JP3517719B2 - Pipe fittings - Google Patents

Description

Detailed Description of the Invention

[0001]

TECHNICAL FIELD The present invention relates to a pipe joint.

[0002]

2. Description of the Related Art A pair of tubular joint members, each of which has an annular seal projection on its abutting end faces, an annular gasket interposed between the abutting end faces of both joint members, and both joint members are connected to each other. As a pipe joint provided with a nut, Japanese Patent Publication No. 2-62756 discloses a pipe joint in which a seal projection presses a radial center portion of a gasket.

In the above-mentioned pipe joint, there is a problem that a recess for forming a liquid pool is formed between the inner edge of the abutting end surface of the joint member and the inner edge of the end surface of the gasket.

Therefore, the applicant of the present invention, as shown in FIG. 25, has the inner diameters of both joint members (41) and (42), both seal projections (43) and (44), and the gasket (45) which are equal to each other. Seal protrusion
(43) (44) filed a pipe joint in which the entire circumference of the inner edge of the gasket (45) is abutted (Japanese Patent Application Laid-Open No. Hei 4-
438183).

[0005]

The pipe joint of the above-mentioned application has no recesses for liquid pools and is suitable for applications requiring extremely high cleanliness such as semiconductor manufacturing. Has the following problems. That is, FIG.
Fig. 5 is an extremely exaggerated drawing of the condition when this pipe joint is tightened to the limit of the proper range. As shown in the figure, when tightening the nut in this pipe joint,
The inner edges of both ends of the gasket (45) should be
There is a problem that wrinkles (S) are generated in the inner peripheral portion (45a) of the gasket even if the tightening is performed properly, and wrinkles (S) accumulate in the wrinkles (S).

An object of the present invention is to provide a pipe joint which does not have a recess which becomes a liquid pool when tightening is completed and which does not cause wrinkles on the inner peripheral portion of the gasket.

Another object of the present invention is to provide a pipe joint in which it is easy to detect the completion of tightening due to a change in the feeling of tightening.

[0008]

A pipe joint according to the present invention comprises a pair of tubular joint members, an annular gasket interposed between the abutting end faces of both joint members, and screw means for connecting both joint members. The seal projections are provided on the butt end surface of each joint member or both end surfaces of the gasket, and when tightening is completed, a recess corresponding to the seal projection is formed on the surface without the seal projection, and the projection of each joint member is formed. In a pipe joint in which the inner edge portion of the mating end surface and the inner edge portion of each end surface of the gasket are in close contact with each other, each seal projection is located radially outward of the inner edge of the end surface where the seal projection is provided. near is, I place
The end of each seal protrusion is
When touching the non-existing surface, the butt end surface of each joint member
Between the outer edge of each end face of the gasket,
From the gap between the mating end face and the inner edge of each end face of the gasket
Is large and there is a gap that disappears when tightening is completed.
There is characterized in Rukoto.

Each of the seal projections is composed of an arcuate cross section extending radially outward from the end surface on which the seal projection is provided, and a straight cross section extending axially from the end surface and continuing to the tip of the arcuate cross section. May be.

An over-tightening prevention projection is provided on the outer edge of the abutting end surface of each joint member, and the abutting end surface of each joint member and the outer edge portion of each end surface of the gasket come into close contact with each other between the protrusions. There may be a resistance to tightening.

Each seal projection is provided on the abutting end surface of each joint member, and recesses corresponding to the seal projection may be provided on both end surfaces of the gasket. Also,
Each seal protrusion is provided on both end faces of the gasket, and a recess corresponding to the seal protrusion may be provided on the abutting end face of each joint member.

[0012]

BEST MODE FOR CARRYING OUT THE INVENTION Embodiments of the present invention will be described below with reference to the drawings. In addition, in the following description, the left and right of FIG.

As shown in FIGS. 1 and 2, the pipe joint is
A first tubular joint member (1) and a second tubular joint member (2),
The right end surface of the first tubular joint member (1) and the second tubular joint member (2)
An annular gasket (3) to be interposed between the left end face of the
And a retainer (5) which holds the annular gasket (3) and is held by the first tubular joint member (1).
By the nut (4) screwed from the joint member (2) side to the first joint member (1), the second joint member (2) becomes the first joint member.
It is fixed to (1). Annular seal projections (7) and (8) are respectively formed at the substantially central portions in the radial direction of the abutting end surfaces of the joint members (1) and (2). (9) and (10) are formed respectively.

Both end surfaces of the gasket (3) are flat surfaces perpendicular to the axial direction. On the outer peripheral surface of the gasket (3), there is a retaining part (3b) consisting of an outward flange, which allows the gasket (3) to be retained by the retainer (5) and the retainer (5) to be attached to each joint member (1). ) It is easy to do the work of holding it in (2).

Both joint members (1) (2) and gasket (3)
Is made of SUS316L. The inner diameters of the joint members (1) and (2) and the inner diameter of the gasket (3) are equal. The materials for both joint members (1) (2) and gasket (3) are:
Stainless steel other than SUS316L and other metals are appropriately adopted.

The retainer (5) is integrally formed of stainless steel plate, and has an annular portion (25) and three claws (28) provided on the right end of the annular portion (25) so as to project inward. Equipped with gasket
The gasket holding part (26) for holding the outer peripheral surface of (3), and the first
The tubular joint member (1) comprises a joint member holding portion (29) adapted to engage with the right end face of the tubular joint member (1). The three claws (28) are slightly elastic, and the tips of the claws (28) are each provided with a slightly elastic bent portion (28a) bent rightward. Then, the gasket (3) is fitted inside each claw (28), the bent portion (28a) is brought into close contact with the gasket (3), and the gasket (3) is retained in the retainer (5) in the radial and axial directions. Movement to is blocked. The annular portion (25) is provided with a pair of axial notches at the positions where the three claws (28) are provided, and the three claw-shaped holding portions (30) formed by the notches. The joint member holding portion (29) is constituted by. Three claw-shaped retainers (30)
Elastically pulls the outer surface of the right end of the first joint member (1) so that the retainer (5) is attached to the first tubular joint member.
It holds in (1). The nail (28) and the nail-shaped holding portion (30) are
The number is not limited to three and may be four.

At the right end of the nut (4) is an inward flange (1
1) is formed, and a portion of this flange (11) is fitted around the second joint member (2). A female thread (12) is formed on the inner circumference of the left end of the nut (4), and this is the first
It is screwed onto a male screw (14) formed on the right side of the joint member (1). An outward flange (13) is formed on the outer periphery of the left end of the second joint member (2), and a thrust ball bearing for preventing co-rotation between this and the inward flange (11) of the nut (4). (6) is interposed.

3 and 4 show in detail the essential parts of the first embodiment of the pipe joint according to the present invention.
(7) (8) has an arc-shaped cross section, and inner flat surfaces (15) (1) are provided on both inner and outer sides of the seal protrusions (7) (8) at each butt end surface.
6) and outer flat surfaces (17) (18) are formed. The inner flat surfaces (15) and (16) are projected to the left and right gasket (3) side from the outer flat surfaces (17) and (18).

The over-tightening prevention annular projections (9) and (10) are projected toward the gasket (3) in the left-right direction from the seal projections (7) and (8), and should be tightened further than proper tightening. In doing so, the retainer (5) is pressed from both sides. Each over-tightening prevention annular protrusion (9) (10) protects the sealing protrusion (7) (8) of each joint member (1) (2) before assembly, which has a significant effect on the sealing performance. It is prevented that the seal projections (7) and (8) exerting damage are damaged.

FIG. 3 is an enlarged view showing a state in which the nut (4) is tightened by hand. As shown in FIG. 3, when the nut (4) is tightened, the seal protrusion (7) The most protruding end of (8) first comes into contact with the end surface of the gasket (3), but at this time, the inner flat surface (15) (16) of each joint member (1) (2) and the left and right end surfaces of the gasket (3) are contacted. There are internal gaps (G1) between
Exists, and the outer flat surface (17) (1) of each joint member (1) (2)
There is a larger outer gap (G2) between 8) and the left and right end faces of the gasket (3). Further, there is a larger gap (G3) between the over-tightening prevention annular projections (9) (10) and the retainer (5). That is,
G1 <G2 <G3. If you tighten the nut (4) with a spanner, etc., after tightening it by hand,
The gasket (3) is deformed and the inner clearance (G1) becomes 0 first. At this time, the outer gap (G2) is not zero. Then, at the time of proper tightening, as shown in FIG. 4, the outer gap (G2) also becomes 0, and the inner flat surfaces (15) and (16) come into close contact with the inner edge portions of the left and right end surfaces of the gasket (3), Inner circumference (1) of each joint member (1) (2)
a) (2a) and the inner circumference (3a) of the gasket (3) are substantially flush with each other. That is, there is no recess that becomes a liquid pool. The gap (G3) between the over-tightening prevention annular projections (9) (10) and the retainer (5) is not zero even at this time. If tightened further than this, the clearance (G3) between the over-tightening prevention annular projections (9) (10) and the retainer (5) becomes 0, and the resistance against tightening becomes extremely large, and over-tightening is prevented. To be prevented.

In the first embodiment, the gasket (3)
And regarding the dimensions of each seal protrusion (7) (8), when the tightening torque is set to an appropriate value, the gap (G1) (G2) between the gasket (3) and each seal protrusion (7) (8) is It is decided to disappear. As an example, the protrusion height of each seal protrusion (7) (8) is 0.1 mm from the inner flat surface (15) (16), and the radius of the arc is 0.
5 mm, and the outer flat surfaces (17) (18) have inner flat surfaces (1
5) It is recessed by 0.02 mm from (16). In addition, the distance between the over-tightening prevention annular projections (9) and (10) and the retainer (5) when tightened by hand is set to 0.17 mm. Then, when rotated by 56.7 ° with the state of being tightened by hand as a reference, the inner flat surfaces (15) and (16) contact the gasket,
When tightened at 68 °, the outer flat surfaces (17) and (18) come into contact with each other. And finally when you tighten it exactly 90 degrees,
The space between both joint members (1) and (2) is reduced by 0.317 mm based on the condition of being tightened by hand, and the inner flat surfaces (15) and (16) are set to 0.
The outer flat surfaces (17) and (18) are 0.04 mm and the outer flat surfaces (17) and (18) bite into the gasket (3) respectively. When tightened further by 5.7 °, the over-tightening prevention projections (9) and (10) come into contact with the retainer (5) to prevent over-tightening.

The arcuate surface of each seal projection (7) (8) may partially include a straight line portion, and the cross-sectional shape of each arcuate surface near the most protruding end may be a straight line instead of a circular arc. Good. Figure 5
6 and FIGS. 10 to 13 show examples in which the shape of the protrusion is variously changed. In the following description, for the joint members (1) and (2) that differ only in the protrusions, only the symbols of the protrusions will be changed, and the same symbols will be applied to common members other than the joint members (1) and (2). Therefore, the description thereof will be omitted.

In the second embodiment shown in FIGS. 5 and 6, the seal projections (37) (38) of the joint members (1) (2) are the same as the seal projections of the first embodiment shown in FIGS. 3 and 4. (7) By removing a part of the outer peripheral portion of (8), the outer peripheral surface of the base end portion of the seal projections (37) (38) extends in the axial direction. The cross-sectional contour shape of each seal protrusion (37) (38) is the same as that of each joint member (1).
A circular arc part extending radially outward from the butt end face of (2)
(37b) and (38b) extend in the axial direction from the same end face and arc (37
b) It is composed of straight line parts (37a) and (38a) connected to the tip of (38b).
The arcuate portions (37b) and (38b) are arcs centered on a point radially inward of the straight line portions (37a) and (38a).

As for the size, the protrusion height of each seal protrusion (37) (38) is 0.1 m from the inner flat surface (15) (16) of each joint member (1) (2).
m, the radius of the arc is 0.5 mm, and the outer flat surface (17)
(18) is recessed by 0.02 mm from the inner flat surfaces (15) and (16). Also, the distance between each over-tightening annular projection (9) (10) and the retainer (5) when tightened by hand is 0.17 mm.
It is said that. The inner flat surfaces (15) and (16) come into contact with the gasket (3) when rotated by 56.7 ° with respect to the state of being tightened by hand, and the outer flat surface (17) when tightened at 68 °. (18) contacts the gasket (3). When finally tightened exactly 90 °, the space between both joint members (1) and (2) is 0.317 with reference to the condition of tightening by hand.
mm narrower, inner flat surface (15) (16) 0.06mm, outer flat surface (17) (18) 0.04mm
It will cut into (3). When tightened further by 5.7 °, the over-tightening prevention projections (9) and (10) come into contact with the retainer (5) to prevent over-tightening.

In FIGS. 7 and 8, the rotation angle of the nut (4) is plotted on the ordinate and the tightening torque is plotted on the abscissa for the first and second embodiments, and the relationship between the two is investigated. It is a thing. FIG. 7 is for the first embodiment, and it can be seen that the tightening torque increases almost linearly as the nut (4) is tightened. FIG. 8 is for the second embodiment, and it can be seen that the inclination changes when the rotation angle of the nut (4) is about 70 °.
That is, in the second embodiment, the radial length of the seal projections (37) (38) is smaller than that in the first embodiment, so that the outer flat surfaces (17) (18) are Until the contact with (3), the increase in the tightening torque with respect to the rotation angle of the nut (4) is small, and therefore the graph is sloping, while the outer flat surfaces (17) (18) are Since the size of the contact area between each joint member (1) (2) and the gasket (3) after contacting with (3) is larger than that of the first embodiment, the rotation angle of the nut (4) is The tightening torque increases greatly, and therefore the slope of the graph becomes nearly horizontal.
Therefore, it is clearly understood that the inclination is changed when the rotation angle of the nut (4) is about 70 °.

FIG. 9 shows the relationship between the third embodiment and the rotation angle of the nut (4) on the ordinate and the tightening torque on the abscissa. Although the pipe joint of the third embodiment is not shown in the drawings, in the second embodiment, the annular protrusions (9) (10) and the retainer (5) for preventing each overtightening when tightened by hand.
The distance between and was 0.17 mm, whereas this distance was 0.15 mm. Therefore,
The distance between the overtightening prevention projections (9) and (10) and the retainer (5) when the outer flat surfaces (17) and (18) abut the gasket (3) is calculated to be 0.03 mm. Then, when the nut is rotated about 85 ° with the state of being tightened by hand as a reference,
The over-tightening protrusions (9) (10) and the retainer (5) are in contact with each other, which makes the graph more horizontal. Therefore, the tightening torque is very great when the nut (4) is rotated by about 85 °, so that the person who is performing the tightening work can detect the end of tightening.

FIG. 10 shows a fourth embodiment in which the seal projections (47) and (48) have a rectangular cross section.
The relationship between the rotation angle of the nut (4) and the tightening torque in the pipe joint having the seal projections (47) and (48) is almost the same as that in FIG. 8 or 9, but the seal projection (47) ( Since the contact area between the tip and the base end of (48) does not change, the torque change until the base end of the seal protrusion (47) (48) contacts the end face of the gasket (3) becomes constant. The change in the slope of becomes clearer.

FIG. 11 shows a fifth embodiment, in which the cross-sectional shape of each seal projection (57) (58) is an isosceles triangle. FIG. 12 shows the sixth embodiment, and the cross-sectional shape of each of the seal projections (67) (68) is a right triangle whose outer peripheral surface extends in the axial direction. FIG. 13 shows the seventh embodiment, and the cross-sectional shape of each of the seal projections (77) and (78) is a right triangle whose inner peripheral surface extends in the axial direction. Seal protrusions (57) (58) (67) (68) (77) from the fifth embodiment to the seventh embodiment
The relationship between the rotation angle of the nut (4) and the tightening torque in the pipe joint having (78) is close to that in FIG. 8 or 9, but these seal protrusions (57) (58) (67) ( Since the tips of 68, 77, and 78 are sharp, each seal protrusion 57, 58, 67, 68, 7
7) (78) is characterized in that the increasing rate of the tightening torque while it is in contact with the corresponding end surface of the gasket (3) is smaller than that of the second embodiment. It is easy to feel the change in response in the latter half, and it is easier to sense when tightening has finished. The pipe joints having the seal projections (57) (58) (67) (68) (77) (78) of the fifth embodiment to the seventh embodiment have the arc-shape shown in the first and second embodiments. Protrusion
It is slightly inferior to those of (7), (8), (37), and (38) in that it is more likely to be painful, and the shape of the seal projection is appropriately selected according to the required performance of the pipe joint. The seal projections (37) (38) shown in the second embodiment not only have the advantage that it is possible to clearly see that the inclination has changed at the completion of tightening, but also Since the tip is arcuate, the seal projection can be worked and hardened, and as a result, it has sufficient durability.

In the above-described first to seventh embodiments, both end faces of the gasket are both flat, and each seal protrusion is provided on the joint member. However, by providing seal protrusions on both end faces of the gasket, The abutting end faces of the members may be flat. Such an example is shown in FIGS. 14 to 17.

FIG. 14 shows an eighth embodiment, in which the seal projections (87) (88) have a rectangular cross-section, and the seal projections (87) (88) and the base end are Since the contact area does not change with the end, the torque change until the base end of the seal protrusion (87) (88) contacts the end face of the gasket (3) becomes constant, and the change in inclination after that becomes clearer. It has the feature of becoming. FIG. 15 shows the ninth embodiment,
The cross-sectional shape of the seal protrusions (97) (98) is an isosceles triangle. FIG. 16 shows the tenth embodiment, in which the seal projections (107), (108) have a cross-sectional shape of a right triangle whose outer peripheral surface extends in the axial direction. FIG. 17 shows the eleventh embodiment, and the cross-sectional shape of the seal projections (117), (118) is a right-angled triangle whose inner peripheral surface extends in the axial direction. These triangular seal protrusions (97) (98) (107) (108) (117) (118)
Then, since its tip is sharp, each seal protrusion (97) (9
8) (107) (108) (117) (118) is characterized in that the increasing rate of tightening torque during contact with the corresponding end surface of the gasket (3) is smaller than that of the second embodiment. Therefore, it has a feature that it is easy to feel a change in response in the latter half of the tightening, and it is easier to sense the completion of the tightening.

In the eighth to eleventh embodiments, the abutting end faces of the joint members (1) and (2) are flush with the inner flat faces (15) and (16) and the outer flat faces (17) and (18). Made and gasket
The inner flat surface (19) (20) of (3) is replaced by the outer flat surface (21) (22)
Is protruded toward the left and right joint members (1) and (2). Therefore, when the nut (4) is tightened by hand, the inner flat surface (15) (16) of each joint member (1) (2) and the inner flat surface (19) (20) of the gasket (3) are There are inner gaps (G1) between them, and the outer flat surfaces (17) (18) of each joint member (1) (2) and the outer flat surfaces (21) (22) of the gasket (3) are present. There is a larger outer gap (G2) between each of them and a larger gap between the overtightening prevention ring projections (9) (10) and the retainer (5). (G3) exists, that is, G1 <G2 <G3. All of these gaps (G1) (G2) (G3) become 0 when the tightening is completed.

FIGS. 18 to 21 show an example in which a joint member having a seal projection is used and recesses corresponding to the seal projection are provided on both end faces of the gasket.

FIG. 18 shows a twelfth embodiment in which the sectional shape of the seal projections (127) (128) of the joint members (1) (2) is
Similar to the second embodiment, the gasket (3) has
Recesses (129) (130) having substantially the same shape as the seal protrusions (127) (128) and slightly smaller than this are provided. FIG. 19 shows a thirteenth embodiment, in which each joint member (1) (2)
The cross-sectional shape of the seal protrusions (137) (138) of the is isosceles triangle, and the gasket (3) has this seal protrusion (1
Recesses (139) (140) having substantially the same shape as those of 37 (138) and slightly smaller than this are provided. FIG. 20 shows a fourteenth embodiment in which the cross-sectional shape of the seal projections (147) and (148) is a right triangle whose outer peripheral surface extends in the axial direction, and the gasket (3) has the seal projections. (147) Recessed portion (149) having a shape similar to that of (148) and slightly smaller than this
(150) is provided. FIG. 21 shows a fifteenth embodiment in which the seal projections (157) and (158) have a cross-sectional shape of a right-angled triangle whose inner peripheral surface extends in the axial direction, and the gasket (3) has this seal. Recesses (159) (160) having substantially the same shape as the protrusions (157) (158) and slightly smaller than this are provided.

In the twelfth to fifteenth embodiments, the recess of the gasket is provided on the flat end surface, and the inner flat surfaces (15) and (16) of the joint members are the outer flat surfaces (1
7) It is projected to the left and right gasket (3) side from (18). Therefore, when the nut (4) is tightened by hand, the inner clearance between the inner flat surfaces (15) and (16) of each joint member (1) and (2) and the left and right end surfaces of the gasket (3), respectively. (G1) is present and the outer flat surface (17) (18) of each joint member (1) (2)
There is a larger outer gap (G2) between the gasket and the left and right end faces of the gasket (3), and the over-tightening annular projections (9) (10) and the retainer (5) In between
There is a larger gap (G3), that is, G1
<G2 <G3. These gaps (G1) (G2) (G3)
Becomes 0 when tightening is completed.

In the twelfth to fifteenth embodiments, the same effects as those of the first to second embodiments can be obtained, and the seal projections (127) (128) (137) ( 138) (1
47) (148) (157) (158) and recesses (129) (130) in gasket (3)
The contact area with (139) (140) (149) (150) (159) (160) is the contact area between the seal protrusions (7) (8) (37) (38) and the end face of the flat gasket (3). Larger than area, seal protrusions (127) (128) (137)
(138) (147) (148) (157) (158) has the advantage of being less painful, and moreover, the sealing protrusions (127) (128) (137) (138) (147)
(148) (157) (158) are concave (129) (130) (139) (140) (149) (15
It also has the advantage that the gasket (3) is positioned when it is fitted into the (0), (159) and (160). The first of these
In the second to fifteenth embodiments, the gasket (3)
If the required level of positioning accuracy is low, the retainer
It is also possible to omit (5).

Although not shown, according to the same concept as in the first to second embodiments, seal protrusions are provided on both end faces of the gasket, and recesses corresponding to the seal protrusions are provided on the abutting end faces of the joint member. May be provided.

FIG. 22 shows a sixteenth embodiment, in which the joint members (201) and (202) are one of the conventional joint members, and the cross section is substantially at the center of the butted end faces. Ring-shaped seal protrusions (207) (208) with a trapezoidal shape and an arcuate tip
Is provided. The inner flat surfaces (215) (216) and the outer flat surfaces (217) (218) formed inside and outside the annular seal protrusions (207) (208) are in the same plane. In this conventional joint member (201) (202), the seal protrusions (207) (208) are larger than the seal protrusions (7) (8) of the joint members (1) (2) shown in the first embodiment. , Gaskets with flat end faces as shown in FIG.
When combined with (3), the gasket will be
Between the inner edge of (3) and the inner edge of the joint member (201) (202),
There was a problem that a gap was created. The gasket (203) shown in FIG. 22 has a shape suitable for the conventional joint members (201) (202) having large sealing protrusions (207) (208). ), The recesses (209) (210) having a trapezoidal cross section are provided. Gasket (203)
Each end face has inner flats (219) (220) and outer flats (221) (222) inside and outside the recesses (209) (210), but the inner part of the gasket (203) is outside. The inner flat surfaces (219) (220) are thicker than the portions, and the inner flat surfaces (219) (220) project more than the outer flat surfaces (221) (222). Therefore, while tightening the nut (4) with the hand shown in FIG. 23, each joint member (201)
Between the inner flat surfaces (215) and (216) of (202) and the inner flat surfaces (219) and (220) of the gasket (203), there are inner clearances (G1).
Is present, and the outer flat surface (2) of each joint member (201) (202) is
Larger outer gaps (G2) are present between the outer surfaces (221) (222) of the gaskets (3) and the gaskets (218), respectively. When the nut (4) is tightened with a tool such as a spanner, the seal protrusions (207) (208) and the gasket
(203) is deformed and the inner gap (G1) becomes zero. At this time,
The outer gap (G2) is not zero. Then, when the tightening is completed, the outer gap (G2) also becomes zero. Incidentally, each joint member (201)
When the outer flat surfaces (217) and (218) of (202) abut the outer flat surfaces (221) and (222) of the gasket (203), the tightening torque inclination is close to horizontal as in the above embodiments. So
It is easy to check if proper tightening is done. Therefore, even in the case of pipe fittings that use conventional fitting members (201) and (202), by exchanging the gasket with the above gasket (203), it is possible to detect the excellent sealing property and the completion of tightening. It can be easy.

FIG. 24 shows a seventeenth embodiment, in which the joint members (231) and (232) are other ones of the conventional joint members, and a gasket is fitted at a substantially central portion of the abutting end faces thereof. Annular recesses (239) (240) for insertion are provided. Such joint members (231) (232) are usually used in combination with a gasket having a circular cross section, and the cross sectional shape of the gasket is considerably larger than that of the recesses (239) (240). Upon completion, gasket inner edge and fittings (231) (232)
There was a problem that a gap was created between the inner edge of the and. The gasket (233) shown in FIG. 24 has a shape suitable for such joint members (231) (232),
Sealing protrusions (237) (238) having an arc-shaped cross section are provided on both end faces of the gasket (233) corresponding to the annular recesses (239) (240) of the joint members (231) (232). . On both ends of the gasket (233), the inner flats (249) (250) and the outer flats (251) are located inside and outside the seal lugs (237) (238), respectively.
(252), but the inner part of the gasket (233) is thicker than the outer part, and the inner flat surface (249) (250) is the outer flat surface (251).
It is designed to project more than (252). Therefore, with the nut (4) tightened by hand as shown in FIG. 24, the inner flat surfaces (245) (246) of the joint members (231) (232) and the inner flat surface (249) of the gasket (223) are tightened. Between (250), there is an inner gap (G1), respectively, each joint member (231)
Larger outer gaps (G2) exist between the outer flat surfaces (247) and (248) of (232) and the outer flat surfaces (251) and (252) of the gasket (233). When the nut (4) is further tightened with a spanner or the like, the gasket (233) is deformed and the inner clearance (G1) becomes zero. At this time, the outer gap (G
2) is not zero. Then, when tightening is completed, the outer clearance
(G2) also becomes 0, and the inner flat surface of each joint member (231) (232)
(245) (246) is the inner flat surface of the gasket (233) (249) (250)
Close to the inner circumference of each joint member (231) (232) (231a) (232a)
And the inner circumference (233a) of the gasket (233) are substantially flush with each other.
That is, there is no recess that becomes a liquid pool. In addition,
When the outer flat surfaces (247) (248) of the joint members (231) (232) are in close contact with the outer flat surfaces (251) (252) of the gasket (233), the tightening torque is the same as in the above embodiments. Since the inclination is close to horizontal, it is easy to check if proper tightening has been achieved. Therefore, even in the case of a pipe joint using the conventional joint members (231) (232) having the annular recesses (239) (240), by exchanging the gasket with the gasket (233), excellent sealing property can be obtained. Moreover, it is possible to make it easy to detect the completion of the tightening.

[0039]

According to the pipe joint of the present invention, as the screw is tightened, the seal projection first comes into close contact with the surface without the seal projection, and then the inner edge portion of the abutting end surface of each joint member. The inner edges of the end faces of the gasket are in close contact with each other to ensure the sealing performance, and there is no recess that serves as a liquid pool. The gasket is most deformed at the position where the seal projection is provided, but this position is not the inner edge of the end surface where the seal projection is provided as in the conventional case, but is the outer side of the inner edge, so the gasket Since the most deformed portion of the gasket is displaced outward from the inner edge portion, and therefore wrinkles do not occur on the inner peripheral portion of the gasket, there is no fear of dust accumulation. Therefore, it can also be used for piping that requires high cleanliness.

Further, when the tip of each seal projection comes into contact with the surface without the seal projection when the screw is tightened, each of the seal projections is provided between the butt end surface of each joint member and the outer edge portion of each end surface of the gasket. since the gap no longer at the time of large and tightening completion than the gap between the butt end face and the inner edge of the end faces of the gasket of the joint member is formed, went tightening the screws, the inner edge of the abutting end face of each joint member When the section and the inner edge of each end face of the gasket were in close contact, a gap was formed between the butt end face of each joint member and the outer edge of each end face of the gasket, and the screws were tightened further. At this time, the abutting end faces of the joint members and the outer edge portions of the end faces of the gasket come into close contact with each other. Therefore, the abutting end surface of each joint member and the end surface of the gasket come into contact with each other with a larger pressure at the inner edge portion than at the outer edge portion, which is advantageous for the sealing property. When the abutting end surface of each joint member and the outer edge of each end surface of the gasket are in close contact with each other, the tightening torque increases, and along with this, the feeling of tightening changes and it is sensed that the tightening is complete. It is possible to prevent over tightening.

The cross-sectional contour shape of each seal projection is composed of an arc portion extending radially outward from the end surface on which the seal projection is provided, and a straight portion extending axially from the end surface and continuing to the tip of the arc portion. In this case, since the protruding surface of the seal projection has a linear outer peripheral surface extending in the axial direction, the screw should be tightened immediately before the abutting end surface of each joint member and the outer edge of each end surface of the gasket come into close contact with each other. However, the contact area between each joint member and the gasket does not increase. Therefore,
During this period, there is no change in the tightening response, and the tightening response changes when the butted end faces of each joint member and the outer edge of each end face of the gasket come into close contact. Can be perceived. Further, since the arc portion can be work-hardened, it has excellent durability.

An overtightening prevention projection is provided on the outer edge of the abutting end surface of each joint member, and the abutting end surface of each joint member and the outer edge portion of each end surface of the gasket are in close contact with each other between the both projections. If the butt end face of each joint member and the outer edge of each end face of the gasket are in close contact with each other, the change in response becomes even greater, so that the tightening is completed. It is easier to sense that.

Each seal projection is provided on the butt end surface of each joint member, and recesses corresponding to the seal projection may be provided on both end surfaces of the gasket. Also,
Each seal protrusion is provided on both end faces of the gasket, and in the case where the joint end face of each joint member is provided with a recess corresponding to the seal protrusion, the tip of the seal protrusion is the face without the seal protrusion. The contact area becomes large when touching, and the durability of the protrusion is improved.

[Brief description of drawings]

FIG. 1 is a vertical sectional view showing a first embodiment of a pipe joint according to the present invention.

FIG. 2 is an exploded perspective view of a main part of FIG.

FIG. 3 is an enlarged cross-sectional view of an essential part of FIG. 1, showing a state where a nut is tightened by hand.

FIG. 4 is a diagram showing a state where the state of FIG. 3 is further tightened and the fastening is completed.

FIG. 5 shows a second embodiment of the pipe joint according to the present invention, and is an enlarged cross-sectional view of a main part in a state where a nut is tightened by hand.

FIG. 6 is a diagram showing a state where the state of FIG. 5 is further tightened and the fastening is completed.

FIG. 7 is a graph showing the relationship between the nut rotation angle and the tightening torque when the pipe joint of the first embodiment is tightened.

FIG. 8 is a graph showing a relationship between a nut rotation angle and a tightening torque when the pipe joint of the second embodiment is tightened.

FIG. 9 is a graph showing the relationship between the nut rotation angle and the tightening torque when the pipe joint of the third embodiment is tightened.

FIG. 10 shows a fourth embodiment of the pipe joint according to the present invention, and is an enlarged cross-sectional view of an essential part in a state where a nut is tightened by hand.

FIG. 11 shows a pipe joint according to a fifth embodiment of the present invention, and is an enlarged cross-sectional view of an essential part in a state where a nut is tightened by hand.

FIG. 12 shows a sixth embodiment of the pipe joint according to the present invention, and is an enlarged cross-sectional view of an essential part in a state where a nut is tightened by hand.

FIG. 13 shows a seventh embodiment of the pipe joint according to the present invention, and is an enlarged cross-sectional view of an essential part of a state where a nut is tightened by hand.

FIG. 14 shows an eighth embodiment of the pipe joint according to the present invention, and is an enlarged cross-sectional view of an essential part of a state where a nut is tightened by hand.

FIG. 15 shows a ninth embodiment of the pipe joint according to the present invention, and is an enlarged sectional view of an essential part of a state where a nut is tightened by hand.

FIG. 16 shows a tenth embodiment of the pipe joint according to the present invention, and is an enlarged cross-sectional view of an essential part of a state where the nut is tightened by hand.

FIG. 17 shows an eleventh embodiment of the pipe joint according to the present invention, and is an enlarged cross-sectional view of an essential part of a state where a nut is tightened by hand.

FIG. 18 shows a twelfth embodiment of the pipe joint according to the present invention, and is an enlarged sectional view of an essential part showing a state when the nut is tightened by hand and a state where the joint member and the gasket are separated from each other. .

FIG. 19 shows a thirteenth embodiment of the pipe joint according to the present invention, and is an enlarged sectional view of an essential part showing a state when the nut is tightened by hand and a state where the joint member and the gasket are separated from each other. .

FIG. 20 shows a fourteenth embodiment of the pipe joint according to the present invention, and is an enlarged sectional view of an essential part showing a state when the nut is tightened by hand and a state where the joint member and the gasket are separated from each other. .

FIG. 21 shows a fifteenth embodiment of the pipe joint according to the present invention, and is an enlarged sectional view of an essential part showing a state when the nut is tightened by hand and a state where the joint member and the gasket are separated from each other. .

FIG. 22 is a vertical sectional view showing a sixteenth embodiment of the pipe joint according to the present invention.

FIG. 23 is an enlarged cross-sectional view of a main part of FIG. 22, showing a state when the nut is tightened by hand.

FIG. 24 is an enlarged sectional view of an essential part showing a seventeenth embodiment of the pipe joint according to the present invention, showing a state when the nut is tightened by hand.

FIG. 25 is a view showing a state at the time of completion of tightening of a conventional pipe joint.

[Explanation of symbols]

(1) (2) Tubular fitting member (3) Annular gasket (4) Nut (7) (8) Seal protrusion (9) (10) Overtightening prevention protrusion (37) (38) Seal protrusion (37a) (38a) ) Seal protrusion straight part (37b) (38b) Seal protrusion arc part (47) (48) (57) (58) (67) (68) (77) Seal protrusion (78) (87) (88) (97) (98) (107) (108) (117) (118) Seal protrusion (127) (128) (137) (138) (147) (148) (157) (158) Seal protrusion (129) (130) ( 139) (140) (149) (150) (159) (160) Recess (201) (202) Tubular fitting member (203) Annular gasket (207) (208) Seal protrusion (231) (232) Tubular fitting member (233) Annular gasket (237) (238) Seal protrusion (239) (240) Recess

─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Shinichi Ikeda 2-3-2 Selling Moat, Nishi-ku, Osaka City Fujikin Co., Ltd. (72) Inventor Tsutomu Shinohara 2-3-2 Selling Moat, Nishi-ku, Osaka City Fujikin Co., Ltd. (72) Inventor, Kazuhiro Yoshikawa, 2-3-2, Selling moat, Nishi-ku, Osaka City, Fujikin Co., Ltd. (72) Inventor, Tetsuya Kojima, 2-3, Selling moat, Nishi-ku, Osaka City, Fujikin Co., Ltd. (56) References 2-501587 (JP, A) (58) Fields surveyed (Int.Cl. ⁷ , DB name) F16L 21/04

Claims (5)

(57) [Claims] 1. A pair of tubular joint members, and an annular gasket interposed between the abutting end faces of both joint members,
With a screw means for connecting both joint members, each joint member has a butt end face or both end faces of a gasket, and a seal protrusion is provided on each face, and when tightening is completed, a recess corresponding to the seal protrusion is provided on the face without the seal protrusion. And a pipe joint in which the inner edge of the abutting end face of each joint member and the inner edge of each end face of the gasket are in close contact with each other, each seal protrusion is Ri near was closer to the radial outward of the inner edge, the screw is tightened, the tips of the seal projection
When touching the surface without the seal protrusion,
Between the mating end face and the outer edge of each end face of the gasket,
Inner edge of butt end face of joint member and each end face of gasket
A gap that is larger than the gap between the
Features and to fittings that you have but formed. 2. The contour shape of the cross section of each seal projection is an arc portion extending radially outward from an end surface on which the seal projection is provided, and a straight portion extending axially from the end surface and continuing to the tip of the arc portion. The pipe joint according to claim 1 , wherein 3. The outer edge of the butt end surface of each joint member,
An overtightening prevention projection is provided, and when the abutting end surfaces of the joint members and the outer edge of each end surface of the gasket come into close contact with each other, a resistance force against tightening is generated between the two overtightening prevention projections. The pipe joint according to claim 1 or 2, characterized in that. Wherein each seal projection is provided on the abutting end face of each joint member, the end faces of the gasket, according to claim 1 or 2, characterized in that the recesses corresponding to the seal projection is provided Pipe fittings. Wherein each seal projection is provided on both end faces of the gasket, the abutting end face of each joint member, according to claim 1 or 2, characterized in that the recesses corresponding to the seal projection is provided Pipe fittings.