubricant j.

Next, performance evaluation related to abnormal noise at the contact portion between the outer peripheral surface 9a and the side end surface 11 will be described. By attaching the seal bodies A of Example 1 , Reference Example 1 and Comparative Example to the pipe joint portion T of the exhaust pipe, fixing the exhaust pipe upstream side and attaching the downstream side to the drive device and moving it up and down, the angle ± The rocking was performed 1 million times 3 times at a frequency of 12 Hz. At this time, a gas burner is used to heat the open pipe upstream of the exhaust pipe, and the temperature of the pipe joint T is maintained at 550 ° C. The test results are shown in FIG. In FIG. 5, Example 1 is the sealing body A of Example 1 shown in FIG. 2, and Reference Example 1 is the sealing body A of Reference Example 1 shown in FIG. The sealing body of the comparative example is the same as the sealing body A according to Example 1 except that the side end face 11 has no recess B and the side end face 11 is not coated with a lubricant.

  Between 1 million times of oscillation, the frequency was set to 4 Hz at a predetermined number of times, and the frictional sound was confirmed and the amount of leakage was measured. The magnitude of the frictional sound is represented by the maximum distance away from the pipe joint T where the frictional noise can be heard. The amount of leakage is measured with a flow meter installed between the pipe connecting the compressor and the exhaust pipe after the upstream and downstream parts of the exhaust pipe are closed with rubber stoppers and compressed air of 0.03 MPa is pressurized with a compressor. Expressed as a flow rate per minute.

[Discussion]
As a result of the abnormal noise generation test, the abnormal noise of the pipe joint portion T described above is not often caused by the friction between the flange surface 5a of the first exhaust pipe 1 and the sliding surface 10, and the second exhaust pipe 2 has a second noise. It has been found that the friction noise caused by rubbing between the two flange surfaces 9a and the side end surfaces 11 is the main cause. In other words, the pipe joint portion T vibrates due to the running vibration of the automobile and the flow of exhaust gas. As a result, the seal body A rotates and moves in the circumferential direction (circumferential direction), and the flange surface 9a and the side end surface thereof. 11, that is, abnormal noise (friction abnormal noise) is generated by friction.

When the seal body of the comparative example is used, abnormal noise is generated by 250,000 times of swinging, and the abnormal noise is large enough to be confirmed even 10 m away. On the other hand, in the case of using the sealing body of Example 1 and Reference Example 1 , the number of abnormal noise occurrences is 900,000 times and 950,000 times, respectively, which is the number of times sufficiently covering the durability as a seal, It can be seen that the audible range is 1 m and the size of the abnormal sound itself is very small. In addition, the leakage amount (leakage amount) as the pipe joint portion T was 0.3 L / min, which was not a problem.

  Based on this new knowledge, the present invention has adopted a configuration in which the concave portion B capable of holding the lubricant j is provided on the side end face 11, thereby eliminating abnormal noise in the pipe joint portion T. It is up to confirming that it is suppressed. That is, since the lubricant j is interposed between the flange surface 9a and the side end surface 11, vibrations of the first flange 1F and the seal body A are attenuated, and abnormal noise is eliminated or suppressed. Friction due to sliding of 9a and 11 and wear caused thereby can be reduced. In addition, since the lubricant is held in the recess B and the lubricant j can be continuously supplied to the contact portion between the flange 9a and the side end face 11, the above-described abnormal noise generation or suppression effect is prolonged. It comes to be exhibited over.

[Another structure of pipe joint portion T and seal body A of Example 4 ]
As shown in FIG. 6, the pipe joint portion T having a different structure has an “inner sliding type” structure in which the inner peripheral surface of the seal body A is a sliding surface in the seal structure. A portion different from the “outside sliding type” pipe joint portion T shown in FIG. In addition, the same code | symbol shall be attached | subjected to the location functionally the same as the pipe joint part T shown in FIG. 1, and the description shall be made.

  The first flange portion 1F includes a base end cylinder portion 4 that is fitted and fixed to the front end portion of the first exhaust pipe 1 in an airtight manner by welding or the like, a diameter expansion portion 9 that follows the base end cylinder portion 4, and a diameter expansion portion 9 And a flange portion 6 formed by bending outward from the outer diameter. The second exhaust pipe 2 includes a tip tube portion 2b having an enlarged diameter and a tapered tube portion 2c that connects the tip tube portion 2b and the tube main body portion 2a. The second flange 2F includes a tip tube portion. 2b, a barrel portion 7 that is hermetically fitted and fixed by welding or the like, a flange portion 8 that is formed by bending outward from the barrel portion 7, and a diameter that is curved from the barrel portion 7 to the distal end side. However, it is formed to have a tapered portion 5 that is extended.

  The enlarged diameter portion 9 includes a cylindrical tube portion 9B parallel to the axis P of the first exhaust pipe 1 and a vertical tube portion 9A orthogonal to the axis P, and the seal body A is fitted in the cylindrical tube portion 9A. The outer peripheral surface 12 and the side end surface 11 inscribed in the longitudinal tube portion 9B are fitted and accommodated in the enlarged diameter curved portion 5. The inner surface 9a of the vertical tube portion 9A that contacts the side end surface 11 corresponds to the “other flange surface 9a”. An outer peripheral surface 5a (an example of one flange surface 5a) of the tapered portion 5 is formed on a convex spherical outer peripheral surface having a radius r and having a center X on the tube axis Z of the second exhaust pipe 2. A sliding surface 11 having a concave spherical inner peripheral surface that abuts on the convex spherical outer peripheral surface 5a so as to be capable of relative angular displacement is formed on the seal body A. That is, the inner peripheral surface of the seal body A is formed on the sliding surface 11, and the outer peripheral surface 9a of the second flange 2F is formed on a convex spherical outer peripheral surface that abuts the sliding surface 11 so as to be capable of relative angular displacement. ing.

That is, as shown in FIGS. 7A and 7B, the seal body A of Example 4 is a surface in the axial Z direction on the outer peripheral surface 12 fitted into the tubular tube portion 9A and the vertical tube portion 9B. It is comprised by the cyclic | annular seal ring which has the side end surface 11 which contact | abuts, and the sliding surface 10 which carries out spherical contact | abutting to the flange surface 9a. The side end face 11 is formed with, for example, a recess B formed by an independent recess 20 or the like. Although not shown, the recess B is filled with a lubricant j.

[Another Example]
The shape of the recess B formed in the side end face 11 is small dents and notches formed in large numbers in the radial direction and circumferential direction, dents opened only on the inner diameter side, dents opened only on the outer diameter side, and various other Things are possible.

DESCRIPTION OF SYMBOLS 1 Fluid transfer pipe 2 Fluid transfer pipe 5a Flange surface 9a Flange surface 10 Sliding surface 11 Side end surface 20 Independent dent A Pipe joint sealing body B Recess Z Z-axis center T Pipe joint j Lubricant m Groove m1, m2 Annular groove

Claims (3)

A pipe joint sealing body that is interposed between flange surfaces of a pair of fluid transfer pipes arranged opposite to each other, and is formed in an annular shape so as to form a pipe joint portion that seals and joins both the fluid transfer pipes. Because
A sliding surface that makes spherical contact with one of the flange surfaces to enable angular displacement between the pair of fluid transfer pipes, and a side end surface that makes contact with the other flange surface in the axial direction of the sliding surface; And a recess capable of holding the lubricant is formed on the side end face,
The concave portion, the inner diameter side and the outer one to the plurality of circumferentially intermittently distributed Deployed pipe joint seal member that is configured by independent depressions not opened even in diameter in the end surface. The seal body for a pipe joint according to claim 1 , wherein the independent recesses are arranged at equal angles with respect to the shaft center, and each of the independent recesses has a circular shape when viewed in the axial direction. A pipe joint sealing body that is interposed between flange surfaces of a pair of fluid transfer pipes arranged opposite to each other, and is formed in an annular shape so as to form a pipe joint portion that seals and joins both the fluid transfer pipes. Because
A sliding surface that makes spherical contact with one of the flange surfaces to enable angular displacement between the pair of fluid transfer pipes, and a side end surface that makes contact with the other flange surface in the axial direction of the sliding surface; And a recess capable of holding the lubricant is formed on the side end face,
The recess, the side end surface of the radially inward out to open one or more pipe joint sealing member that is configured by a groove.

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