US20240044425A1 - Pipe joint - Google Patents

Pipe joint Download PDF

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Publication number
US20240044425A1
US20240044425A1 US18/258,813 US202118258813A US2024044425A1 US 20240044425 A1 US20240044425 A1 US 20240044425A1 US 202118258813 A US202118258813 A US 202118258813A US 2024044425 A1 US2024044425 A1 US 2024044425A1
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US
United States
Prior art keywords
tube
bulge
tapered
axial
press
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Pending
Application number
US18/258,813
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English (en)
Inventor
Yohei Okawa
Ayumi Kurosaki
Shingo Higuchi
Kazukiyo Teshima
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Nippon Pillar Packing Co Ltd
Original Assignee
Nippon Pillar Packing Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Nippon Pillar Packing Co Ltd filed Critical Nippon Pillar Packing Co Ltd
Assigned to NIPPON PILLAR PACKING CO., LTD. reassignment NIPPON PILLAR PACKING CO., LTD. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: HIGUCHI, SHINGO, KUROSAKI, Ayumi, TESHIMA, KAZUKIYO, OKAWA, YOHEI
Publication of US20240044425A1 publication Critical patent/US20240044425A1/en
Pending legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16L—PIPES; JOINTS OR FITTINGS FOR PIPES; SUPPORTS FOR PIPES, CABLES OR PROTECTIVE TUBING; MEANS FOR THERMAL INSULATION IN GENERAL
    • F16L47/00—Connecting arrangements or other fittings specially adapted to be made of plastics or to be used with pipes made of plastics
    • F16L47/04—Connecting arrangements or other fittings specially adapted to be made of plastics or to be used with pipes made of plastics with a swivel nut or collar engaging the pipe
    • F16L47/041—Connecting arrangements or other fittings specially adapted to be made of plastics or to be used with pipes made of plastics with a swivel nut or collar engaging the pipe the plastic pipe end being flared either before or during the making of the connection
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16L—PIPES; JOINTS OR FITTINGS FOR PIPES; SUPPORTS FOR PIPES, CABLES OR PROTECTIVE TUBING; MEANS FOR THERMAL INSULATION IN GENERAL
    • F16L19/00—Joints in which sealing surfaces are pressed together by means of a member, e.g. a swivel nut, screwed on or into one of the joint parts
    • F16L19/04—Joints in which sealing surfaces are pressed together by means of a member, e.g. a swivel nut, screwed on or into one of the joint parts using additional rigid rings, sealing directly on at least one pipe end, which is flared either before or during the making of the connection
    • F16L19/05—Joints in which sealing surfaces are pressed together by means of a member, e.g. a swivel nut, screwed on or into one of the joint parts using additional rigid rings, sealing directly on at least one pipe end, which is flared either before or during the making of the connection with a rigid pressure ring between the screwed member and the exterior of the flared pipe end
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16L—PIPES; JOINTS OR FITTINGS FOR PIPES; SUPPORTS FOR PIPES, CABLES OR PROTECTIVE TUBING; MEANS FOR THERMAL INSULATION IN GENERAL
    • F16L13/00—Non-disconnectible pipe-joints, e.g. soldered, adhesive or caulked joints
    • F16L13/14—Non-disconnectible pipe-joints, e.g. soldered, adhesive or caulked joints made by plastically deforming the material of the pipe, e.g. by flanging, rolling
    • F16L13/16—Non-disconnectible pipe-joints, e.g. soldered, adhesive or caulked joints made by plastically deforming the material of the pipe, e.g. by flanging, rolling the pipe joint consisting of overlapping extremities having mutually co-operating collars
    • F16L13/165—Non-disconnectible pipe-joints, e.g. soldered, adhesive or caulked joints made by plastically deforming the material of the pipe, e.g. by flanging, rolling the pipe joint consisting of overlapping extremities having mutually co-operating collars the pipe or collar being deformed by an axially movable sleeve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16L—PIPES; JOINTS OR FITTINGS FOR PIPES; SUPPORTS FOR PIPES, CABLES OR PROTECTIVE TUBING; MEANS FOR THERMAL INSULATION IN GENERAL
    • F16L33/00—Arrangements for connecting hoses to rigid members; Rigid hose connectors, i.e. single members engaging both hoses
    • F16L33/24—Arrangements for connecting hoses to rigid members; Rigid hose connectors, i.e. single members engaging both hoses with parts screwed directly on or into the hose
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16L—PIPES; JOINTS OR FITTINGS FOR PIPES; SUPPORTS FOR PIPES, CABLES OR PROTECTIVE TUBING; MEANS FOR THERMAL INSULATION IN GENERAL
    • F16L47/00—Connecting arrangements or other fittings specially adapted to be made of plastics or to be used with pipes made of plastics
    • F16L47/04—Connecting arrangements or other fittings specially adapted to be made of plastics or to be used with pipes made of plastics with a swivel nut or collar engaging the pipe

Definitions

  • the present invention relates to a pipe joint.
  • a pipe joint made of a synthetic resin is used as a connection structure that connects flow passages formed in tubes or fluid devices.
  • a pipe joint that includes an inner ring mounted on the inner circumferential side of an end portion of a tube, a cylindrical joint body mounted on the outer circumferential side of the end portion of the tube, and a union nut mounted on the outer circumferential side of the joint body, is known (see, for example, PATENT LITERATURE 1).
  • the inner ring has a cylindrical body portion, a bulge portion formed at one axial end portion of the body portion so as to project toward a radially outer side, and a sealing portion formed at another axial end portion of the body portion.
  • a fluid flow passage is formed inside the inner ring.
  • the bulge portion of the inner ring is press-fitted into the end portion of the tube to increase the diameter of the end portion of the tube.
  • the union nut presses the outer circumferential surface of the tube whose diameter has been increased by the bulge portion of the inner ring, by the thrust force of the union nut when the union nut is attached to the joint body. Accordingly, the sealing portion of the inner ring is pressed into a sealing groove formed on the joint body, and coming-out of the tube can also be prevented. Furthermore, a surface pressure is generated between the tube and the bulge portion, so that a fluid can be inhibited from leaking from between the tube and the bulge portion.
  • the present invention has been made in view of such circumstances, and an object of the present invention is to provide a pipe joint that can ensure a required surface pressure between a bulge portion of an inner ring and a tube even if the tightening torque of a union nut is not increased.
  • a pipe joint of the present invention includes: an inner ring having a bulge portion formed on one axial side so as to project toward a radially outer side, the bulge portion being for press-fitting into an end portion of a tube; a joint body having an inner circumference into which an end portion on another axial side of the inner ring is to be press-fitted in a state where the bulge portion is press-fitted into the end portion of the tube, the joint body having an external thread portion on an outer circumference thereof; and a union nut having an internal thread portion to be tightened to the external thread portion, and configured to press the end portion of the tube toward the other axial side when the internal thread portion is tightened to the external thread portion, wherein the bulge portion has a tapered portion formed so as to be tapered from a middle portion in an axial direction thereof toward the one axial side and configured to generate a surface pressure between the tube and the tapered portion by pressing by the union nut, and an outer circumferential surface of the tapered portion has a concave
  • the concave surface portion is formed in the outer circumferential surface of the tapered portion in the bulge portion of the inner ring, when the union nut presses the tube, the tube is less likely to come into contact with a bottom portion of the concave surface portion. Accordingly, the axial range where the surface pressure is generated between the tapered portion of the bulge portion and the tube is narrower than that in the conventional art, so that the surface pressure generated between the tapered portion of the bulge portion and the tube can be made larger than that in the conventional art. Therefore, even if the tightening torque of the union nut is not increased, the required surface pressure can be ensured between the bulge portion of the inner ring and the tube. As a result, a fluid can be inhibited from leaking from between the bulge portion and the tube to the outside.
  • the concave surface portion is formed over an entire axial length of the outer circumferential surface of the tapered portion.
  • the axial range where the surface pressure is generated between the tapered portion of the bulge portion and the tube can be made further narrower, so that the surface pressure generated between the tapered portion of the bulge portion and the tube can be further increased.
  • the outer circumferential surface of the tapered portion has a convex surface portion formed in a convex surface shape on the one axial side with respect to the concave surface portion in the axial cross-sectional view.
  • the thickness in the radial direction of an end portion on the one axial side can be larger than the concave surface portion in the tapered portion. Accordingly, the strength of the end portion of the tapered portion is increased, so that, even when the tapered portion is pressed via the tube by the union nut, the end portion of the tapered portion can be inhibited from falling down toward the radially inner side. As a result, the flow of the fluid in the inner ring can be inhibited from being obstructed by the tapered portion of the bulge portion.
  • a pipe joint includes: an inner ring having a bulge portion formed on one axial side so as to project toward a radially outer side, the bulge portion being for press-fitting into an end portion of a tube; a joint body having an inner circumference into which an end portion on another axial side of the inner ring is to be press-fitted in a state where the bulge portion is press-fitted into the end portion of the tube, the joint body having an external thread portion on an outer circumference thereof; and a union nut having an internal thread portion to be tightened to the external thread portion, and configured to press the end portion of the tube toward the other axial side when the internal thread portion is tightened to the external thread portion, wherein the bulge portion has a tapered portion formed so as to be tapered from a middle portion in an axial direction thereof toward the one axial side and configured to generate a surface pressure between the tube and the tapered portion by pressing by the union nut, and a diameter D of one axial end of an outer
  • the diameter D of the one axial end of the outer circumferential surface of the tapered portion in the bulge portion of the inner ring and the inner diameter d of the non-deformed portion of the tube satisfy the relationship of D ⁇ 1.4d, the tightening torque of the union nut is not increased.
  • the diameter D of the one axial end of the outer circumferential surface of the tapered portion and the inner diameter d of the non-deformed portion of the tube satisfy the relationship of 1.0d ⁇ D, even if the tightening torque of the union nut is not increased, the required surface pressure can be ensured between the bulge portion of the inner ring and the tube. As a result, a fluid can be inhibited from leaking from between the bulge portion and the tube to the outside.
  • FIG. 1 is an axial cross-sectional view of a pipe joint according to a first embodiment of the present invention.
  • FIG. 2 is an axial cross-sectional view showing an inner ring of the pipe joint.
  • FIG. 3 is an enlarged cross-sectional view of a main part of FIG. 2 , showing a bulge portion of the inner ring.
  • FIG. 4 is a cross-sectional view showing a contact state between a tapered portion of the bulge portion and a tube.
  • FIG. 5 is a cross-sectional view showing a state where the tapered portion of the bulge portion has fallen down toward the radially inner side.
  • FIG. 6 is an enlarged axial cross-sectional view showing a bulge portion of an inner ring in a pipe joint according to a second embodiment of the present invention.
  • FIG. 7 is a cross-sectional view showing a contact state between a tapered portion of the bulge portion and a tube in the second embodiment.
  • FIG. 8 is an enlarged axial cross-sectional view showing an area around a bulge portion of an inner ring in a pipe joint according to a third embodiment of the present invention.
  • FIG. 9 is an enlarged axial cross-sectional view showing a modification of the bulge portion of the inner ring in the third embodiment.
  • FIG. 1 is an axial cross-sectional view showing a pipe joint according to a first embodiment of the present invention.
  • a pipe joint 1 is used, for example, in a pipe path through which a chemical solution (fluid) used in a semiconductor manufacturing apparatus flows.
  • the pipe joint 1 includes a joint body 2 , a union nut 3 , and an inner ring 4 .
  • the left side of FIG. 1 is referred to as one axial side
  • the right side of FIG. 1 is referred to as another axial side (the same applies to FIG. 2 to FIG. 9 ).
  • the inner ring 4 is formed in a cylindrical shape, for example, from a synthetic resin material such as polyvinyl chloride (PVC), polypropylene (PP), polyethylene (PE), or a fluorine resin (perfluoroalkoxy alkane (PFA), polytetrafluoroethylene (PTFE), polyvinylidene fluoride (PVDF), or the like).
  • a synthetic resin material such as polyvinyl chloride (PVC), polypropylene (PP), polyethylene (PE), or a fluorine resin (perfluoroalkoxy alkane (PFA), polytetrafluoroethylene (PTFE), polyvinylidene fluoride (PVDF), or the like.
  • the inner ring 4 includes a body portion 5 formed in a cylindrical shape, a bulge portion 6 formed on the one axial side of the body portion 5 , and a sealing portion 7 formed on the other axial side of the body portion 5 .
  • a fluid flow passage 4 a is formed on the radially inner side of each of the body portion 5 , the bulge portion 6 , and the sealing portion 7 in the inner ring 4 .
  • the fluid flow passage 4 a provides communication between a flow passage 8 a formed inside a tube 8 and a flow passage 2 c formed inside the joint body 2 .
  • the bulge portion 6 is formed on the one axial side of the body portion 5 so as to project toward the radially outer side.
  • the bulge portion 6 is press-fitted into an end portion of the tube 8 , which is made of a synthetic resin material (PFA or the like), to increase the diameter of the end portion of the tube 8 .
  • the bulge portion 6 will be described in detail later.
  • the sealing portion 7 has an annular primary sealing portion 7 a and a cylindrical secondary sealing portion 7 b.
  • the primary sealing portion 7 a is formed so as to project from the radially inner side of another axial end portion of the body portion 5 toward the other axial side.
  • the outer circumferential surface of the primary sealing portion 7 a is formed such that the diameter thereof gradually decreases from one axial end thereof toward another axial end thereof.
  • the primary sealing portion 7 a is press-fitted into a primary sealing groove 2 d (described later) of the joint body 2 .
  • the secondary sealing portion 7 b is formed so as to project from the radially outer side of the other axial end portion of the body portion 5 toward the other axial side.
  • the secondary sealing portion 7 b is press-fitted into a secondary sealing groove 2 e (described later) of the joint body 2 .
  • the joint body 2 is formed in a cylindrical shape, for example, from a synthetic resin material such as PVC, PP, PE, or a fluorine resin (PFA, PTFE, or the like).
  • the inner diameter of the joint body 2 is set to substantially the same dimension as the inner diameter of the inner ring 4 such that the movement of the chemical solution is not hindered.
  • a receiving portion 2 a is formed at one axial end portion of the joint body 2 .
  • the sealing portion 7 of the inner ring 4 in which the bulge portion 6 is press-fitted (at an end portion on the other axial side thereof) into the end portion of the tube 8 is press-fitted to the inner circumference of the receiving portion 2 a . Accordingly, the one axial end portion of the joint body 2 is mounted on the outer circumference of the end portion of the tube 8 .
  • An external thread portion 2 b is formed on the outer circumference of the receiving portion 2 a.
  • the joint body 2 has the annular primary sealing groove 2 d and the annular secondary sealing groove 2 e which are formed on the radially inner side with respect to the receiving portion 2 a .
  • the primary sealing groove 2 d is formed on the radially inner side of the joint body 2 in a tapered shape that is cut such that the diameter thereof gradually decreases from the one axial end thereof toward the other axial end thereof.
  • the secondary sealing groove 2 e is formed on the radially outer side with respect to the primary sealing groove 2 d in the joint body 2 .
  • the union nut 3 is formed in a cylindrical shape, for example, from a synthetic resin material such as PVC, PP, PE, or a fluorine resin (PFA, PTFE, or the like).
  • the union nut 3 has an internal thread portion 3 a formed on the inner circumference on the other axial side thereof, and a pressing portion 3 b formed on the one axial side thereof so as to project toward the radially inner side.
  • the internal thread portion 3 a of the union nut 3 is tightened to the external thread portion 2 b of the joint body 2 .
  • the union nut 3 is attached to the joint body 2 , and a corner portion 3 c formed at another axial end portion of the pressing portion 3 b presses a diameter-increased portion 8 b of the tube 8 whose diameter has been increased by the bulge portion 6 of the inner ring 4 .
  • the portion, of the pressing portion 3 b that presses the tube 8 is not limited to the corner portion 3 c .
  • a chamfered portion may be formed at the other axial end portion of the pressing portion 3 b instead of the corner portion 3 c , and the tube 8 may be pressed by the chamfered portion.
  • the primary sealing portion 7 a and the secondary sealing portion 7 b of the inner ring 4 are press-fitted into the primary sealing groove 2 d and the secondary sealing groove 2 e of the joint body 2 , respectively. Accordingly, sealing performance at the connection portion between the inner ring 4 and the joint body 2 can be ensured.
  • the corner portion 3 c of the union nut 3 can prevent coming-out of the tube 8 by pressing the diameter-increased portion 8 b of the tube 8 toward the other axial side.
  • FIG. 2 is an axial cross-sectional view of the inner ring 4 .
  • the bulge portion 6 of the inner ring 4 has a maximum thickness portion 11 in which the thickness in the radial direction thereof is maximum, a proximal end portion 12 formed on the other axial side of the maximum thickness portion 11 , and a tapered portion 13 formed on the one axial side of the maximum thickness portion 11 .
  • the maximum thickness portion 11 is formed over a predetermined length in the axial direction.
  • the outer circumferential surface of the proximal end portion 12 is formed such that the diameter thereof gradually decreases from another axial end of the maximum thickness portion 11 toward the other axial side. Accordingly, the proximal end portion 12 is formed such that the thickness in the radial direction thereof gradually decreases from the other axial end of the maximum thickness portion 11 toward the other axial side. Another axial end of the proximal end portion 12 is connected to the body portion 5 .
  • the outer circumferential surface of the proximal end portion 12 is inclined in a flat surface shape, but may be inclined in a curved surface shape.
  • An inner circumferential surface 14 of the tapered portion 13 is formed such that the diameter thereof gradually increases from the other axial side toward one axial end thereof.
  • An outer circumferential surface 15 of the tapered portion 13 is formed such that the diameter thereof gradually decreases from one axial end of the maximum thickness portion 11 toward the one axial side. Accordingly, the tapered portion 13 is formed such that the thickness in the radial direction thereof gradually decreases, that is, the tapered portion 13 is tapered, from a middle portion in the axial direction of the bulge portion 6 toward the one axial side.
  • FIG. 3 is an enlarged cross-sectional view of a main part of FIG. 2 , showing the bulge portion 6 of the inner ring 4 .
  • the outer circumferential surface 15 of the tapered portion 13 of the bulge portion 6 has a concave surface portion 15 a which is formed in a concave surface shape so as to be recessed radially inward.
  • the concave surface portion 15 a is formed, for example, in a concave arc shape.
  • the concave surface portion 15 a of the present embodiment is formed over the entire axial length of the outer circumferential surface 15 of the tapered portion 13 .
  • the concave surface portion 15 a is formed in the outer circumferential surface 15 of the tapered portion 13 in the bulge portion 6 of the inner ring 4 , when the diameter-increased portion 8 b of the tube 8 is pressed toward the other axial side by the union nut 3 (not shown) as shown in FIG. 4 , the inner circumferential surface of the tube 8 is less likely to come into contact with a bottom portion 15 al of the concave surface portion 15 a .
  • the axial range where the surface pressure is generated between the tapered portion 13 of the bulge portion 6 and the tube 8 is narrower than that in the conventional art, so that the surface pressure generated between the tapered portion 13 of the bulge portion 6 and the tube 8 can be made larger than that in the conventional art. Therefore, even if the tightening torque of the union nut 3 is not increased, the required surface pressure can be ensured between the bulge portion 6 of the inner ring 4 and the tube 8 . As a result, the chemical solution flowing through the fluid flow passage 4 a of the inner ring 4 can be inhibited from leaking from between the bulge portion 6 and the tube 8 to the outside.
  • the concave surface portion 15 a is formed over the entire axial length of the outer circumferential surface 15 of the tapered portion 13 , the axial range where the surface pressure is generated between the tapered portion 13 of the bulge portion 6 and the tube 8 can be further narrower than that in the case where the concave surface portion 15 a is formed in only a part in the axial direction of the outer circumferential surface 15 of the tapered portion 13 . Accordingly, the surface pressure generated between the tapered portion 13 of the bulge portion 6 and the tube 8 can be further increased.
  • the distal end portion of the tapered portion 13 since the thickness in the radial direction of a distal end portion (one axial end portion) of the tapered portion 13 is small, when the tapered portion 13 is pressed via the tube 8 by the union nut 3 , the distal end portion of the tapered portion 13 easily falls down toward the radially inner side (fluid flow passage 4 a side) as shown in FIG. 5 , so that the tube 8 and the inner circumferential surface 14 do not become flush with each other.
  • the distal end portion of the tapered portion 13 falls down as described above, the flow of the chemical solution in the fluid flow passage 4 a of the inner ring 4 may be obstructed by the distal end portion of the tapered portion 13 . Therefore, in a second embodiment described below, a configuration for inhibiting the distal end portion of the tapered portion 13 from falling down is provided.
  • FIG. 6 is an enlarged axial cross-sectional view showing a bulge portion 6 of an inner ring 4 in a pipe joint 1 according to the second embodiment of the present invention.
  • the shape of an outer circumferential surface 15 of a tapered portion 13 of the bulge portion 6 is different from that of the first embodiment. The difference will be described below.
  • the outer circumferential surface 15 of the tapered portion 13 of the bulge portion 6 has a concave surface portion 15 a which is formed in a concave surface shape so as to be recessed radially inward, and a convex surface portion 15 b which is formed in a convex surface shape on the one axial side with respect to the concave surface portion 15 a so as to project toward the radially outer side.
  • the concave surface portion 15 a is formed, for example, in a concave arc shape.
  • the convex surface portion 15 b is formed, for example, in a convex arc shape.
  • the concave surface portion 15 a is formed between another axial end and a middle portion on the one axial side of the outer circumferential surface 15 .
  • the convex surface portion 15 b is formed between the middle portion and one axial end of the outer circumferential surface 15 . Accordingly, in the outer circumferential surface 15 of the tapered portion 13 , the concave surface portion 15 a and the convex surface portion 15 b are formed so as to be continuous in the axial direction, and the convex surface portion 15 b is formed at a distal end portion of the tapered portion 13 .
  • the other components of the second embodiment are the same as those of the first embodiment, and thus are designated by the same reference signs, and the description thereof is omitted.
  • the concave surface portion 15 a is formed in the outer circumferential surface 15 of the tapered portion 13 in the bulge portion 6 of the inner ring 4 , when the diameter-increased portion 8 b of the tube 8 is pressed toward the other axial side by the union nut 3 (not shown) as shown in FIG. 7 , the inner circumferential surface of the tube 8 is less likely to come into contact with a bottom portion 15 al of the concave surface portion 15 a .
  • the axial range where the surface pressure is generated between the tapered portion 13 of the bulge portion 6 and the tube 8 is narrower than that in the conventional art, so that the surface pressure generated between the tapered portion 13 of the bulge portion 6 and the tube 8 can be made larger than that in the conventional art. Therefore, even if the tightening torque of the union nut 3 is not increased, the required surface pressure can be ensured between the bulge portion 6 of the inner ring 4 and the tube 8 . As a result, the chemical solution flowing through the fluid flow passage 4 a of the inner ring 4 can be inhibited from leaking from between the bulge portion 6 and the tube 8 to the outside.
  • the thickness in the radial direction of the distal end portion of the tapered portion 13 can be larger than that in the first embodiment. Accordingly, the strength of the distal end portion of the tapered portion 13 is increased, so that, even when the tapered portion 13 is pressed via the tube 8 by the union nut 3 , the distal end portion of the tapered portion 13 can be inhibited from significantly falling down toward the radially inner side as in the first embodiment (see FIG. 5 ). As a result, the flow of the chemical solution in the fluid flow passage 4 a of the inner ring 4 can be inhibited from being obstructed by the tapered portion 13 of the bulge portion 6 .
  • FIG. 8 is an enlarged axial cross-sectional view showing an area around a bulge portion 6 of an inner ring 4 in a pipe joint 1 according to a third embodiment of the present invention.
  • the shape of a tapered portion 13 of the bulge portion 6 is different from that of the first embodiment. The difference will be described below.
  • the tapered portion 13 of the bulge portion 6 is formed so as to be shorter in the axial direction than the tapered portion 13 of the bulge portion 6 in the first embodiment.
  • a flat surface 16 is formed at one axial end of the tapered portion 13 so as to extend in the radial direction.
  • the flat surface 16 extends from one axial end 15 c of an outer circumferential surface 15 of the tapered portion 13 toward the radially inner side, and is connected to one axial end of an inner circumferential surface 14 of the tapered portion 13 .
  • the outer circumferential surface 15 of the tapered portion 13 is formed in a convex surface shape (e.g., a convex arc shape) over the entire axial length thereof.
  • a diameter D of the one axial end 15 c of the outer circumferential surface 15 of the tapered portion 13 and an inner diameter d of a non-deformed portion 8 c of a tube 8 are set so as to satisfy a relationship of 1.0d ⁇ D ⁇ 1.4d.
  • the non-deformed portion 8 c is a portion, of the tube 8 , that does not become deformed even when the bulge portion 6 of the inner ring 4 is press-fitted into an end portion of the tube 8 .
  • the reason why D ⁇ 1.4d is satisfied is that, if the diameter D of the one axial end 15 c exceeds 1.4d, a pressing force is generated in the axial direction by a corner portion 3 c of a union nut 3 over the entirety of the flat surface 16 , and thus the tightening torque of the union nut 3 is increased.
  • the reason why 1.0d ⁇ D is satisfied is that, if the diameter D of the one axial end 15 c is less than 1.0d, the axial range where a surface pressure is generated between the tapered portion 13 of the bulge portion 6 and the tube 8 is longer, so that a required surface pressure cannot be ensured between the bulge portion 6 and the tube 8 .
  • the other components of the third embodiment are the same as those of the first embodiment, and thus are designated by the same reference signs, and the description thereof is omitted.
  • the flat surface 16 is formed at the one axial end of the tapered portion 13 , but a shape (e.g., a tapered surface or the like) other than a flat surface may be formed thereat.
  • the shape of the outer circumferential surface 15 of the tapered portion 13 is not limited to the convex surface shape, and may be formed, for example, as a flat surface shape as shown in FIG. 9 .
  • the diameter D of the one axial end 15 c of the outer circumferential surface 15 of the tapered portion 13 and the inner diameter d of the non-deformed portion 8 c of the tube 8 satisfy the relationship of 1.0d ⁇ D, even if the tightening torque of the union nut 3 is not increased, the required surface pressure can be ensured between the bulge portion 6 of the inner ring 4 and the tube 8 . As a result, the chemical solution flowing through the fluid flow passage 4 a of the inner ring 4 can be inhibited from leaking from between the bulge portion 6 and the tube 8 to the outside.
  • the pipe joint of the present invention can also be applied to the liquid crystal/organic EL field, the medical/pharmaceutical field, automotive-related fields, etc., in addition to a semiconductor manufacturing apparatus.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Joints That Cut Off Fluids, And Hose Joints (AREA)
  • Joints With Pressure Members (AREA)
  • Branch Pipes, Bends, And The Like (AREA)
US18/258,813 2021-02-18 2021-10-04 Pipe joint Pending US20240044425A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP2021-024153 2021-02-18
JP2021024153A JP2022126218A (ja) 2021-02-18 2021-02-18 管継手
PCT/JP2021/036665 WO2022176258A1 (ja) 2021-02-18 2021-10-04 管継手

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US20240044425A1 true US20240044425A1 (en) 2024-02-08

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US18/258,813 Pending US20240044425A1 (en) 2021-02-18 2021-10-04 Pipe joint

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US (1) US20240044425A1 (ja)
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