JPH08277976A - Joint device for piping - Google Patents

Abstract

PURPOSE: To prevent a pipe connecting part from coming off without requiring any increase in material strength or in thickness in a pipe member. CONSTITUTION: In a joint device in which a male side pipe member 10 and a female side pipe member 20 are fitted to each other so as to be connected together by clamping the fitting part between them from the outer circumference side by means of resin fastening members 30, 40, the female side pipe member 20 is brought into contact with the fastening members 30, 40 via two positions, in other words, via a pipe radius directional projection part 10a arranged in the female side pipe member 20 and a slanting face. In this way, concentration of contact loads to only one position in the female side pipe member 20 is prevented, so that deformation in the contact part in the female side pipe member 20 can be prevented excellently.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a pipe joint device suitable for connecting fluid pipes, for example, refrigerant pipes of a refrigeration cycle.

[0002]

2. Description of the Related Art Conventionally, as a pipe coupling device which can be easily attached and detached, for example, there is one disclosed in Japanese Patent Publication No. 60-59478, and in this conventional device, a flange portion formed at an end portion of a female side pipe has a circular cross section. It is structured to be locked by a circular spring.

[0003]

However, in the above-mentioned pipe joint device, since the male and female pipes are connected to each other by locking only one of the flange portions, the internal pressure of the pipe increases. If the tensile force acting on the connecting part of both male and female piping increases, the flange part will deform and the fatal defect that the connecting part of both male and female piping will come off (disengage) will occur. was there.

In order to prevent disconnection of the connecting portion between the male and female pipes, it is necessary to take measures such as changing the material of the fluid pipe to one having high strength or increasing the pipe wall thickness. Increases costs. The present invention has been made in view of the above points, and provides a pipe joint device capable of reliably preventing disconnection of a connecting portion without requiring an improvement in material strength of a fluid pipe or an increase in pipe wall thickness. With the goal.

[0005]

In order to achieve the above object, the present invention employs the following technical means. In the invention according to claim 1, in the pipe joint device for connecting two fluid pipes (P2, P2), the both pipes (P2, P2)
Female side pipe member (20) provided at one end of the one side, and male side provided at the other ends of the both pipes (P2, P2) and fitted to the female side pipe member (20) A tube member (10),
The female tube member (20) and the male tube member (10)
Fastening members (30, 40) arranged on the outer peripheral side of the fitting portion of
And the female side pipe member (20) and the male side pipe member (10) are connected by the fastening members (30, 40), and the female side pipe member (20) is ,
A pipe joint device provided with first and second contact portions (20a), (20c, 20d) that come into contact with the fastening member (30, 40) at two locations separated by a predetermined distance in the axial direction. Is characterized by.

According to a second aspect of the invention, in a pipe joint device for connecting two fluid pipes (P2, P2),
A female pipe member (20) provided at one end of the two pipes (P2, P2) and another female pipe member (20) provided at the other end of the two pipes (P2, P2). ), And a first side and a first side having a substantially arcuate inner surface shape corresponding to the outer shapes of the male side tube member (20) and the male side tube member (20). 2 fastening members (30,
40), and the first and second fastening members (30,
One end of 40) is rotatably connected by a hinge connection, and the first and second fastening members (30, 4) are connected.
The other end of 0) is configured to be detachably locked, and the first and second fastening members (30, 40).
The fitting portion of the female side pipe member (20) and the male side pipe member (10) is arranged on the inner peripheral side of the second end of the first and second fastening members (30, 40). By locking, the female tube member (20) and the male tube member (10)
Are connected to each other, and the female tube member (2
0), the first and second abutting portions (20a), (20c, 20c, 20a, 20a, 20a, 20a, 20a, 20a, 20a, 20a, 20a, 20a, 20b, 20a, 20b, 20c, 20c, 20c, 20c, 20c, which contact the first and second fastening members 30, 40 at two positions spaced apart by a predetermined distance in the axial direction. Two
0d) is provided.

According to a third aspect of the present invention, in the pipe joint apparatus according to the first or second aspect, the first abutting portion is outside the radial direction of the pipe at the tip of the female-side pipe member (20). The male side tube member (10) is composed of a projecting portion (20a) projecting in a flange shape toward one side, and faces the projecting portion (20a) at the tip of the female side tube member (20). A protrusion (10a) is formed on the first and second protrusions (10a, 20a) are arranged adjacent to each other and are configured to abut each other.

According to a fourth aspect of the present invention, in the pipe joint device according to any one of the first to third aspects, the second contact portion has an inclined surface (2) inclined in the pipe radial direction.
0c), and the inclined surface (20c) is configured to come into line contact with the fastening members (30, 40). According to a fifth aspect of the invention, in the pipe joint device according to any one of the first to third aspects, the second contact portion is formed as a contact surface (20d) parallel to the pipe radial direction. The fastening members (30, 40) are provided with contact surfaces (30d, 40d) parallel to the pipe radial direction so as to face the contact surfaces (20d) parallel to the pipe radial direction. The contact surfaces (20d) and (30d, 40d) are configured to contact each other.

According to a sixth aspect of the present invention, in the pipe joint apparatus according to any one of the first to fifth aspects, the fastening members (30, 40) are symmetrical in shape in the axial direction. It is characterized by being. According to a seventh aspect of the present invention, in the pipe joint device according to any one of the first to sixth aspects, the fastening member (30,
40) is molded from a resin having a high temperature creep strength.

The reference numerals in parentheses of the above-mentioned means indicate the correspondence with the concrete means described in the embodiments described later.

[0011]

According to the invention described in claims 1 to 7, since it has the above-mentioned technical means, the internal fluid pressure of both the male and female pipe members rises or is repeatedly pressurized. In this case, since both the first and second abutting portions provided on the female-side pipe member come into contact with the fastening member, the load exerted by the female-side pipe member on the fastening member is dispersed at two locations, and It is possible to suppress deformation of the abutting portion of the pipe member, and it is possible to reliably prevent occurrence of a fatal defect such as detachment (detachment) of the female side pipe member.

Therefore, unlike the conventional device, it is not necessary to improve the material strength of the fluid pipe or increase the pipe wall thickness, and the pipe joint device can be manufactured at a low cost. Particularly, in the invention according to claim 4, the second abutting portion is formed as an inclined surface inclined in the pipe radial direction, and the inclined surface is configured to come into contact with the fastening member in line contact. Therefore, even if the second contact portion is an inclined surface that is easy to process,
Since the load applied from the inclined surface to open the fastening member in the pipe radial direction can be sufficiently reduced, the deformation of the fastening member can be reduced.

According to the invention of claim 5, the second
The contact part of the pipe is parallel to the pipe radial direction, and the fastening member has a contact surface parallel to the pipe radial direction so as to face the contact surface parallel to the pipe radial direction. Since the two contact surfaces are formed in contact with each other, a load for opening the fastening member in the radial direction of the pipe is not generated, and the fastening member can be reliably prevented from being deformed by this load. .

Further, in the invention according to claim 6, since the fastening member is formed in a bilaterally symmetric shape in the axial direction thereof, the assembling directionality of the fastening member with respect to both the male and female pipe members is eliminated, The fastening member can be assembled to both pipe members from either the left or right direction, and the assembling workability can be improved. Further, in the invention according to claim 7, since the fastening member is formed of resin, the whole shape can be easily integrally formed, the fastening member can be manufactured at low cost, and the high-temperature creep strength resin is used. Since it is molded, even if the temperature of the internal fluid becomes high, the required strength of the fastening member can be maintained and the high temperature deformation of the fastening member can be prevented.

[0015]

Embodiments of the present invention will be described below with reference to the drawings. (First Embodiment) FIGS. 1 to 5 show a pipe / pipe joint apparatus according to the present invention, and FIG. 6 shows a refrigeration cycle apparatus for an automobile air conditioner adopting the pipe joint apparatus according to the present invention. Is shown.

First, the outline of the refrigeration cycle of the automobile air conditioner will be described. In FIG. 6, the compressed refrigerant discharged from the compressor 100 driven by the automobile engine is supplied to the condenser 110 through the high pressure pipes P1 and P1. Then cool and condense here. And the high pressure pipe P2
, P2, the condensed refrigerant is supplied into the receiver 120, and the liquid refrigerant separated in the receiver 120 is separated into high-pressure pipes P3, P3, the pipe joint 130, and the high-pressure pipe P4.
Is supplied to the temperature type automatic expansion valve 140 through which the refrigerant is decompressed and expanded to a gas-liquid two-phase state. The gas-liquid two-phase refrigerant is then supplied to the evaporator 150, where it is evaporated and the conditioned air is cooled by the latent heat of evaporation.

The evaporated gas refrigerant returns to the compressor 100 through the low pressure pipe P5, the pipe joint 130, and the low pressure pipes P6, P6. The pipe joint device according to the present embodiment is used as a joint for both high-pressure pipes P2, P2 on the downstream side of the condenser 110 of the refrigeration cycle. The concrete constitution of this pipe joint device will be described in detail below.

As shown in FIGS. 1 to 5, this piping joint device includes a male-side pipe member 10, a female-side pipe member 20, and two resin-made substantially semi-cylindrical fastening members 3 hinged to each other.
0 and 40. Both high pressure pipes P2
, P2 are made of metal such as aluminum, copper, iron, etc., and the male-side pipe member 10 and the female-side pipe member 20 are coaxially integrally formed at the ends of the high-pressure pipes P2, P2. The male side tube member 10 is airtightly fitted to the inner peripheral side of the female side tube member 20 via a rubber O-ring (elastic sealing material) 60.

Here, as shown in FIG. 4, the male side tube member 1
0, a bulge-shaped U-shaped projecting portion 10a in the radial direction, a tip enlarged diameter portion 10b formed further on the tip side of the bulging portion 10a, and a tip enlarged diameter portion 10b, 2 in the circumferential direction in which the O-ring 60 is fitted
One concave groove 10c is provided. On the other hand, the female tube member 2
0 is formed at the tip enlarged diameter portion 20b into which the tip enlarged diameter portion 10b of the male side tube member 10 is fitted and the end portion of the tip enlarged diameter portion 20b, and is projected in a flange shape (disc shape) in the radial direction. A protruding portion 20a is provided. This protrusion 20a
Is formed so as to face the protruding portion 10a, and its outer diameter is slightly larger than the outer diameter of the protruding portion 10a.

Further, the enlarged diameter portion 20b of the distal end of the female tube member 20
In the above, an inclined surface (conical surface) 20c is formed at a portion opposite to the protruding portion 20a. Further, both fastening members 30 and 40 are integrally formed by a resin having high high-temperature creep strength (for example, polybutylene terephthalate, polyphenylene sulfide, or those obtained by adding 40% of glass fiber) to each other. The fastening members 30 and 40 are molded into shapes having substantially arc-shaped inner surface shapes 30a and 40a corresponding to the outer shapes of the fitting portions of the male-side tube member 10 and the female-side tube member 20, respectively. The male side pipe member 10 is provided in the substantially arc-shaped inner surface shapes 30a and 40a.
And a circumferential recessed groove 30 into which the projecting portions 10a, 20a projecting in the radial direction of the female tube member 20 are fitted and abutted.
b and 40b are formed on both sides in the axial direction.

Of the concave grooves 30b and 40b,
Inclined surfaces (conical surfaces) 30c and 40c along the inclined surface 20c are formed at a portion of the distal end enlarged diameter portion 20b of the female side tube member 20 facing the inclined surface 20c. The inclined surface 20c and the inclined surface 30c are formed. , 40c can come into contact with each other. In the axial contact portion between the female tube member 20 and the fastening members 30 and 40, the contact portion between the protruding portion 20a and the side walls of the concave grooves 30b and 40b constitutes the first contact portion, and the inclined portion The contact portion between the surface 20c and the inclined surfaces 30c and 40c constitutes the second contact portion.

The reason why the above-mentioned circumferential grooves 30b, 40b and the inclined surfaces 30c, 40c are formed on both sides in the axial direction is that both fastening members 30, 40 are arranged in the axial direction as shown in FIG.
Even if the protrusions 10a and 20a are formed in a shape symmetrical with respect to the center line A and the positions of the protrusions 10a and 20a are reversed left and right in the axial direction as shown in FIG. 5, the first and second fastening members 30, 40
This is for allowing the male-side tube member 10 and the female-side tube member 20 to be arranged on the inner peripheral surface of. As a result, the first and second fastening members 30, 40 can eliminate the directionality of pipe connection.

On the other hand, hinge portions 31 and 41 are formed at one end of each of the fastening members 30 and 40 in the circumferential direction. The hinge portions 31 and 41 form a fitting structure of a shaft and a bearing portion, and are hinged so as to be rotatable with respect to each other. That is, the hinge shaft 31 provided at one end of the first fastening member 30 is integrally formed with the rotary shaft 31a. On the other hand, the hinge portion 41 provided at one end of the second fastening member 40 is integrally formed with a bearing portion 41a that rotatably holds the rotating shaft 31a.

Here, a protrusion 41a '(see FIG. 3) is formed at the entrance of the bearing 41a of the hinge 41 so that the size of the entrance is smaller than the outer diameter of the rotary shaft 31a. . The protrusion 41a 'can prevent the rotary shaft 31a from slipping out of the bearing 41a. Further, a portion forming a rectangular locking hole 32 is formed on the outer circumferential surface of the other end portion in the circumferential direction of one fastening member 30, and the outer circumferential surface of the other end portion in the circumferential direction of the other fastening member 40 is formed. Is formed in a rectangular parallelepiped shape so that the locking portion 42 faces the locking hole portion 32.

As shown in FIG. 3, the engaging hole portion 32 of the one fastening member 30 is open toward the engaging portion 42 side, and the radially outer inner wall of the engaging hole portion 32 is A claw 33 (see FIGS. 2 and 3) having a right-angled triangular cross section is formed to project. The inclined wall 33a of the claw 33 is formed so as to be higher toward the left side in the drawing. The locking portion 42 includes a metal plate spring-like locking piece 50 such as stainless steel (SUS304).
The base 51 is insert-molded when the fastening member 40 is integrally molded with resin.
Extends substantially along the circumferential direction so as to be inserted into the locking hole portion 32. In this case, the end surface 42 of the locking portion 42
The extension angle of the locking piece 50 from a is approximately 90 degrees.

Further, as shown in FIGS. 1 to 3, the front end portion 52 of the locking piece 50 is directed toward the upper side of the pawl 33 as shown in FIGS. 1 to 3 so as to easily ride on the inclined wall 33a of the pawl 33 in the locking hole portion 32. It is curved, and the claw 33 is provided at an intermediate portion of the locking piece 50.
An engaging hole portion 53 for engaging with is formed. In addition, the base portion 51 of the locking piece 50 is formed with a retaining hole portion 54 so as to prevent the retaining member 42 from coming off from the retaining portion 42 after insert molding into the fastening member 40.

In the pipe joint device constructed as described above, the fastening members 30 and 40 sandwich the male-side pipe member 10 and the female-side pipe member 20 coaxially fitted to each other from the radial direction. Then, in the process of sandwiching in this way, the locking piece 50 is inserted into the locking hole portion 32 while riding on the inclined wall 33a of the claw 33 at the tip portion 52 thereof. As a result, the claw 33 is locked in the locking hole portion 53,
The other ends of the fastening members 30, 40 are integrally locked to each other, and the male pipe member 10 and the female pipe member 20 arranged on the inner peripheral side of the fastening members 30, 40 are integrally connected.

Further, the first contact portion which is the contact portion between the protrusions 10a and 20a and the circumferential grooves 30b and 40b, and the contact portion between the inclined surface 20c and the inclined surfaces 30c and 40c. By the second contact portion, the first and second fastening members 30, 40 and the male-side tube member 10 and the female-side tube member 20 are reliably fixed in the axial direction. By the way, the refrigerant pressure (fluid pressure) inside both pipe members 10 and 20
Is raised or repeatedly pressed, the projecting portion 20a of the female tube member 20 comes into contact with the side walls of the recessed grooves 30b, 40b of the fastening members 30, 40 to start deformation, and at the same time, the female tube The inclined surface 20c of the member 20 is fastened to the fastening members 30, 4
Since the load applied to the fastening members 30 and 40 from the female-side pipe member 20 is abutted against the inclined surfaces 30c and 40c of 0, the deformation of the protrusion 20a of the female-side pipe member 20 is suppressed, and the female-side pipe member 20 is prevented from being deformed. It is possible to reliably prevent the occurrence of a fatal defect such as detachment (detachment) of the side pipe member 20. (Second to Fourth Embodiments) FIGS. 7 to 9 show second to fourth embodiments. In the first embodiment, the inclined surface 20c and the inclined surface 30
Since c and 40c are formed to have the same inclination angle for the tapered surfaces, when the internal pressure of both pipe members 10 and 20 further rises, the inclined surfaces 30 of the fastening members 30 and 40 are
The inclined surface 20c of the female tube member 20 acts as a wedge with respect to c and 40c, and a load is applied to open the fastening members 30 and 40 in the pipe radial direction, thereby deforming the fastening members 30 and 40, There is a fear of destruction.

Therefore, in the second embodiment of FIG. 7, the inclined surface 2
0c and the inclination angles of the inclined surfaces 30c and 40c are changed (see FIG.
In the example shown in FIG.
(larger than c)), the contact surfaces of both inclined surfaces are not contact surfaces but contact surfaces in the circumferential direction to reduce the load on the fastening members 30 and 40. As a result, the possibility of deformation of the fastening members 30, 40 can be greatly reduced.

In the third embodiment of FIG. 8, the fastening members 30, 4 are
No concave grooves 30b, 40b are provided with inclined surfaces 30c, 40c, and instead, contact surfaces 30 parallel to the pipe radial direction are provided.
By providing d and 40d and abutting the abutting surfaces 30d and 40d against the inclined surface 20c of the female-side tube member 20 with line contact, the same operational effect as the second embodiment of FIG. 7 is exhibited. It was done like this.

In the fourth embodiment shown in FIG. 9, when there is no problem in formability of the female side tubular member 20 made of metal such as aluminum, the inclined surface 20 of the female side tubular member 20 is also included.
c is eliminated and a contact surface 20d parallel to the pipe radial direction is formed so that the contact surface 20d abuts the contact surfaces 30d and 40d of the fastening members 30 and 40 parallel to the pipe radial direction. It was done.

As a result, the contact surface 20d and the contact surface 30 are
Only axial load acts between d and 40d,
Since a load for opening the fastening members 30, 40 in the radial direction of the pipe is not generated, the fastening members 30, 40 due to this load are not generated.
The deformation of can be completely eliminated. (Fifth Embodiment) FIG. 10B shows a fifth embodiment. FIG.
0 (a) is a view corresponding to the BB cross section of FIG. 1 in the above-described first embodiment, and as shown in FIG.
In the structure in which one end of the rotating shaft 31a is integrally formed so as to support both ends of the rotating shaft 31a, when a load is generated to open the fastening members 30 and 40 in the pipe radial direction, the load is applied to the rotating shaft 31a. Both ends of 31a act in the direction of pulling away from the hinge part 31 (support part), and as a result, shearing force acts on the rotating shaft 31a.

For example, when the rotating shaft 31a has a small cross-sectional area, the rotating shaft 31a may be broken by the shearing force. Therefore, in the fifth embodiment, as shown in FIG.
As shown in (b), 4 of the hinge portion 31 of the fastening member 30.
The rotary shaft 31a is integrally molded from the location, and the shearing force is distributed to the four locations.
It is intended to prevent breakage of a.

Further, as shown in FIG. 10A, the hinge portion 3
In the configuration in which one rotary shaft 31a is integrally molded so as to support both ends of the rotary shaft 31a, the hinge portions 31 on both ends of the shaft are molded at the time of resin molding.
Since the molten resin flows from this to form one rotary shaft 31a, a weld (a portion where the molded resin is incompletely joined) is likely to occur in the middle of the rotary shaft 31a. On the contrary, according to the fifth embodiment of FIG. 10 (b), when the resin is molded, the molten resin only flows from the hinge portion 31 toward the tip side of each of the rotating shafts 31a, and each rotating shaft 31a is molded. Therefore, there is also an advantage that a molding defect such as the weld does not occur. (Sixth Embodiment) FIG. 11 shows a sixth embodiment, except that the fastening members 30 and 40 are formed in asymmetrical shapes with respect to the center line A, only in the first embodiment. The other points are the same as those in the first embodiment. In this example, the fastening member 30,
40 is formed in a left-right asymmetric shape, and the concave grooves 30b, 40b are formed.
Since the inclined surfaces 30c and 40c are provided only on one side in the axial direction, the fastening members 30 and 40 can be assembled to the pipe members 10 and 20 only in the specific direction shown in FIG. (Seventh Embodiment) FIGS. 12 and 13 show a seventh embodiment. In the above-described first to sixth embodiments, the pair of semi-cylindrical fastening members 30 and 40 hinged to each other are integrally locked at their ends, so that the inner circumferential sides of both fastening members 30 and 40 are secured. Although the arranged male-side pipe member 10 and female-side pipe member 20 are integrally connected, it is unavoidable that the fastening portions of the fastening members 30 and 40 are loosened due to variations in manufacturing dimensions.

If there is looseness in the fastening portions of the fastening members 30 and 40, vibration may cause refrigerant leakage. Therefore, in order to prevent such refrigerant leakage, a double seal structure using two O-rings is adopted.
At low temperatures in winter, the compression set of the O-ring becomes large,
Even with the double seal, there is a possibility that the leakage of the refrigerant may occur due to the vibration.

The seventh embodiment proposes a concrete structure for effectively preventing such a refrigerant leak, and the male side pipe member 10 and the female side pipe member 20 caused by the looseness of the fastening portion. Focusing on the compressibility of the O-ring that fluctuates due to relative movement (in particular, inclination), among the O-rings having the double seal structure, the inner seal O-ring (the right O-ring in FIG. 12) 60
The arrangement position of b is set to a position where the O-ring compression rate is minimized, and the above problem is solved.

The seventh embodiment will be specifically described with reference to FIGS. 12 and 13. The double sealing structure using two O-rings is used for the fastening portions of both fastening members 30 and 40. Then, a double seal structure is formed by the inner seal O-ring 60b located inside the refrigerant leakage path of the fastening portion and the outer seal O-ring 60a located outside the refrigerant leakage path of the fastening portion.

Then, the male side tube member 10 and the female side tube member 20.
Backlash in the fitting portion with the both pipe members 10,
20 flange-shaped protrusions 10a, 20a and a groove 30b,
Due to the backlash with 40b, both pipe members 10 and 20 are inclined by an angle θ with the point O as the apex. Here, when the male tube member 10 is fixed, the female tube member 20 is in a free state, and vibration is applied, the female tube member 20 makes a motion with a cone having the point O as its apex as a locus. The internal seal O-ring 60b is located at the position O at the apex of this conical locus motion in the axial direction of the pipe joint.
Is set to

When the female tube member 20 moves along a conical locus with the point O as the apex, both O-rings 60a and 60b are moved.
The compression margin of changes as shown in the graph at the bottom of FIG. In this graph, lines a and b indicate the amount of change in compression allowance when the female tube member 20 is tilted in 180 ° different directions. As understood from the above graph, in this example, the compression margin of the outer seal O-ring 60a is 0.
Although it fluctuates by 17 mm, since the internal seal O-ring 60b is set at the position O which is the apex of the conical locus motion, the amount of change in the compression allowance becomes almost 0, which is the minimum.

FIG. 13 shows changes in the O-ring compression rate. Since the compression margin of the outer seal O-ring 60a varies within the above-mentioned 0.17 mm range, the compression rate varies within the range indicated by the solid line c. It may fall below the lower limit (10%) of the appropriate range. On the contrary, the compression rate of the internal seal O-ring 60b is maintained at a constant value of about 12% which is within the proper range.

As a result, even if the sealing action of the outer seal O-ring 60a may be reduced by vibration (conical locus motion), the inner seal O-ring 60b maintains a proper compression ratio to ensure a good seal. The action can be maintained. (Eighth Embodiment) FIG. 14 shows an eighth embodiment.
In the above-described first to seventh embodiments, a pair of semi-cylindrical fastening members 30 and 40 hinged to each other are integrally locked at their ends, so that both fastening members 3 are joined together.
Although the male side pipe member 10 and the female side pipe member 20 arranged on the inner peripheral side of 0 and 40 are integrally connected, there is looseness in the fastening portions of both fastening members 30 and 40 due to dimensional variations in manufacturing and the like. It is unavoidable that the position shifts.

If the looseness and positional deviation of the fastening portions of the two fastening members 30 and 40 are to be reduced during the assembling of the joint, it is necessary to correct the shape by hand and the workability of the assembling is considerably deteriorated. . Therefore, in this example, in FIG.
As shown in FIG.
0, 400, a predetermined length (0.5 ~
By adding the chamfered portions 301 and 401 having 2 mm), the workability at the time of assembling the joint is improved.

According to this example, both male and female tubular members 10, 2
When the end portions of the pair of fastening members 30 and 40 are integrally locked after fitting 0, the chamfered portions 301 and 401 are formed at the inner peripheral side corners of the mating surfaces 300 and 400. Even if the inner peripheral circular shapes of the fastening members 30 and 40 are slightly displaced, the chamfered portions 301 and 401 allow the two pipe members 1 to be formed.
It is possible to automatically correct the fitting positions of 0 and 20 and both fastening members 30 and 40 to a position where the gap between them is minimized.

Therefore, according to this example, the mating surfaces 300,
The chamfered portions 301 and 401 formed in 400 can facilitate the fastening work of both fastening members 30 and 40, and
The fitting gap between the two pipe members 10 and 20 and the fastening members 30 and 40 can be minimized. In the embodiment described above, the condenser 11 is used in the refrigeration cycle of FIG.
0, the pipe joint device for connecting the high-pressure pipes P2, P2 between the receiver 120 has been described, but the present invention has pipes P1, P3 other than the high-pressure pipes P2, P2.
Of course, it can be applied to the connecting portion of P4, P5, and P6.

The present invention is not limited to the connection of refrigerant pipes,
It is widely applicable to fluid piping for various purposes.

[Brief description of drawings]

FIG. 1 is a perspective view showing a first embodiment of the present invention with a fastening member opened.

2 is a side view of the piping joint device shown in FIG. 1. FIG.

FIG. 3 is a cross-sectional view showing a first embodiment of the present invention.

FIG. 4 is a cross-sectional view of essential parts showing a state when the pipes according to the first embodiment of the present invention are assembled.

FIG. 5 is a cross-sectional view of essential parts showing a state in which the pipe assembling direction is reversed from that of FIG. 4 in the first embodiment of the present invention.

FIG. 6 is an exploded perspective view of a refrigeration cycle device of an automobile air conditioner to which the present invention is applied.

FIG. 7 is a cross-sectional view of essential parts showing a second embodiment of the present invention.

FIG. 8 is a cross-sectional view of essential parts showing a third embodiment of the present invention.

FIG. 9 is a cross-sectional view of essential parts showing a fourth embodiment of the present invention.

FIG. 10 is a cross-sectional view of essential parts showing a fifth embodiment of the present invention.

FIG. 11 is a cross-sectional view of essential parts showing a sixth embodiment of the present invention.

FIG. 12 is a view showing a seventh embodiment of the present invention and is a view in which a sectional view of a main part and an O-ring compression margin explanatory view are combined.

FIG. 13 is an O-ring compression ratio explanatory diagram according to the seventh embodiment of the present invention.

FIG. 14 is a perspective view showing an eighth embodiment of the present invention with a fastening member opened.

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 10 ... Male side tube member, 10a ... Projection part, 20 ... Female side tube member, 20a ... Projection part, 20c ... Inclined surface, 20d ... Abutting surface, 30, 40 ... 1st, 2nd fastening member, 30c, 40
c ... inclined surface, 30d, 40d ... abutting surface, 31, 41 ... hinge part, 32 ... engaging hole part, 33 ... claw, 50 ... locking piece, 5
3 ... Engagement hole portion.

Claims (7)

[Claims] 1. A pipe joint device for connecting two fluid pipes, comprising: a female pipe member provided at one end of both pipes; and a female pipe member provided at the other end of both pipes. A male-side pipe member fitted to the female-side pipe member; and a fastening member arranged on an outer peripheral side of a fitting portion of the female-side pipe member and the male-side pipe member. The female tube member and the male tube member are connected to each other, and the female tube member has a first and a first abutting portion which are in contact with the fastening member at two positions separated by a predetermined distance in the axial direction. 2. A pipe joint device, comprising: two contact portions. 2. A pipe joint device for connecting two fluid pipes, the female pipe member being provided at one end of both pipes, and the female pipe member being provided at the other end of both pipes. A male side pipe member fitted to the female side pipe member, and first and second fastening members having substantially arcuate inner surface shapes corresponding to the outer shapes of the female side pipe member and the male side pipe member. One end of each of the first and second fastening members is rotatably connected by a hinge coupling, and the other end of each of the first and second fastening members is detachably locked. The first and second fastening members are provided with fitting portions of the female-side pipe member and the male-side pipe member on the inner peripheral side thereof, and
The female side pipe member and the male side pipe member are connected by locking the other end portion of the second fastening member, and the female side pipe member has a predetermined axial direction. A pipe joint device comprising: first and second abutting portions that abut the first and second fastening members at two locations spaced apart from each other. 3. The first abutting portion is composed of a projecting portion projecting outward in the pipe radial direction in a flange shape at the tip end portion of the female side pipe member, and the tip end portion of the female side pipe member. 2. The male-side tube member is formed with a protrusion so as to face the protrusion, and both protrusions are arranged adjacent to each other and are configured to abut each other. Or the piping joint device according to 2. 4. The second contact portion is formed as an inclined surface that is inclined in the pipe radial direction, and the inclined surface is configured to come into line contact with the fastening member. The pipe joint device according to any one of claims 1 to 3. 5. The second contact portion is formed as a contact surface parallel to the pipe radial direction, and the fastening member faces the contact surface parallel to the pipe radial direction. 4. A pipe according to any one of claims 1 to 3, wherein an abutting surface parallel to the pipe radial direction is formed, and the abutting surfaces are abutted with each other. Coupling device. 6. The pipe joint device according to claim 1, wherein the fastening member has a bilaterally symmetrical shape in the axial direction. 7. The pipe joint device according to claim 1, wherein the fastening member is formed of a resin having high temperature creep strength.