US20120216586A1 - High pressure fuel fittings - Google Patents
High pressure fuel fittings Download PDFInfo
- Publication number
- US20120216586A1 US20120216586A1 US13/469,861 US201213469861A US2012216586A1 US 20120216586 A1 US20120216586 A1 US 20120216586A1 US 201213469861 A US201213469861 A US 201213469861A US 2012216586 A1 US2012216586 A1 US 2012216586A1
- Authority
- US
- United States
- Prior art keywords
- conduit
- exterior surface
- nut
- shaped
- generally
- Prior art date
- Legal status (The legal status 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 status listed.)
- Abandoned
Links
- 239000000446 fuel Substances 0.000 title description 14
- 239000012530 fluid Substances 0.000 claims abstract description 30
- 239000002184 metal Substances 0.000 claims abstract description 11
- 229910052751 metal Inorganic materials 0.000 claims abstract description 11
- 238000004519 manufacturing process Methods 0.000 claims abstract description 3
- 238000000034 method Methods 0.000 claims description 7
- 239000011248 coating agent Substances 0.000 claims description 5
- 238000000576 coating method Methods 0.000 claims description 5
- RYGMFSIKBFXOCR-UHFFFAOYSA-N Copper Chemical compound [Cu] RYGMFSIKBFXOCR-UHFFFAOYSA-N 0.000 claims description 4
- 229910052802 copper Inorganic materials 0.000 claims description 4
- 239000010949 copper Substances 0.000 claims description 4
- 238000009713 electroplating Methods 0.000 claims description 2
- 230000003746 surface roughness Effects 0.000 claims description 2
- 238000007789 sealing Methods 0.000 description 16
- 238000010276 construction Methods 0.000 description 10
- 238000004891 communication Methods 0.000 description 3
- 238000001514 detection method Methods 0.000 description 3
- 230000009467 reduction Effects 0.000 description 3
- 229910000831 Steel Inorganic materials 0.000 description 2
- 238000005452 bending Methods 0.000 description 2
- 238000006243 chemical reaction Methods 0.000 description 2
- 230000008878 coupling Effects 0.000 description 2
- 238000010168 coupling process Methods 0.000 description 2
- 238000005859 coupling reaction Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 239000010959 steel Substances 0.000 description 2
- 230000004323 axial length Effects 0.000 description 1
- 238000005219 brazing Methods 0.000 description 1
- 230000000295 complement effect Effects 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 230000007246 mechanism Effects 0.000 description 1
- 230000008569 process Effects 0.000 description 1
Images
Classifications
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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
- F16L27/00—Adjustable joints, Joints allowing movement
- F16L27/02—Universal joints, i.e. with mechanical connection allowing angular movement or adjustment of the axes of the parts in any direction
- F16L27/04—Universal joints, i.e. with mechanical connection allowing angular movement or adjustment of the axes of the parts in any direction with partly spherical engaging surfaces
- F16L27/047—Universal joints, i.e. with mechanical connection allowing angular movement or adjustment of the axes of the parts in any direction with partly spherical engaging surfaces held in place by a screwed member having an internal spherical surface
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M55/00—Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
- F02M55/004—Joints; Sealings
- F02M55/005—Joints; Sealings for high pressure conduits, e.g. connected to pump outlet or to injector inlet
-
- 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
- F16L19/02—Pipe ends provided with collars or flanges, integral with the pipe or not, pressed together by a screwed member
- F16L19/025—Pipe ends provided with collars or flanges, integral with the pipe or not, pressed together by a screwed member the pipe ends having integral collars or flanges
-
- 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
- F16L27/00—Adjustable joints, Joints allowing movement
- F16L27/02—Universal joints, i.e. with mechanical connection allowing angular movement or adjustment of the axes of the parts in any direction
- F16L27/04—Universal joints, i.e. with mechanical connection allowing angular movement or adjustment of the axes of the parts in any direction with partly spherical engaging surfaces
- F16L27/06—Universal joints, i.e. with mechanical connection allowing angular movement or adjustment of the axes of the parts in any direction with partly spherical engaging surfaces with special sealing means between the engaging surfaces
- F16L27/073—Universal joints, i.e. with mechanical connection allowing angular movement or adjustment of the axes of the parts in any direction with partly spherical engaging surfaces with special sealing means between the engaging surfaces one of the cooperating surfaces forming the sealing means
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10S285/00—Pipe joints or couplings
- Y10S285/924—Vented
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T29/00—Metal working
- Y10T29/49—Method of mechanical manufacture
- Y10T29/49428—Gas and water specific plumbing component making
- Y10T29/4943—Plumbing fixture making
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T29/00—Metal working
- Y10T29/49—Method of mechanical manufacture
- Y10T29/49826—Assembling or joining
Definitions
- the present invention relates to fittings for high pressure fuel lines, particularly fittings that make fluid seals with metal-to-metal contact and allow for a limited amount of axial misalignment between first and second fuel conduits coupled by the fitting.
- the invention provides a fitting for making a metal-to-metal fluid seal between a first conduit and a second conduit, the fitting including a first conduit defining a first fluid passage, the first conduit having a generally spherical-shaped exterior surface at a first end thereof.
- a second conduit defines a second fluid passage, the second conduit having a generally conical-shaped interior surface for receiving the generally spherical-shaped exterior surface of the first conduit.
- the second conduit includes a threaded exterior surface.
- a nut is engaged with the threaded exterior surface of the second conduit, tightening of the nut on the threaded exterior surface urging the first and second conduits axially together to apply increasing pressure between the generally spherical-shaped exterior surface and the generally conical-shaped interior surface.
- a ring is positioned between the first conduit and the nut, the ring having a radially facing outer surface that is radially spaced a distance from a radially facing inner surface of the nut.
- the invention provides a fitting for making a metal-to-metal fluid seal between a first conduit and a second conduit, the fitting including a first conduit defining a first fluid passage, the first conduit having a generally spherical-shaped exterior surface at a first end thereof.
- a second conduit defines a second fluid passage, the second conduit having a generally conical-shaped interior surface for receiving the generally spherical-shaped exterior surface of the first conduit.
- the second conduit includes a threaded exterior surface.
- a nut is engaged with the threaded exterior surface of the second conduit, tightening of the nut on the threaded exterior surface urging the first and second conduits axially together to apply increasing pressure between the generally spherical-shaped exterior surface and the generally conical-shaped interior surface.
- the generally spherical-shaped exterior of the first conduit includes a first portion contacting the generally conical-shaped surface and a second portion to which axial load from the nut is transferred, the first portion having a smaller radius than the second portion.
- the invention provides a method of manufacturing a ball and cone fluid fitting.
- a first conduit is provided with a generally spherical-shaped exterior surface.
- a second conduit is provided with a generally conical-shaped interior surface.
- the generally conical-shaped surface is coined with a master ball to create a seating surface for the generally spherical-shaped exterior surface of the first conduit.
- At least a portion of the generally spherical-shaped exterior surface is coated with a softer metal.
- the invention provides a fitting for making a metal-to-metal fluid seal between a first conduit and a second conduit, the fitting including a first conduit formed with a generally spherical-shaped exterior surface that includes a first portion and a second portion axially spaced from each other.
- a second conduit is formed with a generally conical-shaped interior surface that is engageable with the first portion of the generally spherical-shaped exterior surface to fluidly seal the first and second conduits.
- a nut is threaded into engagement with the second conduit and configured to apply pressure to the second portion of the generally spherical-shaped exterior surface to axially urge the first conduit and the second conduit together.
- a ring is positioned between the nut and the second portion of the generally spherical-shaped exterior surface, the ring providing a lower net coefficient of friction between the nut and the first conduit during rotation of the nut relative to the first conduit compared to direct contact between the nut and the first conduit.
- FIG. 1 is a cross-sectional view of a fitting according to one embodiment of the present invention.
- FIG. 2 is a cross-sectional view of a fitting according to another embodiment of the present invention.
- FIG. 3 is a cross-sectional view of a fitting according to yet another embodiment of the present invention.
- FIG. 4 is a perspective view of a ring configured to be used with the fitting of FIG. 3 .
- FIG. 5 is a perspective view of an alternate ring configured to be used with the fitting of FIG. 3 .
- FIG. 1 illustrates a fitting 20 including a first conduit 24 defining a first generally axial fluid passage 26 and a second conduit 28 defining a second generally axial fluid passage 30 .
- the first and second conduits 24 , 28 are coupled as described in further detail below to establish fluid communication between the respective fluid passages 26 , 30 .
- the fitting 20 is generally described as a ball and cone type fitting, which can be used in a high pressure fuel system in which the first conduit 24 and the second conduit 28 may or may not be in axial alignment.
- the first and second conduits 24 , 28 are in direct contact with each other to establish a fluid seal therebetween via metal-to-metal contact without any intermediate sealing members (e.g., elastomeric rings).
- the first conduit 24 includes a generally spherical-shaped exterior surface 32 that is received by a generally conical-shaped interior surface 36 of the second conduit 28 .
- the interface between the exterior surface 32 of the first conduit 24 and the interior surface 36 of the second conduit 28 enables the first conduit 24 and the second conduit 28 to be coupled in variable different relative orientations.
- the second conduit 28 includes a threaded exterior surface 40 .
- a nut 44 at least partially encloses the first conduit 24 and is threaded onto the second conduit 28 . Tightening of the nut 44 on the threaded exterior surface 40 urges the first and second conduits 24 , 28 axially together to apply increasing pressure between the generally spherical-shaped exterior surface 32 and the generally conical-shaped interior surface 36 . Greater torque applied to the nut 44 generally results in a higher axial sealing force and sealing pressure between the exterior surface 32 of the first conduit 24 and the interior surface 36 of the second conduit 28 .
- the generally spherical-shaped exterior surface 32 of the first conduit 24 constitutes a “ball portion” of the first conduit 24 and includes a first portion 32 A and a second portion 32 B.
- the first portion 32 A contacts the generally conical-shaped interior surface 36 .
- Axial load from the nut 44 is received by the second portion 32 B.
- the first conduit 24 also includes a generally cylindrical stem portion 48 extending generally axially from the ball portion.
- the end of a fuel line 50 is at least partially received and supported by the stem portion 48 .
- the first portion 32 A has a radius R 1 that is smaller than a radius R 2 of the second portion 32 B. In the illustrated construction, the first and second portions 32 A, 32 B have a common center point.
- the contact between the first portion 32 A and the interior surface 36 of the second conduit 28 is generally line-type contact in a ring shape having a diameter D 1 as shown in FIG. 1 .
- the second portion 32 B of the exterior surface 32 also engages in generally line-type contact in a ring shape through which axial load from the nut 44 is applied to the first conduit 24 .
- the diameter D 2 of the contact ring around the second portion 32 B is larger than the diameter D 1 of the contact ring around the first portion 32 A.
- a ring 60 is disposed between the nut 44 and the first conduit 24 to transfer load therebetween.
- the ring 60 is substantially coaxial with both the nut 44 and the first conduit 24 .
- the ring 60 is a tapered ring having a tapered interior surface 62 and a substantially flat radially facing exterior surface 64 .
- the ring 60 may be constructed of high strength steel.
- the exterior surface 64 of the ring 60 is radially spaced a distance from a radially facing inner surface 68 of the nut 44 .
- the ring 60 further includes an axially facing surface 70 contacting an internal axially facing surface 72 of the nut 44 .
- the ring load includes a normal component directed perpendicular to the tapered interior surface 62 at any given circumferential location and frictional component directed parallel to the tapered interior surface 62 at any given circumferential location.
- Axial loading of the ring 60 by the nut 44 results in a reaction force exerted on the tapered interior surface 62 of the ring 60 from the exterior surface 32 of the first conduit 24 that has a substantial component acting radially outward.
- the radially exterior surface 64 of the ring 60 is spaced from the radial surface 68 of the nut 44 , the radially outward reaction force on the ring 60 is borne by the ring 60 . Substantially no radial loads are transferred between the nut 44 and the ring 60 . Thus, the nut 44 is not subjected to any radially outward loading when the nut 44 is tightened onto the second conduit 28 . If applied, such loads act to try to split open the nut 44 , which can occur depending upon material strength and the amount of torque applied. The ring 60 prevents any splitting-apart type loading of the nut 44 .
- the fitting 20 may be further provided with a dedicated “leak path” for simplification of leak detection.
- the leak path does not promote leakage from inside the fluid passages 26 , 30 but rather, is configured to direct fluid that is inside the fitting 20 (e.g., inside the nut 44 ) but outside the first and second conduits 24 , 28 and the associated fluid passages 26 , 30 to a predetermined location in the event that a leak does exist between the exterior surface 32 of the first conduit 24 and the interior surface 36 of the second conduit 28 .
- the ring 60 includes a recess or groove 76 formed adjacent the axially facing surface 70 .
- the groove 76 allows fluid to flow from a location between the ring 60 and the nut 44 to a location outside of the fitting 20 . Therefore, leak detection can be performed by sensing for the leak at a single, known location of the fitting 20 , which makes leak detection quicker and less susceptible to error. In a fuel system for example, a small leak may result in only fuel vapor, and not liquid, escaping the fitting 20 , which may be difficult to detect if the potential location of the vapor discharge is not known.
- a further feature of the ring 60 is that it may enable a reduction in friction and correspondingly less torque required to be applied to the nut 44 to seal the first and second conduits 24 , 28 to each other.
- the net coefficient of friction that exists in the fitting 20 between the nut 44 and the first conduit 24 is influenced by the respective interfaces between the ring 60 and both the nut 44 and the first conduit 24 .
- the nut contacts the first conduit directly.
- the ring 60 is configured to offer a lower net coefficient of friction between the nut 44 and the first conduit 24 , compared to direct contact between the nut 44 and the first conduit 24 .
- the effect of the reduced friction coefficient is an actual reduction in friction when the nut 44 is being tightened onto the second conduit 28 . Therefore, the torque required to be applied to the nut 44 to achieve a particular axial sealing force is reduced. Alternately, a greater axial sealing force can be achieved with a given amount of torque applied to the nut 44 .
- FIG. 2 illustrates a fitting 120 including a first conduit 124 defining a first generally axial fluid passage 126 and a second conduit 128 defining a second generally axial fluid passage 130 .
- the first and second conduits 124 , 128 are coupled as described in further detail below to establish fluid communication between the respective fluid passages 126 , 130 .
- the fitting 120 is generally described as a ball and cone type fitting, which can be used in a high pressure fuel system in which the first conduit 124 and the second conduit 128 may or may not be in axial alignment.
- the first and second conduits 124 , 128 are in direct contact with each other to establish a fluid seal therebetween via metal-to-metal contact without any intermediate sealing members (e.g., elastomeric rings).
- the first conduit 124 includes a generally spherical-shaped exterior surface 132 that is received by a generally conical-shaped interior surface 136 of the second conduit 128 .
- the interface between the exterior surface 132 of the first conduit 124 and the interior surface 136 of the second conduit 128 enables the first conduit 124 and the second conduit 128 to be coupled in variable different relative orientations.
- the second conduit 128 of FIG. 2 includes a threaded exterior surface 140 .
- a nut 144 at least partially encloses the first conduit 124 and is threaded onto the second conduit 128 . Tightening of the nut 144 on the threaded exterior surface 140 urges the first and second conduits 124 , 128 axially together to apply increasing pressure between the generally spherical-shaped exterior surface 132 and the generally conical-shaped interior surface 136 in the same way as the nut 44 of the fitting 20 of FIG. 1 .
- the first conduit 124 of FIG. 2 is formed with the generally spherical-shaped exterior surface 132 having a single, constant radius.
- the first conduit 124 includes a stem portion 124 A and a ball portion 124 B.
- the stem portion 124 A is a tubular fuel line, but it may alternately be configured to receive and support a tubular fuel line.
- the stem portion 124 A and the ball portion 124 B can be joined together by a copper braze or other suitable means for physically and sealingly connecting them together.
- the stem portion 124 A and the ball portion 124 B are manufactured or prefabricated separately from each other, the ball portion 124 B being prefabricated without any portion protruding axially beyond the extent of the generally spherical-shaped surface 132 (e.g., no integrated stem portion).
- the ball portion 124 B need not be manufactured on a lathe and can be manufactured from spherical stock rather than cylindrical stock. This allows the exterior surface 132 , which is used for sealing, to be manufactured with a better surface finish as discussed in further detail below.
- the ball portion 124 B is manufactured from a ball bearing.
- the ball bearing can have a surface finish about 50 times better than a lathe-produced ball portion and a roundness about 25 times better.
- the diameter tolerance for the ball bearing type ball portion 124 B can be about 20 times better than a lathe-produced ball portion.
- the prefabricated ball portion 124 B can have a surface finish of about 0.05 micron, a roundness of about 0.0006 millimeter, and a diameter tolerance of about 0.0012 millimeter.
- the ball portion 124 B also has a full-length opening 154 such that the stem portion 124 A can extend to a common terminal end 158 . Conventionally, the end of a fuel line is abutted against an internal chamfer in the ball portion, which can hinder the escape of air necessary for the brazing process.
- the location where the tapered surface 180 of the nut 144 contacts the exterior surface 132 can be moved axially further toward the end of the ball portion 124 B.
- the result is that the contact angle (i.e., the angle of the tapered surface 180 ) can be substantially increased over that of a conventional fitting.
- the angle of the tapered surface 180 can be about 80 degrees, whereas a conventional fitting has about a 60 degree contact angle. Therefore, the torque required to be applied to the nut 144 to achieve a particular axial sealing force between the first and second conduits 124 , 128 is reduced.
- the normal force between the tapered surface 180 and the exterior surface 132 to achieve a particular axial sealing force is also reduced as the direction of the normal force is closer to the axial direction.
- the normal force may be less than 80 percent (e.g., about 77.8 percent) of the normal force required for a 60 degree contact angle. This reduces the severity of the nut 144 galling into the ball portion 124 B. Alternately, if the full amount of torque is applied to the nut 144 , a greater axial sealing force can be achieved.
- the lack of an integral axially-extending stem portion reduces the axial length of the illustrated ball portion 124 B, reducing the potential bending load on the stem portion 124 A.
- the possible fatigue failure is reduced by using the ball bearing type ball portion 124 B compared to a ball-stem component, which can apply a high bending load to a fuel line at the terminal end of the stem portion.
- a ring may be positioned between the nut 144 and the exterior surface 132 of the first conduit 124 similar to the ring 60 of the fitting 20 of FIG. 1 .
- the fitting 120 of FIG. 2 also provides an alternate mechanism of reducing the “splitting-apart” type loading by reducing the amount of radial loading on the nut 144 for a given torque applied between the nut 144 and the first conduit 124 .
- Additional improvements in the fitting 120 of FIG. 2 can include coining the generally conical-shaped interior surface 136 (e.g., with a master ball) to create a seating surface for the generally spherical-shaped exterior surface 132 of the first conduit 124 .
- the master ball is a high quality ball bearing having the shape of the generally spherical-shaped exterior surface 132 , but having tighter tolerances and a better surface finish.
- the master ball is adapted to be part of the hammer of a coining press.
- the coining operation creates a very small spherical-shaped impression in the generally conical-shaped interior surface 136 , into which the ball portion 124 B can be seated without a great amount of torque applied to the nut 144 during final assembly of the fitting 120 .
- at least a portion of the generally spherical-shaped exterior surface 132 can be coated with a softer metal (e.g., copper electroplating), which can reduce the surface roughness of the coated portion by about 50 percent.
- the coating may have a thickness less than about 0.001 inch, such as a thickness of about 0.0005 inch.
- FIG. 3 illustrates a fitting 220 including a first conduit 224 defining a first generally axial fluid passage 226 and a second conduit 228 defining a second generally axial fluid passage 230 .
- the first and second conduits 224 , 228 are coupled as described in further detail below to establish fluid communication between the respective fluid passages 226 , 230 .
- the fitting 220 is generally described as a ball and cone type fitting, which can be used in a high pressure fuel system in which the first conduit 224 and the second conduit 228 may or may not be in axial alignment.
- the first and second conduits 224 , 228 are in direct contact with each other to establish a fluid seal therebetween via metal-to-metal contact without any intermediate sealing members (e.g., elastomeric rings).
- the first conduit 224 includes a generally spherical-shaped exterior surface 232 that is received by a generally conical-shaped interior surface 236 of the second conduit 228 .
- the interface between the exterior surface 232 of the first conduit 224 and the interior surface 236 of the second conduit 228 enables the first conduit 224 and the second conduit 228 to be coupled in variable different relative orientations.
- the second conduit 228 includes a threaded exterior surface 240 .
- a nut 244 at least partially encloses the first conduit 224 and is threaded onto the second conduit 228 . Tightening of the nut 244 on the threaded exterior surface 240 urges the first and second conduits 224 , 228 axially together to apply increasing pressure between the generally spherical-shaped exterior surface 232 and the generally conical-shaped interior surface 236 . Greater torque applied to the nut 244 generally results in a higher axial sealing force and sealing pressure between the exterior surface 232 of the first conduit 224 and the interior surface 236 of the second conduit 228 .
- the generally spherical-shaped exterior surface 232 of the first conduit 224 constitutes a “ball portion” of the first conduit 224 , which is compressed between the nut 244 and the second conduit 228 .
- the first conduit 224 also includes a generally cylindrical stem portion 248 extending generally axially from the ball portion. The end of a fuel line 250 is at least partially received and supported by the stem portion 248 .
- a ring 260 is disposed between the nut 244 and the first conduit 224 to transfer load therebetween.
- the ring 260 is substantially coaxial with both the nut 244 and the first conduit 224 .
- the ring 260 is a washer having a conical shape to complement the tapered or conical interior surface 272 of the nut 244 .
- the ring 260 may be constructed of copper, while the nut 244 may be constructed of steel.
- the net coefficient of friction that exists in the fitting 220 between the nut 244 and the first conduit 224 is influenced by the respective interfaces between the ring 260 and both the nut 244 and the first conduit 224 .
- the nut contacts the first conduit directly.
- the ring 260 is configured to offer a lower net coefficient of friction between the nut 244 and the first conduit 224 , compared to direct contact between the nut 244 and the first conduit 224 .
- the effect of the reduced friction coefficient is an actual reduction in friction when the nut 244 is being tightened onto the second conduit 228 . Therefore, the torque required to be applied to the nut 244 to achieve a particular axial sealing force is reduced.
- the ring 260 can be prefabricated as a flat washer ( FIG. 4 ) and deformed to at least partially conform to the shape of the conical interior surface 272 of the nut 244 .
- the ring 260 can be prefabricated in a conical shape ( FIG. 5 ) that complements the interior surface 272 of the nut 244 .
- the invention provides various improvements over conventional ball and cone type fittings. Although illustrated and described as three distinct constructions, the features of the invention may be combined in different combinations than those shown in the figures and described above. Various features and advantages of the invention are set forth in the following claims.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Joints With Pressure Members (AREA)
- Taps Or Cocks (AREA)
- Joints Allowing Movement (AREA)
Abstract
A method of manufacturing a ball and cone fluid fitting includes providing a first conduit with a generally spherical-shaped exterior surface, and providing a second conduit with a generally conical-shaped interior surface. The generally conical-shaped surface is coined with a master ball to create a seating surface for the generally spherical-shaped exterior surface of the first conduit. At least a portion of the generally spherical-shaped exterior surface is coated with a softer metal.
Description
- This application claims priority as a divisional to U.S. patent application Ser. No. 12/365,218, filed Feb. 4, 2009, now U.S. Pat. No. ______, the entire contents of which are hereby incorporated by reference.
- The present invention relates to fittings for high pressure fuel lines, particularly fittings that make fluid seals with metal-to-metal contact and allow for a limited amount of axial misalignment between first and second fuel conduits coupled by the fitting.
- In one embodiment, the invention provides a fitting for making a metal-to-metal fluid seal between a first conduit and a second conduit, the fitting including a first conduit defining a first fluid passage, the first conduit having a generally spherical-shaped exterior surface at a first end thereof. A second conduit defines a second fluid passage, the second conduit having a generally conical-shaped interior surface for receiving the generally spherical-shaped exterior surface of the first conduit. The second conduit includes a threaded exterior surface. A nut is engaged with the threaded exterior surface of the second conduit, tightening of the nut on the threaded exterior surface urging the first and second conduits axially together to apply increasing pressure between the generally spherical-shaped exterior surface and the generally conical-shaped interior surface. A ring is positioned between the first conduit and the nut, the ring having a radially facing outer surface that is radially spaced a distance from a radially facing inner surface of the nut.
- In another embodiment, the invention provides a fitting for making a metal-to-metal fluid seal between a first conduit and a second conduit, the fitting including a first conduit defining a first fluid passage, the first conduit having a generally spherical-shaped exterior surface at a first end thereof. A second conduit defines a second fluid passage, the second conduit having a generally conical-shaped interior surface for receiving the generally spherical-shaped exterior surface of the first conduit. The second conduit includes a threaded exterior surface. A nut is engaged with the threaded exterior surface of the second conduit, tightening of the nut on the threaded exterior surface urging the first and second conduits axially together to apply increasing pressure between the generally spherical-shaped exterior surface and the generally conical-shaped interior surface. The generally spherical-shaped exterior of the first conduit includes a first portion contacting the generally conical-shaped surface and a second portion to which axial load from the nut is transferred, the first portion having a smaller radius than the second portion.
- In another embodiment, the invention provides a method of manufacturing a ball and cone fluid fitting. A first conduit is provided with a generally spherical-shaped exterior surface. A second conduit is provided with a generally conical-shaped interior surface. The generally conical-shaped surface is coined with a master ball to create a seating surface for the generally spherical-shaped exterior surface of the first conduit. At least a portion of the generally spherical-shaped exterior surface is coated with a softer metal.
- In another embodiment, the invention provides a fitting for making a metal-to-metal fluid seal between a first conduit and a second conduit, the fitting including a first conduit formed with a generally spherical-shaped exterior surface that includes a first portion and a second portion axially spaced from each other. A second conduit is formed with a generally conical-shaped interior surface that is engageable with the first portion of the generally spherical-shaped exterior surface to fluidly seal the first and second conduits. A nut is threaded into engagement with the second conduit and configured to apply pressure to the second portion of the generally spherical-shaped exterior surface to axially urge the first conduit and the second conduit together. A ring is positioned between the nut and the second portion of the generally spherical-shaped exterior surface, the ring providing a lower net coefficient of friction between the nut and the first conduit during rotation of the nut relative to the first conduit compared to direct contact between the nut and the first conduit.
- Other aspects of the invention will become apparent by consideration of the detailed description and accompanying drawings.
-
FIG. 1 is a cross-sectional view of a fitting according to one embodiment of the present invention. -
FIG. 2 is a cross-sectional view of a fitting according to another embodiment of the present invention. -
FIG. 3 is a cross-sectional view of a fitting according to yet another embodiment of the present invention. -
FIG. 4 is a perspective view of a ring configured to be used with the fitting ofFIG. 3 . -
FIG. 5 is a perspective view of an alternate ring configured to be used with the fitting ofFIG. 3 . - Before any embodiments of the invention are explained in detail, it is to be understood that the invention is not limited in its application to the details of construction and the arrangement of components set forth in the following description or illustrated in the following drawings. The invention is capable of other embodiments and of being practiced or of being carried out in various ways. Also, it is to be understood that the phraseology and terminology used herein is for the purpose of description and should not be regarded as limiting. The use of “including,” “comprising,” or “having” and variations thereof herein is meant to encompass the items listed thereafter and equivalents thereof as well as additional items. Unless specified or limited otherwise, the terms “mounted,” “connected,” “supported,” and “coupled” and variations thereof are used broadly and encompass both direct and indirect mountings, connections, supports, and couplings. Further, “connected” and “coupled” are not restricted to physical or mechanical connections or couplings.
-
FIG. 1 illustrates afitting 20 including afirst conduit 24 defining a first generallyaxial fluid passage 26 and asecond conduit 28 defining a second generallyaxial fluid passage 30. The first andsecond conduits respective fluid passages fitting 20 is generally described as a ball and cone type fitting, which can be used in a high pressure fuel system in which thefirst conduit 24 and thesecond conduit 28 may or may not be in axial alignment. The first andsecond conduits first conduit 24 includes a generally spherical-shapedexterior surface 32 that is received by a generally conical-shapedinterior surface 36 of thesecond conduit 28. The interface between theexterior surface 32 of thefirst conduit 24 and theinterior surface 36 of thesecond conduit 28 enables thefirst conduit 24 and thesecond conduit 28 to be coupled in variable different relative orientations. - The
second conduit 28 includes a threadedexterior surface 40. Anut 44 at least partially encloses thefirst conduit 24 and is threaded onto thesecond conduit 28. Tightening of thenut 44 on the threadedexterior surface 40 urges the first andsecond conduits exterior surface 32 and the generally conical-shapedinterior surface 36. Greater torque applied to thenut 44 generally results in a higher axial sealing force and sealing pressure between theexterior surface 32 of thefirst conduit 24 and theinterior surface 36 of thesecond conduit 28. - The generally spherical-shaped
exterior surface 32 of thefirst conduit 24 constitutes a “ball portion” of thefirst conduit 24 and includes afirst portion 32A and asecond portion 32B. Thefirst portion 32A contacts the generally conical-shapedinterior surface 36. Axial load from thenut 44 is received by thesecond portion 32B. In addition to the ball portion, thefirst conduit 24 also includes a generallycylindrical stem portion 48 extending generally axially from the ball portion. The end of afuel line 50 is at least partially received and supported by thestem portion 48. Thefirst portion 32A has a radius R1 that is smaller than a radius R2 of thesecond portion 32B. In the illustrated construction, the first andsecond portions - The contact between the
first portion 32A and theinterior surface 36 of thesecond conduit 28 is generally line-type contact in a ring shape having a diameter D1 as shown inFIG. 1 . Thesecond portion 32B of theexterior surface 32 also engages in generally line-type contact in a ring shape through which axial load from thenut 44 is applied to thefirst conduit 24. The diameter D2 of the contact ring around thesecond portion 32B is larger than the diameter D1 of the contact ring around thefirst portion 32A. Thus, for any given axial load, a greater pressure is exerted at the sealing interface between thefirst conduit 24 and thesecond conduit 28 compared to what is exerted between thenut 44 and thefirst conduit 24. - As shown in
FIG. 1 , aring 60 is disposed between thenut 44 and thefirst conduit 24 to transfer load therebetween. Thering 60 is substantially coaxial with both thenut 44 and thefirst conduit 24. In the illustrated construction, thering 60 is a tapered ring having a taperedinterior surface 62 and a substantially flat radially facingexterior surface 64. Thering 60 may be constructed of high strength steel. Theexterior surface 64 of thering 60 is radially spaced a distance from a radially facinginner surface 68 of thenut 44. Thering 60 further includes anaxially facing surface 70 contacting an internalaxially facing surface 72 of thenut 44. - As the
nut 44 is tightened onto thesecond conduit 28, a ring load is generated at the interface between thering 60 and thefirst conduit 24. The ring load includes a normal component directed perpendicular to the taperedinterior surface 62 at any given circumferential location and frictional component directed parallel to the taperedinterior surface 62 at any given circumferential location. Axial loading of thering 60 by thenut 44 results in a reaction force exerted on the taperedinterior surface 62 of thering 60 from theexterior surface 32 of thefirst conduit 24 that has a substantial component acting radially outward. Because theradially exterior surface 64 of thering 60 is spaced from theradial surface 68 of thenut 44, the radially outward reaction force on thering 60 is borne by thering 60. Substantially no radial loads are transferred between thenut 44 and thering 60. Thus, thenut 44 is not subjected to any radially outward loading when thenut 44 is tightened onto thesecond conduit 28. If applied, such loads act to try to split open thenut 44, which can occur depending upon material strength and the amount of torque applied. Thering 60 prevents any splitting-apart type loading of thenut 44. - As illustrated in
FIG. 1 , the fitting 20 may be further provided with a dedicated “leak path” for simplification of leak detection. The leak path does not promote leakage from inside thefluid passages second conduits fluid passages exterior surface 32 of thefirst conduit 24 and theinterior surface 36 of thesecond conduit 28. In the illustrated embodiment, thering 60 includes a recess or groove 76 formed adjacent theaxially facing surface 70. Thegroove 76 allows fluid to flow from a location between thering 60 and thenut 44 to a location outside of the fitting 20. Therefore, leak detection can be performed by sensing for the leak at a single, known location of the fitting 20, which makes leak detection quicker and less susceptible to error. In a fuel system for example, a small leak may result in only fuel vapor, and not liquid, escaping the fitting 20, which may be difficult to detect if the potential location of the vapor discharge is not known. - A further feature of the
ring 60 is that it may enable a reduction in friction and correspondingly less torque required to be applied to thenut 44 to seal the first andsecond conduits nut 44 and thefirst conduit 24 is influenced by the respective interfaces between thering 60 and both thenut 44 and thefirst conduit 24. In a conventional fitting, the nut contacts the first conduit directly. In the illustrated construction, thering 60 is configured to offer a lower net coefficient of friction between thenut 44 and thefirst conduit 24, compared to direct contact between thenut 44 and thefirst conduit 24. The effect of the reduced friction coefficient is an actual reduction in friction when thenut 44 is being tightened onto thesecond conduit 28. Therefore, the torque required to be applied to thenut 44 to achieve a particular axial sealing force is reduced. Alternately, a greater axial sealing force can be achieved with a given amount of torque applied to thenut 44. -
FIG. 2 illustrates a fitting 120 including a first conduit 124 defining a first generallyaxial fluid passage 126 and asecond conduit 128 defining a second generallyaxial fluid passage 130. The first andsecond conduits 124, 128 are coupled as described in further detail below to establish fluid communication between the respectivefluid passages second conduit 128 may or may not be in axial alignment. The first andsecond conduits 124, 128 are in direct contact with each other to establish a fluid seal therebetween via metal-to-metal contact without any intermediate sealing members (e.g., elastomeric rings). Specifically, the first conduit 124 includes a generally spherical-shapedexterior surface 132 that is received by a generally conical-shapedinterior surface 136 of thesecond conduit 128. The interface between theexterior surface 132 of the first conduit 124 and theinterior surface 136 of thesecond conduit 128 enables the first conduit 124 and thesecond conduit 128 to be coupled in variable different relative orientations. - Similar to the fitting 20 of
FIG. 1 , thesecond conduit 128 ofFIG. 2 includes a threadedexterior surface 140. Anut 144 at least partially encloses the first conduit 124 and is threaded onto thesecond conduit 128. Tightening of thenut 144 on the threadedexterior surface 140 urges the first andsecond conduits 124, 128 axially together to apply increasing pressure between the generally spherical-shapedexterior surface 132 and the generally conical-shapedinterior surface 136 in the same way as thenut 44 of the fitting 20 ofFIG. 1 . Unlike the fitting 20 ofFIG. 1 , the first conduit 124 ofFIG. 2 is formed with the generally spherical-shapedexterior surface 132 having a single, constant radius. - Furthermore, the first conduit 124 includes a
stem portion 124A and a ball portion 124B. In the illustrated construction, thestem portion 124A is a tubular fuel line, but it may alternately be configured to receive and support a tubular fuel line. Thestem portion 124A and the ball portion 124B can be joined together by a copper braze or other suitable means for physically and sealingly connecting them together. Thestem portion 124A and the ball portion 124B are manufactured or prefabricated separately from each other, the ball portion 124B being prefabricated without any portion protruding axially beyond the extent of the generally spherical-shaped surface 132 (e.g., no integrated stem portion). Thus, the ball portion 124B need not be manufactured on a lathe and can be manufactured from spherical stock rather than cylindrical stock. This allows theexterior surface 132, which is used for sealing, to be manufactured with a better surface finish as discussed in further detail below. - In one construction, the ball portion 124B is manufactured from a ball bearing. The ball bearing can have a surface finish about 50 times better than a lathe-produced ball portion and a roundness about 25 times better. Furthermore, the diameter tolerance for the ball bearing type ball portion 124B can be about 20 times better than a lathe-produced ball portion. In one construction, the prefabricated ball portion 124B can have a surface finish of about 0.05 micron, a roundness of about 0.0006 millimeter, and a diameter tolerance of about 0.0012 millimeter. The ball portion 124B also has a full-
length opening 154 such that thestem portion 124A can extend to a commonterminal end 158. Conventionally, the end of a fuel line is abutted against an internal chamfer in the ball portion, which can hinder the escape of air necessary for the brazing process. - Because the ball portion 124B is not formed with an integral axially-extending stem portion, the location where the tapered
surface 180 of thenut 144 contacts theexterior surface 132 can be moved axially further toward the end of the ball portion 124B. The result is that the contact angle (i.e., the angle of the tapered surface 180) can be substantially increased over that of a conventional fitting. For example, the angle of the taperedsurface 180 can be about 80 degrees, whereas a conventional fitting has about a 60 degree contact angle. Therefore, the torque required to be applied to thenut 144 to achieve a particular axial sealing force between the first andsecond conduits 124, 128 is reduced. The normal force between thetapered surface 180 and theexterior surface 132 to achieve a particular axial sealing force is also reduced as the direction of the normal force is closer to the axial direction. For example, the normal force may be less than 80 percent (e.g., about 77.8 percent) of the normal force required for a 60 degree contact angle. This reduces the severity of thenut 144 galling into the ball portion 124B. Alternately, if the full amount of torque is applied to thenut 144, a greater axial sealing force can be achieved. Furthermore, the lack of an integral axially-extending stem portion reduces the axial length of the illustrated ball portion 124B, reducing the potential bending load on thestem portion 124A. Thus, the possible fatigue failure is reduced by using the ball bearing type ball portion 124B compared to a ball-stem component, which can apply a high bending load to a fuel line at the terminal end of the stem portion. - Although not illustrated, a ring may be positioned between the
nut 144 and theexterior surface 132 of the first conduit 124 similar to thering 60 of the fitting 20 ofFIG. 1 . However, the fitting 120 ofFIG. 2 also provides an alternate mechanism of reducing the “splitting-apart” type loading by reducing the amount of radial loading on thenut 144 for a given torque applied between thenut 144 and the first conduit 124. - Additional improvements in the fitting 120 of
FIG. 2 can include coining the generally conical-shaped interior surface 136 (e.g., with a master ball) to create a seating surface for the generally spherical-shapedexterior surface 132 of the first conduit 124. The master ball is a high quality ball bearing having the shape of the generally spherical-shapedexterior surface 132, but having tighter tolerances and a better surface finish. The master ball is adapted to be part of the hammer of a coining press. The coining operation creates a very small spherical-shaped impression in the generally conical-shapedinterior surface 136, into which the ball portion 124B can be seated without a great amount of torque applied to thenut 144 during final assembly of the fitting 120. Furthermore, at least a portion of the generally spherical-shapedexterior surface 132 can be coated with a softer metal (e.g., copper electroplating), which can reduce the surface roughness of the coated portion by about 50 percent. The coating may have a thickness less than about 0.001 inch, such as a thickness of about 0.0005 inch. -
FIG. 3 illustrates a fitting 220 including afirst conduit 224 defining a first generallyaxial fluid passage 226 and asecond conduit 228 defining a second generallyaxial fluid passage 230. The first andsecond conduits fluid passages first conduit 224 and thesecond conduit 228 may or may not be in axial alignment. The first andsecond conduits first conduit 224 includes a generally spherical-shapedexterior surface 232 that is received by a generally conical-shaped interior surface 236 of thesecond conduit 228. The interface between theexterior surface 232 of thefirst conduit 224 and the interior surface 236 of thesecond conduit 228 enables thefirst conduit 224 and thesecond conduit 228 to be coupled in variable different relative orientations. - The
second conduit 228 includes a threadedexterior surface 240. Anut 244 at least partially encloses thefirst conduit 224 and is threaded onto thesecond conduit 228. Tightening of thenut 244 on the threadedexterior surface 240 urges the first andsecond conduits exterior surface 232 and the generally conical-shaped interior surface 236. Greater torque applied to thenut 244 generally results in a higher axial sealing force and sealing pressure between theexterior surface 232 of thefirst conduit 224 and the interior surface 236 of thesecond conduit 228. - The generally spherical-shaped
exterior surface 232 of thefirst conduit 224 constitutes a “ball portion” of thefirst conduit 224, which is compressed between thenut 244 and thesecond conduit 228. In addition to the ball portion, thefirst conduit 224 also includes a generallycylindrical stem portion 248 extending generally axially from the ball portion. The end of afuel line 250 is at least partially received and supported by thestem portion 248. - A
ring 260 is disposed between thenut 244 and thefirst conduit 224 to transfer load therebetween. Thering 260 is substantially coaxial with both thenut 244 and thefirst conduit 224. In the illustrated construction, thering 260 is a washer having a conical shape to complement the tapered or conicalinterior surface 272 of thenut 244. Thering 260 may be constructed of copper, while thenut 244 may be constructed of steel. By establishing contact between the generally spherical-shapedexterior surface 232 and thering 260 rather than thenut 244 directly, torque loss during nut tightening may be reduced. The net coefficient of friction that exists in the fitting 220 between thenut 244 and thefirst conduit 224 is influenced by the respective interfaces between thering 260 and both thenut 244 and thefirst conduit 224. In a conventional fitting, the nut contacts the first conduit directly. In the illustrated construction, thering 260 is configured to offer a lower net coefficient of friction between thenut 244 and thefirst conduit 224, compared to direct contact between thenut 244 and thefirst conduit 224. The effect of the reduced friction coefficient is an actual reduction in friction when thenut 244 is being tightened onto thesecond conduit 228. Therefore, the torque required to be applied to thenut 244 to achieve a particular axial sealing force is reduced. Alternately, a greater axial sealing force can be achieved with a given amount of torque applied to thenut 244. Thering 260 can be prefabricated as a flat washer (FIG. 4 ) and deformed to at least partially conform to the shape of the conicalinterior surface 272 of thenut 244. Alternately, thering 260 can be prefabricated in a conical shape (FIG. 5 ) that complements theinterior surface 272 of thenut 244. - Thus, the invention provides various improvements over conventional ball and cone type fittings. Although illustrated and described as three distinct constructions, the features of the invention may be combined in different combinations than those shown in the figures and described above. Various features and advantages of the invention are set forth in the following claims.
Claims (7)
1. A method of manufacturing a ball and cone fluid fitting comprising:
providing a first conduit with a generally spherical-shaped exterior surface;
providing a second conduit with a generally conical-shaped interior surface; and
coining the generally conical-shaped surface with a master ball to create a seating surface for the generally spherical-shaped exterior surface of the first conduit.
2. The method of claim 1 , further comprising coating at least a portion of the generally spherical-shaped exterior surface with a softer metal.
3. The method of claim 2 , wherein coating at least a portion of the generally spherical-shaped exterior surface includes copper electroplating.
4. The method of claim 2 , wherein coating the portion of the generally spherical-shaped exterior surface reduces its surface roughness by about 50 percent.
5. The method of claim 2 , wherein the coating has a thickness of about 0.0005 inch.
6. The method of claim 1 , wherein providing the first conduit with a generally spherical-shaped exterior surface includes providing a prefabricated ball portion, providing a prefabricated stem portion, and joining the prefabricated ball and stem portions together.
7. The method of claim 6 , wherein the prefabricated ball portion includes a surface finish of about 0.05 micron, a roundness of about 0.0006 millimeter, and a diameter tolerance of about 0.0012 millimeter.
Priority Applications (1)
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US13/469,861 US20120216586A1 (en) | 2009-02-04 | 2012-05-11 | High pressure fuel fittings |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
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US12/365,218 US8196967B2 (en) | 2009-02-04 | 2009-02-04 | Improvements to high pressure fuel fittings |
US13/469,861 US20120216586A1 (en) | 2009-02-04 | 2012-05-11 | High pressure fuel fittings |
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US12/365,218 Division US8196967B2 (en) | 2009-02-04 | 2009-02-04 | Improvements to high pressure fuel fittings |
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US20120216586A1 true US20120216586A1 (en) | 2012-08-30 |
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US12/365,218 Expired - Fee Related US8196967B2 (en) | 2009-02-04 | 2009-02-04 | Improvements to high pressure fuel fittings |
US13/469,861 Abandoned US20120216586A1 (en) | 2009-02-04 | 2012-05-11 | High pressure fuel fittings |
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US12/365,218 Expired - Fee Related US8196967B2 (en) | 2009-02-04 | 2009-02-04 | Improvements to high pressure fuel fittings |
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Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20150027413A1 (en) * | 2012-02-28 | 2015-01-29 | Usui Kokusai Sangyo Kaisha Ltd. | Terminal structure of high-pressure fuel pipe for direct injection engine |
CN109140081A (en) * | 2017-06-28 | 2019-01-04 | 中国航发贵阳发动机设计研究所 | A kind of pipeline coupling structure that can be adjusted circumferentially |
Families Citing this family (39)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US8517065B2 (en) * | 2007-01-23 | 2013-08-27 | Sidel Holdings & Technology S.A. | Filling apparatus |
US8038178B2 (en) * | 2009-03-31 | 2011-10-18 | Hitachi, Ltd | High pressure fuel pipe construction for an internal combustion engine |
US8855668B2 (en) * | 2009-05-27 | 2014-10-07 | Telefonaktiebolaget L M Ericsson (Publ) | Device specific tracking area identity lists |
EP2787262B1 (en) * | 2009-09-11 | 2015-11-18 | Victaulic Company | Flexible assembly for sprinklers |
DE102009051065B3 (en) * | 2009-10-28 | 2011-01-20 | Benteler Automobiltechnik Gmbh | Fuel distributor |
US9101950B2 (en) * | 2009-11-04 | 2015-08-11 | Birko Corporation | Sprayer swivel body for packing house washer |
JP5394206B2 (en) | 2009-11-20 | 2014-01-22 | 三桜工業株式会社 | Piping fastening structure |
DE102011002996A1 (en) * | 2011-01-21 | 2012-07-26 | Robert Bosch Gmbh | Fuel injector with improved high pressure connection |
DE102012004359B4 (en) | 2011-03-10 | 2024-04-11 | Löwenstein Medical Technology S.A. | Ball joint with two ball segments |
JP5942351B2 (en) * | 2011-07-12 | 2016-06-29 | 株式会社ニコン | Objective lens, microscope |
US20140041635A1 (en) * | 2012-08-09 | 2014-02-13 | GM Global Technology Operations LLC | Fuel rail connector |
US10746332B1 (en) | 2012-09-27 | 2020-08-18 | Roger C. Haines | Adjustable pipe coupling |
US9157824B2 (en) * | 2012-09-28 | 2015-10-13 | Rosemount Inc. | High pressure fluid coupling |
DE202012104347U1 (en) | 2012-11-12 | 2012-11-28 | Ti Automotive (Heidelberg) Gmbh | Screw connection device for pipelines, in particular for motor vehicle pipelines |
US9777859B2 (en) * | 2012-11-19 | 2017-10-03 | Continental Automotive Systems, Inc. | Purging and sealing-reductant delivery unit for selective catalytic reduction systems |
JP6441824B2 (en) * | 2013-03-01 | 2018-12-19 | ガンサー−ハイドロマグ アーゲーGanser−Hydromag Ag | Device for injecting fuel into a combustion chamber of an internal combustion engine |
DE102013103808B4 (en) * | 2013-04-16 | 2021-09-02 | Tenneco Gmbh | Mounting socket for exhaust pipe |
JP6343444B2 (en) * | 2013-12-20 | 2018-06-13 | 三桜工業株式会社 | Fuel distribution and supply device |
EP3097303B1 (en) | 2014-03-03 | 2018-03-28 | Siemens Aktiengesellschaft | Conical screw connection of a fuel line |
US20150308597A1 (en) * | 2014-04-24 | 2015-10-29 | Brad Lillmars | Swiveling Plumbing Fitting |
DE102014208369A1 (en) * | 2014-05-05 | 2015-11-05 | Bayerische Motoren Werke Aktiengesellschaft | Fuel line for an internal combustion engine |
CN104514941A (en) * | 2014-11-26 | 2015-04-15 | 中国北方发动机研究所(天津) | High-pressure pipeline sealing device |
CN105987241B (en) * | 2015-01-30 | 2018-07-10 | 中国石油天然气集团公司 | A kind of pressure piping joint sealing device |
DE102015102877A1 (en) * | 2015-02-27 | 2016-09-01 | Benteler Automobiltechnik Gmbh | Connecting arrangement for pipes |
JP2016217323A (en) * | 2015-05-26 | 2016-12-22 | 三桜工業株式会社 | Connecting head part of fuel piping and fuel piping |
DE102015122309A1 (en) * | 2015-12-18 | 2017-06-22 | Voss Fluid Gmbh | pipe connection |
DE202016005439U1 (en) * | 2016-09-07 | 2017-09-08 | Bernd Stängle | joint line |
JP6734179B2 (en) | 2016-10-31 | 2020-08-05 | 三桜工業株式会社 | Fuel piping |
CN108145000B (en) * | 2017-12-08 | 2019-08-09 | 航天材料及工艺研究所 | A kind of uniform wall thickness method of titanium alloy thick spherical shell isothermal punching press |
KR102087367B1 (en) * | 2018-03-30 | 2020-03-10 | 주식회사 피에스하이텍 | swivel joint |
JP2020139578A (en) * | 2019-02-28 | 2020-09-03 | 株式会社タブチ | Swingable joint |
CN110939806B (en) * | 2019-12-11 | 2021-07-27 | 徐州徐工液压件有限公司 | Low-temperature-resistant rubber combined joint |
US11352992B2 (en) | 2020-02-12 | 2022-06-07 | Delphi Technologies Ip Limited | Fuel injector |
US10995716B1 (en) | 2020-02-21 | 2021-05-04 | Delphi Technologies Ip Limited | Fuel system having a connection between a fuel injector and a fuel distribution conduit |
US11143154B2 (en) * | 2020-03-13 | 2021-10-12 | Delphi Technologies Ip Limited | Fuel system having a connection between a fuel injector and a fuel distribution conduit |
US10995720B1 (en) * | 2020-07-29 | 2021-05-04 | Delphi Technologies Ip Limited | Fuel system having a connection between a fuel injector and a fuel distribution conduit |
US20220307454A1 (en) * | 2021-03-26 | 2022-09-29 | Robert Bosch Gmbh | Fitting for a Fluid Delivery System |
FR3122456A1 (en) | 2021-04-29 | 2022-11-04 | Duncha France | Fuel supply device |
CN114776909A (en) * | 2022-04-24 | 2022-07-22 | 西京学院 | High-pressure-resistant quartz-metal pipeline sealing interface |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3875027A (en) * | 1973-06-29 | 1975-04-01 | Bundy Corp | Method of electroplating tubing prior to terne alloy coating |
US4788382A (en) * | 1987-05-18 | 1988-11-29 | Isotronics, Inc. | Duplex glass preforms for hermetic glass-to-metal compression sealing |
US7832660B2 (en) * | 2003-09-29 | 2010-11-16 | Continental Automotive Systems Us, Inc. | Injector seat that includes a coined seal band |
Family Cites Families (36)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US717882A (en) * | 1902-08-21 | 1903-01-06 | Holland Co | Ball-and-socket joint. |
US900533A (en) * | 1905-05-06 | 1908-10-06 | Barco Brass And Joint Company | Flexible fluid-joint. |
US840324A (en) * | 1905-05-06 | 1907-01-01 | Us Flexible Joint Company | Flexible fluid-joint. |
US1187642A (en) * | 1914-10-17 | 1916-06-20 | Max J Milz | Pipe-joint |
US1346523A (en) * | 1919-08-30 | 1920-07-13 | Bard Francis Norwood | Composite non-metallic gasket |
US2564938A (en) * | 1945-05-21 | 1951-08-21 | Charles F Warren | Flexible pipe joint |
US2649314A (en) * | 1951-08-07 | 1953-08-18 | Cecil K Farr | Quick detachable swivel pipe union |
US2680358A (en) * | 1952-05-14 | 1954-06-08 | John A Zublin | Flexible conduit for high-pressure fluid |
US2726881A (en) * | 1953-01-05 | 1955-12-13 | Clifford M Howard | Knuckle joint with lateral actuating means |
US2931672A (en) * | 1956-06-05 | 1960-04-05 | George W Merritt | Flexible duct mounting |
US3361450A (en) * | 1964-08-19 | 1968-01-02 | Imp Eastman Corp | Laterally and angularly adjustable tube fitting |
US3479061A (en) * | 1966-09-23 | 1969-11-18 | Arthur L Smookler | Partially balanced flexible pipe joint |
DE1945523A1 (en) * | 1969-09-09 | 1971-03-11 | Martin Herter | Ball joint pipe connection |
US4012060A (en) * | 1975-03-31 | 1977-03-15 | Reneau Bobby J | Ball flex union |
JPS55102070U (en) * | 1979-01-11 | 1980-07-16 | ||
US4776615A (en) * | 1983-01-24 | 1988-10-11 | Pomeco Corporation | Vapor recovery apparatus with swiveled nozzle |
JPS6339770A (en) * | 1986-08-01 | 1988-02-20 | 高橋 清 | Vacuum forceps made of total fluorocarbon resin |
DE4407306C1 (en) | 1994-03-04 | 1995-09-07 | Guido Juergen Dipl Ing | Pressure pipe connection for fuel injection system |
US5658022A (en) * | 1995-07-27 | 1997-08-19 | Shi; Wu-Huan | Pipe connector improvement structure |
US6045162A (en) * | 1997-01-14 | 2000-04-04 | Usui Kokusai Sangyo Kaisha Limited | Joint head for high-pressure metal piping, and common rail to which the piping is to be joined |
US5975588A (en) * | 1997-09-06 | 1999-11-02 | Hesseln; Joerg | Turnable pipe and hose connections |
US5975490A (en) * | 1998-01-07 | 1999-11-02 | Essman Screw Products, Inc. | Swivel coupling for hose |
US6158781A (en) * | 1998-05-18 | 2000-12-12 | Taper-Lok | Pipeline swivel coupling |
US6123268A (en) * | 1999-05-04 | 2000-09-26 | Nordson Corporation | Angularly adjustable nozzle |
DE19927145A1 (en) * | 1999-06-15 | 2000-12-28 | Bosch Gmbh Robert | High pressure connection for a fuel injection system for internal combustion engines |
US6374806B1 (en) * | 1999-10-25 | 2002-04-23 | International Truck And Engine Corp. | Actuating fluid delivery system for a fuel injector |
DE10125865B4 (en) * | 2000-05-29 | 2007-06-06 | Usui Kokusai Sangyo Kaisha Ltd., Nagasawa | High-pressure metal pipe with connection head, method for forming the head and a connection disk for the connection head |
JP2002130075A (en) * | 2000-10-23 | 2002-05-09 | Otics Corp | Connecting structure of common rail and injection pipe |
US6705647B1 (en) * | 2000-11-22 | 2004-03-16 | Strahman Valves, Inc. | Fluid coupling device |
JP2004019541A (en) * | 2002-06-17 | 2004-01-22 | Denso Corp | High-pressure fuel injection pipe |
JP4046334B2 (en) * | 2003-06-18 | 2008-02-13 | 臼井国際産業株式会社 | Connection structure of branch connection for common rail |
JP4498693B2 (en) * | 2003-06-20 | 2010-07-07 | 臼井国際産業株式会社 | High pressure fuel injection pipe |
JP4357362B2 (en) * | 2004-05-19 | 2009-11-04 | 臼井国際産業株式会社 | Joint structure of branch connection for common rail |
DE102005003519A1 (en) * | 2005-01-25 | 2006-08-03 | Benteler Automobiltechnik Gmbh | Connecting arrangement for pipes |
US20060284421A1 (en) * | 2005-06-15 | 2006-12-21 | Fonville Carl E | High-pressure fuel line end fitting and method |
JP5178176B2 (en) * | 2007-12-17 | 2013-04-10 | 臼井国際産業株式会社 | Connecting head structure of high-pressure fuel injection pipe |
-
2009
- 2009-02-04 US US12/365,218 patent/US8196967B2/en not_active Expired - Fee Related
- 2009-12-03 JP JP2009275097A patent/JP5623734B2/en not_active Expired - Fee Related
-
2010
- 2010-01-19 DE DE102010004918A patent/DE102010004918A1/en not_active Ceased
-
2012
- 2012-05-11 US US13/469,861 patent/US20120216586A1/en not_active Abandoned
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3875027A (en) * | 1973-06-29 | 1975-04-01 | Bundy Corp | Method of electroplating tubing prior to terne alloy coating |
US4788382A (en) * | 1987-05-18 | 1988-11-29 | Isotronics, Inc. | Duplex glass preforms for hermetic glass-to-metal compression sealing |
US7832660B2 (en) * | 2003-09-29 | 2010-11-16 | Continental Automotive Systems Us, Inc. | Injector seat that includes a coined seal band |
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20150027413A1 (en) * | 2012-02-28 | 2015-01-29 | Usui Kokusai Sangyo Kaisha Ltd. | Terminal structure of high-pressure fuel pipe for direct injection engine |
US20160123287A1 (en) * | 2012-02-28 | 2016-05-05 | Usui Kokusai Sangyo Kaisha Ltd. | Terminal structure of high-pressure fuel pipe for direct injection engine |
US9599080B2 (en) * | 2012-02-28 | 2017-03-21 | Usui Kokusai Sangyo Kaisha Limited | Terminal structure of high-pressure fuel pipe for direct injection engine |
US9664163B2 (en) * | 2012-02-28 | 2017-05-30 | Usui Kokusai Sangyo Kaisha Limited | Terminal structure of high-pressure fuel pipe for direct injection engine |
CN109140081A (en) * | 2017-06-28 | 2019-01-04 | 中国航发贵阳发动机设计研究所 | A kind of pipeline coupling structure that can be adjusted circumferentially |
Also Published As
Publication number | Publication date |
---|---|
JP2010180875A (en) | 2010-08-19 |
DE102010004918A1 (en) | 2010-08-05 |
JP5623734B2 (en) | 2014-11-12 |
US8196967B2 (en) | 2012-06-12 |
US20100194096A1 (en) | 2010-08-05 |
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Owner name: ROBERT BOSCH GMBH, GERMANY Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:SIMS, DEWEY M., JR.;REEL/FRAME:028197/0246 Effective date: 20090202 Owner name: ROBERT BOSCH LLC, ILLINOIS Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:SIMS, DEWEY M., JR.;REEL/FRAME:028197/0246 Effective date: 20090202 |
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