Abstract
A pipe joint structure has a joint body, a fixed ring and a union nut. A flared end of a tube has a conical surface and a tubular surface. The conical surface and tubular surface are connected to a tube connecting portion of the joint body. The union nut is fastened to a locking thread of the tube connecting portion. An interior recess portion of the union nut is coupled with a bulging surface of the fixed ring. The tube is compressed evenly and secured firmly on the joint body.
Claims
1. A pipe joint structure comprising: a main tube; the main tube being made of fluororesin materials; a pipe joint; the pipe joint being made of fluororesin materials; the pipe joint being fasten to an end of the main tube; the pipe joint comprising a joint body, a union nut and a fixed ring; the union nut comprising a tapered opening; the fixed ring comprising a central bore; the end of the main tube passing through the tapered opening of the union nut and the central bore of the fixed ring; the end of the main tube being expanded to form a flared end; the main tube comprising a cone tube and a cylindrical tube; the cone tube and the cylindrical tube being formed at the flared end; the joint body comprising a center through hole; the center through hole being configured to direct a fluid; the joint body further comprising a tube connecting portion at an end thereof; the tube connecting portion being engaged with the union nut and abutting against the main tube; the tube connecting portion comprising a conical surface, a cylindrical surface and a locking thread; the conical surface and the cylindrical surface of the tube connecting portion abutting against the cone tube and the cylindrical tube of the main tube; the conical surface comprising a conical angle ε, the conical angle ε being 50° to 75°; the locking thread being engaged with the union nut; the union nut further comprising an inner side, a threaded part, a recess and a tapered end; the threaded part, the recess and the tapered end being formed on the inner side; the threaded part of the union nut being engaged with the locking thread of the tube connecting portion; the center of said tapered end has a tapered opening containing an inner curved surface at its inner side; the recess comprising an applied force ring edge; the fixed ring further comprising a stress ring edge; the applied force ring edge of the recess abutting against the stress ring edge of the fixed ring; the fixed ring further comprising two bulging curved surfaces; the two bulging curved surfaces being formed near the central bore; the fixed ring further comprising a compression ring edge; the stress ring edge being formed on one of the two bulging curved surfaces; the compression ring edge being formed on the other one of the two bulging curved surfaces; the fixed ring further comprising a symmetrical or asymmetrical near-trapezoid cross-section; the compressing ring edge abutting against the cone tube, opposite to the conical surface; the bulging curved surface comprising a compressions angle β; the compressions angle β being 55° to 75°; a compression force; the compression force being transmitted to the compression ring edge; an applied force included angle θ; the applied force included angle θ being formed in between the compression force and a normal line of the conical surface; and the applied force included angle θ being 0° to 15°.
2. The pipe joint structure as claimed in claim 1 further comprising: an outer periphery of fixed ring being installed with a color-changing indicator paper strip capable of reacting with leaked fluid.
3. The pipe joint structure as claimed in claim 1 further comprising: the cone tube comprising a conical spot; and the compressing ring edge being prevented from abutting against the conical spot.
Description
BRIEF DESCRIPTIONS OF THE DRAWINGS
(1) FIG. 1A: The structural cross-section view showing the 1st embodiment example of pipe joint of the present invention.
(2) FIG. 1B: The diagram showing the 1st embodiment example of joint body of the present invention.
(3) FIG. 1C: The diagram showing the 1st embodiment example of union nut of the present invention.
(4) FIG. 1D: The diagram showing the 1st embodiment example of fixed ring of the present invention.
(5) FIG. 1E: The diagram showing the 1st embodiment example of fastening and compression of the present invention.
(6) FIG. 2A: The structural cross-section view showing the 2nd embodiment example of pipe joint of the present invention.
(7) FIG. 2B: The diagram showing the 2nd embodiment example of joint body of the present invention.
(8) FIG. 2C: The diagram showing the 2nd embodiment example of union nut of the present invention.
(9) FIG. 2D: The diagram showing the 2nd embodiment example of fixed ring of the present invention.
(10) FIG. 2E: The diagram showing the 2nd embodiment example of fastening and compression of the present invention.
(11) FIG. 3A: The structural cross-section view showing the 3rd embodiment example of pipe joint of the present invention.
(12) FIG. 3B: The diagram showing the 3rd embodiment example of joint body of the present invention.
(13) FIG. 3C: The diagram showing the 3rd embodiment example of union nut of the present invention.
(14) FIG. 3D: The diagram showing the 3rd embodiment example of fixed ring of the present invention.
(15) FIG. 3E: The diagram showing the 3rd embodiment example of fastening and compression of the present invention.
(16) FIG. 4A: The structural cross-section view showing the 4th embodiment example of pipe joint of the present invention.
(17) FIG. 4B: The diagram showing the 4th embodiment example of joint body of the present invention.
(18) FIG. 4C: The diagram showing the 4th embodiment example of union nut of the present invention.
(19) FIG. 4D: The diagram showing the 4th embodiment example of fixed ring of the present invention.
(20) FIG. 4E: The diagram showing the 4th embodiment example of fastening and compression of the present invention.
(21) FIG. 5A: The flaring deformation of pipe joint (2) after it has been subjected to tensile test.
(22) FIG. 5B: The flaring deformation of pipe joint (7) after it has been subjected to tensile test.
(23) FIG. 5C: The flaring deformation of pipe joint (7A) after it has been subjected to tensile test.
(24) FIG. 5D: The flaring deformation of pipe joint (1) after it has been subjected to tensile test.
(25) FIG. 6A: Description and comparison on U moving direction of sealed surface's wall material, based on the compression angle β=70° and conical angle ε=45°.
(26) FIG. 6B: Description and comparison on U moving direction of sealed surface's wall material, based on the compression angle β=70° and conical angle ε=60°.
(27) FIG. 6C: Description and comparison on V moving direction of sealed surface's wall material, based on the compression angle β=90° and conical angle ε=60°.
(28) FIG. 6D: Description and comparison on V moving direction of sealed surface's wall material, based on the compression angle β=70° and conical angle ε=60°.
(29) FIG. 6E: Description and comparison on V moving direction of sealed surface's wall material, based on the compression angle β=60° and conical angle ε=60°.
(30) FIG. 7A: Diagram showing the structural cross-section view of conventional pipe joint in cited case 1.
(31) FIG. 7B: Diagram showing the structural cross-section view of conventional pipe joint in cited case 2.
(32) FIG. 7C: Diagram showing the conventional disc-shaped anchor plate in cited case 2.
(33) FIG. 7D: Diagram showing the structural cross-section view of conventional pipe joint in cited case 5.
(34) FIG. 7E: Diagram showing the cross-section view of conventional pipe joint's fixed ring in cited case 5.
(35) FIG. 8: Diagram showing the plane exploded view of conventional pipe joint's parts in cited case 3.
(36) FIG. 9: Diagram showing the cross-section view of pipe joint after being fastened firmly in cited case 3.
DETAILED DESCRIPTION OF THE INVENTION
(37) The example of the 1st embodiment: As shown in FIG. 1A, FIG. 1B, FIG. 1C, FIG. 1D and FIG. 1E, the assembly drawing of first embodiment example of pipe joint (2) can be seen in FIG. 1A. The said pipe joint (2) is comprised of three parts, namely a joint body (20), a union nut (26) and a fixed ring (27), all being made of PFA material.
(38) The end portion of PFA tube (18) is initially passed through the tapered opening (261) of union nut (26) and the central bore (279) of fixed ring (27). After being cooled or heated by a jig, the expanded hole is transformed into a flared end (180), comprising of a conical tube (181) and a cylindrical tube (182).
(39) As shown in FIG. 1B, the joint body (20) features a central through hole (14) to direct the fluid. One end of the tube connecting portion (200) is used to connect with union nut (26) and tube (18), the other threaded end (12) to connect with other equipment or device, and the central tool engaging portion (15) to install with pipe joint (2).
(40) According to order, the tube connecting portion (200) features a conical surface (201), a cylindrical surface (202), a trust end (203) and locking thread (204). The conical surface (201) is used to install with cone tube (181) and cylindrical tube (182) of tube (18). The conical angle ε of the conical surface (201) comes in specification of 50°≦ε≦70°. The cylindrical wall thickness is able to allow the overall axial compression of pipe joint to have a more uniform deformation, and its locking thread (204) is used to fasten with union nut (26).
(41) As shown in FIG. 1C, the inner diameter of union nut (26) features a threaded part (266), a recess (262) and a tapered end (260). A shown in FIG. 1A, the threaded part 266) is used to fasten with the locking thread (204) of tube connecting portion (200). The center of tapered end (262) has a tapered opening (261) containing an inner recess (262) on its inner side. The said recess (262) comes with an applied force ring edge (2622) and a skew surface (2623). The outer fringe of inner recess (262) has a positioning curved surface (2621) that shrunk inward in a smooth arc manner, capable of coordinating with the stress ring edge (2702) to guide the fixed ring (27) into a center position. The skew surface (2623) has an axial gap (2624) much larger than the applied force curved surface (2622) to restrict the contact area of sliding surface, and reduce the generation of unfavorable influences caused by dimensional tolerance to lower the frictional risk of sliding.
(42) As shown in FIG. 1D, the fixed ring (27) features a central bore (279) and an annular bulging surface (270) on both edges. It features symmetrical or asymmetrical trapezoid cross-section area, with the outer periphery (271) having a shorter axial length for placing in with an indicator paper strip on top of the indicator paper slot (2711). One end of the bulging curved surface (270) nearer to the central bore (279) is a compressing ring (2701) for pressing against the tube wall. It has a compression angle β of specification 50°≦β≦75°, with sufficient lead angle space at the fringe of central bore to prevent the compression ring (2701) from pressing on the small conical diameter (186) site of cone tube (181), as this place is prong to generate tube wall hardening phenomenon and prevent the sealed surface from achieving a good seal. On the other side is a stress ring edge (2702) for coupling with the applied force ring edge (2622) of union nut (26) to form a sealed surface. The included angle starting from the stress point of stress ring surface (2702) to the connecting line of compression ring (2701) and the center line of central bore (279) is known as the compression angle γ of compression F, with a specification of 10°≦γ≦30°
(43) As shown in FIG. 1E, during the locking process of union nut (26), the axial direction of extended tube (18) will compress the flared end (180) to form a sealed surface (180). Coupled with its compression angle β of specification 50°≦β≦75°, it will cause the tube wall to generate a continuous cumulative deformation to strengthen the pulling resistance ability. During the locking process, the fixed ring (27) will maintain at the center position by means of a guiding mechanism, being made up of the positioning curved surface (2621) of inner periphery (262) plus the stress ring's curved surface (2702) to guide the fixed ring (27) to stay at the center position. This will allow the compression force F to distribute evenly around the circumferential direction. The applied force angle γ of compression force F of specification γ≦30° will generate an applied force angle θ of specification 5°≦θ≦15°, thereby improving the normal distribution force Fn to increase the pulling resistance distribution force Ft to achieve a sealing effect and prevent the tube from being subjected to external stretch and slip off. When the fixed ring (27) is subjected to pressure and deform, the sliding surface's contact area created by applied force ring edge (2622) and stress ring edge (2702) will enlarge following the deformation. To avoid the fixed ring (27) from rotating caused by invalid sliding resulted from enlarged stress area, the axial gap of skew surface (2623) will restrict the stress deformation into a certain range to ensure a continuous sliding motion. This is to ensure that the sealed surface (183) resulted from coupling sliding action of fixed ring (27) and union nut (26) will not generate friction. In other words, no experienced operator and careful management are needed in applying the torque to achieve a sealing effect and prevent the tube (18) from being subjected to external stretch and slip off.
(44) The example of the 2nd embodiment: As shown in FIG. 2A, FIG. 2B, FIG. 2C, FIG. 2D and FIG. 2E, this example has a structural difference at tube connecting portion (300) of joint body (30) as compared with the 1st embodiment case. The assembly drawing of the 2nd embodiment example of pipe joint (3) can be seen in FIG. 2A. The said pipe joint (3) is comprised of three parts, namely a joint body (30), a union nut (36) and a fixed ring (37), all being made of fluorine material.
(45) The end portion of PFA tube (18) is initially passed through the tapered opening (361) of union nut (36) and the central bore (379) of fixed ring (37). After being cooled or heated by a jig, the expanded hole is transformed into a flared end (180), comprising of a conical tube (181) and a cylindrical tube (182).
(46) As shown in FIG. 2B, the joint body (30) features a central through hole (14) to direct the fluid. One end of the tube connecting portion (300) is used to connect with union nut (36) and tube (18), the other threaded end (12) to connect with other equipment or device, and the central tool engaging portion (15) to install with pipe joint (3).
(47) The tube connecting portion (300) is made up of a conical surface (301), a cylindrical surface (302) and locking thread (304). It is composed of an annular slot (3052) separated by a dual-concentric structure of outer periphery and inner periphery. The surface of outer periphery comes with locking thread (304), and the surface of inner periphery contains a conical surface (301) and cylindrical surface (302). The annular slot (3052) lies between the cylindrical surface (302) and guiding inner diameter (3051), the base of which has a trust end (3053). The space of this annular slot (3052) is big enough to accommodate the cylindrical tube (181). The conical surface (301) and the cylindrical surface (302) are used to install with cone tube (181) of tube (18) and the cylindrical tube (182). When the cone tube (181) is subjected to compression, its inner wall will abut the conical surface (301). The conical angle ε of conical surface (301) of specification 50°≦ε≦75° and the wall thickness of cylindrical surface (302) will allow the overall axial compression of pipe joint to generate a more uniform deformation, and the locking thread (304) is used to fasten with union nut (36).
(48) As shown in FIG. 2C, the inner diameter of union nut (36) has a threaded part (366), an inner recess (362) and a tapered end (360). The threaded part (366) is used to fasten with the locking thread (304) of tube connecting portion (300). The center of tapered end (360) has a tapered opening (361) that comprises of an inner recess (362) at the inner side. The said inner recess contains an applied force ring edge (3622) and a skew surface (3623). The applied force ring edge (3622) is able to couple with the stress ring curved edge (3702) to form a sliding surface to transmit the compression force F to fixed ring (37). The skew surface (3623) has a much larger axial gap (3624) than the applied force ring edge (3622) to restrict the sliding surface's contact area within a certain range, thereby reducing unfavorable influences caused by dimensional tolerance to lower the frictional risk of sliding.
(49) As shown in FIG. 2D, the fixed ring (37) features a central bore (379) and an annular bulging surface (370) on both edges. Its cross-section area shows a symmetrical or asymmetrical trapezoid structure, with the outer periphery (371) having a shorter axial length. This outer periphery (371) is able to coordinate with the guiding inner diameter (3051) of tube connecting portion (300) to guide the fixed ring (37) to stay at the center position. There is a compression ring (3701) with a compression angle β of specification 55°≦β≦75° near the central bore (379) on one side of the bulging surface (370) that used to abut the tube wall of cone tube (181). The lead angle at the fringe of central bore has sufficient space to prevent the compression ring (3701) from compressing the small conical diameter (186) site of cone tube (181), as this place is prong to generate tube wall hardening phenomenon and prevent the sealed surface from achieving a good seal. There is a stress ring edge (3702) on the other side for coupling with the applied force ring edge (3622) of union nut (36) to form a sliding surface. The included angle starting from the stress point of stress ring surface (3702) to the connecting line of compression ring (3701) and the center line of central bore (379) is known as the compression angle γ of compression F, with a specification of γ≦30°.
(50) As shown in FIG. 2E, during the locking process of union nut (36), the axial of extended tube (181) will compress the flared end (180) of cone tube (181) to form a sealed surface. Coupled with its compression angle β of specification 50°≦β≦75°, it will cause the tube wall to generate a continuous cumulative deformation to strengthen the pulling resistance ability. During the locking process, the fixed ring (37) will maintain at the center position by means of a guiding mechanism, being made up of the guiding inner diameter (3051) of tube connecting portion (300) and the outer periphery (371) of fixed ring (37) to guide the fixed ring (37) to stay at the center position. This will allow the pressing force F to distribute evenly around the circumferential direction. The applied force angle γ of compression force F of specification 10°≦γ≦30° and applied force included angle ↓ of specification 5°≦θβ15° will improve the normal distribution force Fn and increase the pulling resistance distribution force Ft to achieve the sealing effect and prevent the tube from being subjected to external stretch and slip off. When the fixed ring (37) is subjected to pressure and deform, the sliding surface's contact area created by applied force ring edge (3622) and the stress ring edge (3702) will enlarge following the deformation. To avoid the fixed ring (37) from rotating caused by invalid sliding resulting from enlarged stress area, the axial gap of skew surface (3623) is able to restrict the stress deformation into a certain range to ensure a continuous sliding motion. This is to ensure that the sealed surface (183) resulted from coupling sliding of fixed ring (37) and union nut (36) will not generate friction. In other words, no experienced operator and careful management are needed in applying the torque to achieve a sealing effect and prevent the tube (18) from being subjected to external stretch and slip off.
(51) The example of the 3rd embodiment: As shown in FIG. 3A, FIG. 3B, FIG. 3C, FIG. 3D and FIG. 3E, this example has a structural difference in the tube connecting portion (400) of joint body (40) as compared with the 2nd embodiment case. The assembly drawing of the 3rd embodiment example of pipe joint (4) can be seen in FIG. 3A. The said pipe joint (4) is comprised of three parts, namely a joint body (40), a union nut (46) and a fixed ring (47), all being made of fluorine material.
(52) As shown in FIG. 3B, the tube connecting portion (400) is made up of a conical surface (401), a cylindrical surface (402) and locking thread (404). It is composed of an annular slot (4052) separated by a dual-concentric structure of outer periphery and inner periphery. The conical surface (401) of tube connecting portion (400) is vertical with a conical angle ε of specification ε=90°. When the cone tube (181) is subjected to compression, the point where the wall is pressed by the compression ring (4701) will response with more deformation, allowing the inner wall of sealed surface to abut on the conical surface (401). Meanwhile, the wall thickness of cylindrical wall (402) is able to allow the overall axial compression on pipe joint to have a more uniform deformation.
(53) As shown in FIG. 3C, the inner diameter of union nut (46) has a threaded part (466), an inner recess (462) and a tapered end (460). The inner side of tapered end (460) is an inner recess (462) containing an applied force ring edge (4622) located near the central bore and a skew surface (4623). The applied force ring edge (4622) is able to couple with the stress ring edge (4702) to form a coupling sliding surface to transmit the compression force F to fixed ring (47). The skew surface (4623) has a much larger axial gap (4624) than the applied force edge (4622) to restrict this contact area of coupling sliding surface within a certain range, thereby reducing the unfavorable influences and lower the frictional risk of sliding at the sealed surface.
(54) As shown in FIG. 3D, the fixed ring (47) features a central bore (479) and at least an annular bulging surface (470) at one edge. Its cross-section area shows a symmetrical or asymmetrical trapezoid structure, with the outer periphery (471) having a shorter axial length being able to coordinate with the guiding inner diameter (4051) of tube connecting portion (400) to guide the fixed ring (47) to stay at the center position. There is a compression ring (4701) with a compression angle β of specification 55°≦β≦75° near the central bore (479) on one side of the bulging surface (470) to abut the tube wall of cone tube (181). The lead angle at the fringe of central bore has sufficient space to prevent the compression ring (4701) from pressing on the small conical diameter (186) site of cone tube (181), as this place is prong to generate tube wall hardening phenomenon and prevent the sealed surface from achieving a good seal. The force stress ring edge (4702) on the other side is used to couple with the applied force ring edge (4622) of union nut (46) to form a sliding surface. The included angle starting from the stress point of stress ring surface (4702) to the connecting line of compression ring (4701) and the center line of central bore (479) is known as the compression angle γ of compression F, with a specification of γ≦10°.
(55) As shown in FIG. 3E, during the locking process of union nut (46), the axial of extended tube (18) will compress the tapered end (180) of cone tube (181), forcing the cone tube (181) to make local deformation. There is also an annular surface to abut the conical surface (401) with an angle γ=90°. Coupled with its compression angle β of specification 50°≦β≦75°, the annular sealed surface (183) will cause the tube wall to generate a continuous cumulative deformation to strengthen the pulling resistance ability. During the locking process, the fixed ring (47) will maintain at the center position by means of a guiding mechanism, being made up of the guiding inner diameter (4051) of tube connecting portion (400) and the outer periphery (471) of fixed ring (47) to guide the fixed ring (47) to stay at the center position. This will allow the compression force F to distribute evenly around the circumferential direction. The applied force angle γ of compression force F of specification 0°≦γ≦10° and the applied force included angle θ of specification 0°≦θ≦15° will improve the normal distribution force Fn and increase the pulling resistance distribution force Ft to achieve a sealing effect and prevent the tube from being subjected to external stretch and slip off. When the fixed ring (47) is subjected to pressure and deform, the sliding surface's contact area created by applied force ring edge (4622) and the stress ring edge (4702) will enlarge following the deformation. To avoid the fixed ring (47) from rotating caused by invalid sliding resulting from enlarged stress area, the axial gap of skew surface (4623) is able to restrict the stress deformation into a certain range to ensure a continuous sliding motion. This is to guarantee that the sealed surface (183) resulted from coupling sliding of fixed ring (47) and union nut (46) will not generate friction. In other words, no experienced operator and careful management are needed in applying the torque to achieve a sealing effect and prevent the tube (18) from being subjected to external stretch and slip off.
(56) The example of the 4th embodiment: As shown in FIG. 4A, FIG. 4B, FIG. 4C, FIG. 4D and FIG. 4E, it is difference from the 3rd cited case for being able to ensure that the fixed ring (57) will not move completely. The assembly drawing of the 4th embodiment example of innovative pipe joint (5) can be seen in FIG. 4A. The said pipe joint (5) is comprised of three parts, namely a joint body (50), a union nut (56) and a fixed ring (57), all being made of fluorine material.
(57) As shown in FIG. 4B, the tube connecting portion (500) is made up of a conical surface (501), a cylindrical surface (502) and locking thread (504). It is composed of an annular slot (5052) separated by a dual-concentric structure of outer periphery and inner periphery. The conical surface (501) of the tube connecting portion (500) is vertical with a conical angle ε of specification ε=90°. When the cone tube (181) is subjected to compression, the point where the wall is compressed by the compression ring (5701) will response with more deformation, allowing the inner wall of sealed surface to abut on the conical surface (501). Meanwhile, the wall thickness of cylindrical surface (502) is able to allow the overall axial compression on pipe joint to have a more uniform deformation.
(58) As shown in FIG. 4C, the inner diameter of union nut (56) has a threaded part (566), an inner recess (562) and a tapered end (560). The inner side of tapered end (560) is an inner recess (562) containing an applied force ring edge (5622) located near the central bore. The applied force ring edge (5622) is able to couple with the stress ring edge (5702) to form a coupling sliding surface to transmit the compression force F to fixed ring (57).
(59) As shown in FIG. 4D, the fixed ring (57) features a central bore (579) and at least an annular bulging surface (570) at one edge. Its cross-section area shows a symmetrical or asymmetrical trapezoid structure, with the outer periphery (571) having a shorter axial length being able to coordinate with the guiding inner diameter (5051) of tube connecting portion (500) to guide the fixed ring (57) to stay at the center position. This outer periphery (571) has a plurality of axial slots (5711) to coordinate with the plurality of bulging ribs (5052) found at the guiding inner diameter (5051) of tube connecting portion (500), preventing the fixed ring (57) from rotating and completely eliminating the sliding friction on the sealed surface (183). The bulging surface (570) at the other end near the central bore (579) is a compression ring (5701) with a compression angle β of specification 55°≦β≦75° for compressing the tube wall of cone tube (181). The lead angle at the fringe of central bore has sufficient space to prevent the compression ring (5701) from compressing the small conical diameter (186) site of cone tube (181), as this place is prong to generate tube wall hardening phenomenon and prevent the sealed surface from achieving a good seal. The stress ring edge (5702) on the other side will couple with the applied force ring edge (5622) of union nut (56) to form a sliding surface. The included angle starting from the stress point of stress ring surface (4702) to the connecting line of compression ring (4701) and the center line of central bore (479) is known as the compression angle γ of compression F, with a specification of γ≦10°.
(60) As shown in FIG. 4E, during the locking process of union nut (56), the axial extended tube (18) will compress the tapered end (180) of cone tube (181) to form a sealed surface (183). Coupled with its compression angle β of specification 50°≦β≦75°, it will cause the tube wall to generate a continuous cumulative deformation to strengthen the pulling resistance ability. During the locking process, the fixed ring (57) will maintain at the center position by means of a guiding mechanism, being made up of the guiding inner diameter (5051) of tube connecting portion (500) and the outer periphery (571) of fixed ring (57) to guide the fixed ring (57) to stay at the center position. This will allow the compression force F to distribute evenly around the circumferential direction. The applied force angle γ of compression force F of specification 0°≦γ≦10° and the applied force included angle θ of specification 0°≦θ≦15° will improve the normal distribution force Fn and increase the pulling resistance distribution force Ft to achieve a sealing effect and prevent the tube from being subjected to external stretch and slip off. The axial slot (5711) at the outer periphery of (571) of fixed ring (57) will coordinate with the bulging rib (5054) of guiding inner diameter (5051) to allow only an axial motion of extended tube (18) and not a rotational movement. This will completely eliminate sliding friction of the sealed surface (183) to achieve a sealing effect and prevent the tube (18) from being subjected to external stretch and slip off.
(61) Please refer to Table 1. The respective pipe joint (2), pipe joint (3), pipe joint (7), pipe joint (7A) and pipe joint (1) have one end of their tube (18) being welded and sealed, and fastened firmly. After undergoing a 150° C. high-temperature baking procedure, they are conducted with a hydrostatic pressure resistance test to obtain the maximum pressure resistance values. Only pipe joint (2) and pipe joint (3) were found to withstand the non-leakage requirement of 7 bar pressure, i.e. when the distribution compression force Fn of the sealed surface being able to distribute evenly. Both pipe joint (2) and pipe joint (3) were found to have a uniform compression deformation when fastened to various parts. These compression deformations within the elasticity range will lose part of their elasticity and lower their compression forces when subjected to 150° C. high-temperature heating, but they are still able to maintain a uniform compression deformation on the sealed surface with a better compression force.
(62) TABLE-US-00001 TABLE 1 Hydrostatic Pressure Test Values of 1″ Tubes After Being Baked Pipe joint (2) and (3) in the Pipe joint (7) Pipe joint (7A) Pipe joint (1) Specifi- present in the cited in the cited in the cited cation invention case 1 case 2 case 5 Pressure 9 1 1.5 3 kg/cm.sup.2
(63) Please refer to Table 2. The 1″ PFA tubes has a basic wall thickness of 1.6 mm thick, and their flared ends (180) of tubes (18) are fastened firmly with four different pipe joints. The center portion of straight tube portion (184) is subjected to stretch. The said pulling strength value is based on the condition where one end of the tube (18) has been stretched, and that elongation rate referred to the comparison value of final plastic deformation length over the original length of the straight tube portion (184) where the tube (18) has been stretched. The test results indicate that the pulling resistance ability of the innovative pipe joint is found to be outstanding, with an elongation rate of exceeding two times its original length.
(64) TABLE-US-00002 TABLE 2 Tensile Test Values of 1″ Pipe Joints Pipe joint (2) and (3) in the Pipe joint (7) Pipe joint (7A) Pipe joint (1) Specifi- present in the cited in the cited in the cited cation invention case 1 case 2 case 5 Tensile >180 kg >110 kg >110 kg >160 kg Strength Value(Kg) Elonga- >2 >1.1 >1.2 >1.6 tion (100%)
(65) Please refer to FIG. 5A, FIG. 5B, FIG. 5C and FIG. 5D which shows the flared end (180) of tube (18) and the deformed condition of straight tube portion (184) after they have been conducted with tensile test. Among them, FIG. 5A is pipe joint (2), FIG. 5B is pipe joint (7), FIG. 5C is pipe joint (7A) and FIG. 5E is pipe joint (1). After tube (18) has been stretched, the tube wall's material moving manner of sealed surface (183) is related to whether or not the compression distribution force Fn of sealed surface is able to distribute evenly.
(66) The straight tube (184) portions of pipe joint (2) and pipe joint (3) have been stretched twice longer than their original lengths, and their flared ends (180) have been stretched to become a regular conical shape where their opening end portions have formed a thicker round ring (185) in near annular design, indicating that their sealing abilities are the best.
(67) The straight tube (184) of pipe joint (7) has been stretched twice longer than its original length, and the flared end (180) been stretched to become an irregular conical shape but no annular ring has been formed on the opening portion, indicating that it has a poor sealing ability.
(68) The straight tube portion (184) of pipe joint (7A) has been stretched twice longer than its original length, and the flared end (180) been stretched to become an irregular conical shape where almost no annular ring has been formed on the opening portion. This indicates that it has a poor sealing ability and the disc-shaped anchor plate (77) has helped to improve the sealing ability but it has yet to meet with requirements.
(69) The straight tube portion (184) of pipe joint (7A) has been stretched less than two times its original length, and the flared end (180) been stretched to become an irregular conical shape. Its opening end has shown a fixed ring (185) to indicate it has a poor sealing ability. The fixed ring (17) has significantly helped to improve the sealing ability but it has yet to meet with requirements.
(70) From the above tests on stretch deformation of flared end (180), we are able to understand the sealed surface (183) further, whether or not the compression distribution force Fn is able to distribute evenly. For example, pipe joint (2) has shown a regular conical shape to denote a uniform distribution, whereas, the remaining cases have shown uneven distribution.
(71) More detailed descriptions on the formation and appearance of annular ring (185) are shown in FIG. 6A, FIG. 6B, FIG. 6C, FIG. 6D and FIG. 6D. Under the circumstances that the compression distribution force Fn of sealed surface (183) is adequate, and when the tube wall of sealed surface is subjected to stretching force T, the cone tube's wall material moving direction U and the applied force ring's wall material moving direction V are related to the included angle λ of pulling force T. This represents that it is the course where the sealed surface's wall material must change when subjected to stress deformation and moves, and that the material moving directions on the tube walls of both sealed surfaces are different.
(72) When the conical angle ε of conical surface is 45°, the material moving included angle of conical surface's tube wall moving direction U is 45°, wherein the material movement has to change and make a 45° turn. When the conical angle is 60°, the material moving included angle has increased to 60°, making it hard to move as the material movement has to change and make a 60° turn. When the compression angle β is 90°, the material moving included angle λ of compression ring's tube wall material moving direction V is 90°; when the compression angle λ is 70°, the material moving included angle has to increase to 110°, obviously making it hard to move as the material movement has to change and bypass 110°. When the compression angle β is 60°, the material moving included angle λ has to increase to 120°, obviously making it more difficult to move as the tube wall material movement has to bypass the compression angle by 120°.
(73) From the sizes of material moving included angles mentioned above, we are able to understand the relative movements of tube wall materials on the conical surface, indicating that an adequate compression distribution force Fn is needed to apply on the sealed surface (183) before it is able to reduce the excessive material movement and lower the pulling resistance ability, and the wall material on the compression angle β will relatively hard to move. Hence, the smaller the compression angle β, the harder is the movement of wall material. When there is enough compression distribution force Fn, there is more wall material on compression angle β to generate a continuous annular deformation to accumulate wall thickness δ when it is subjected to pulling force. The accumulated material thickness δ is generated from plastic deformation, which will relatively move towards the tube opening end continuously to form a thicker annular ring (185). When the compression angle β is 90°, the material moving included angle λ of compression surface's tube wall moving direction V is 90°. At this point, the tube wall material movement is relatively simple as it only needs to bypass the compression angle by 90° and not easy to generate a continuous annular deformation and an accumulated wall thickness δ. In other words, it is unlikely to form an annular ring (185) around the opening and cannot achieve a high pulling resistance ability. As shown in FIG. 6D and FIG. 6D of respective compression angles β of 70° and 90°, when the compression angle β is smaller than 90°, the material moving included angle λ of compression ring's tube wall moving direction V will be greater than 90°. At this point, the tube wall material movement will need to bypass the compression angle greater than 90°. Furthermore, the smaller the compression angle β, the greater is the material moving included angle λ and the harder it is for the material to move. This will easily generate a continuous annular deformation and cumulative wall thickness δ, and easier to form an annular ring (185) around the opening to achieve a high pulling resistance ability.
EFFECTS OF THE INVENTION
(74) The result findings of pipe joint (2), pipe joint (3) and pipe joint (4) in these examples indicate that they have a high sealing ability, as fixed ring (27), fixed ring (37) and fixed ring (47) are truly able to secure on the center position, allowing the compression force distribution force Fn of sealing surface (183) to distribute evenly to maintain the compression angle as close as 10° and increase the Fn distribution force. After undergoing a tensile test on these embodiment examples, they have been found to generate an annular cumulative deformation of tube wall material to increase the pulling force ability. Pipe joint (5) can even immobilize the fixed ring (57) completely and eliminate the frictional risk of sliding on the sealed surface.
