US20140042714A1 - High-pressure sealing ring - Google Patents
High-pressure sealing ring Download PDFInfo
- Publication number
- US20140042714A1 US20140042714A1 US13/982,789 US201213982789A US2014042714A1 US 20140042714 A1 US20140042714 A1 US 20140042714A1 US 201213982789 A US201213982789 A US 201213982789A US 2014042714 A1 US2014042714 A1 US 2014042714A1
- Authority
- US
- United States
- Prior art keywords
- sealing
- sealing ring
- piston
- ring
- cylinder
- 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
- 238000007789 sealing Methods 0.000 title claims abstract description 135
- 238000005096 rolling process Methods 0.000 claims abstract description 3
- 230000000712 assembly Effects 0.000 abstract description 6
- 238000000429 assembly Methods 0.000 abstract description 6
- 238000003780 insertion Methods 0.000 description 9
- 230000037431 insertion Effects 0.000 description 9
- 230000007246 mechanism Effects 0.000 description 6
- 230000009471 action Effects 0.000 description 4
- 238000000034 method Methods 0.000 description 4
- 238000005452 bending Methods 0.000 description 3
- 238000013461 design Methods 0.000 description 3
- 210000002445 nipple Anatomy 0.000 description 3
- 238000001816 cooling Methods 0.000 description 2
- 230000003247 decreasing effect Effects 0.000 description 2
- 239000012530 fluid Substances 0.000 description 2
- 239000007789 gas Substances 0.000 description 2
- 238000010438 heat treatment Methods 0.000 description 2
- 238000009434 installation Methods 0.000 description 2
- 230000004044 response Effects 0.000 description 2
- 239000002253 acid Substances 0.000 description 1
- 150000007513 acids Chemical class 0.000 description 1
- 230000002411 adverse Effects 0.000 description 1
- 230000000295 complement effect Effects 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000001125 extrusion Methods 0.000 description 1
- 231100001261 hazardous Toxicity 0.000 description 1
- 238000011065 in-situ storage Methods 0.000 description 1
- 230000000670 limiting effect Effects 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 239000003921 oil Substances 0.000 description 1
- 238000010248 power generation Methods 0.000 description 1
- 238000003825 pressing Methods 0.000 description 1
- 239000012857 radioactive material Substances 0.000 description 1
- 230000002829 reductive effect Effects 0.000 description 1
- 230000008439 repair process Effects 0.000 description 1
- 230000003068 static effect Effects 0.000 description 1
Images
Classifications
-
- 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
- F16B—DEVICES FOR FASTENING OR SECURING CONSTRUCTIONAL ELEMENTS OR MACHINE PARTS TOGETHER, e.g. NAILS, BOLTS, CIRCLIPS, CLAMPS, CLIPS OR WEDGES; JOINTS OR JOINTING
- F16B31/00—Screwed connections specially modified in view of tensile load; Break-bolts
- F16B31/04—Screwed connections specially modified in view of tensile load; Break-bolts for maintaining a tensile load
- F16B31/043—Prestressed connections tensioned by means of liquid, grease, rubber, explosive charge, or the like
-
- 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
- F16J—PISTONS; CYLINDERS; SEALINGS
- F16J15/00—Sealings
- F16J15/02—Sealings between relatively-stationary surfaces
- F16J15/06—Sealings between relatively-stationary surfaces with solid packing compressed between sealing surfaces
-
- 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
- F16J—PISTONS; CYLINDERS; SEALINGS
- F16J15/00—Sealings
- F16J15/02—Sealings between relatively-stationary surfaces
- F16J15/06—Sealings between relatively-stationary surfaces with solid packing compressed between sealing surfaces
- F16J15/061—Sealings between relatively-stationary surfaces with solid packing compressed between sealing surfaces with positioning means
-
- 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
- F16J—PISTONS; CYLINDERS; SEALINGS
- F16J15/00—Sealings
- F16J15/02—Sealings between relatively-stationary surfaces
- F16J15/06—Sealings between relatively-stationary surfaces with solid packing compressed between sealing surfaces
- F16J15/062—Sealings between relatively-stationary surfaces with solid packing compressed between sealing surfaces characterised by the geometry of the seat
-
- 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
- F16J—PISTONS; CYLINDERS; SEALINGS
- F16J15/00—Sealings
- F16J15/02—Sealings between relatively-stationary surfaces
- F16J15/06—Sealings between relatively-stationary surfaces with solid packing compressed between sealing surfaces
- F16J15/08—Sealings between relatively-stationary surfaces with solid packing compressed between sealing surfaces with exclusively metal packing
- F16J15/0887—Sealings between relatively-stationary surfaces with solid packing compressed between sealing surfaces with exclusively metal packing the sealing effect being obtained by elastic deformation of the packing
-
- 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
- F16J—PISTONS; CYLINDERS; SEALINGS
- F16J15/00—Sealings
- F16J15/02—Sealings between relatively-stationary surfaces
- F16J15/06—Sealings between relatively-stationary surfaces with solid packing compressed between sealing surfaces
- F16J15/10—Sealings between relatively-stationary surfaces with solid packing compressed between sealing surfaces with non-metallic packing
- F16J15/104—Sealings between relatively-stationary surfaces with solid packing compressed between sealing surfaces with non-metallic packing characterised by structure
- F16J15/106—Sealings between relatively-stationary surfaces with solid packing compressed between sealing surfaces with non-metallic packing characterised by structure homogeneous
-
- 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
- F16J—PISTONS; CYLINDERS; SEALINGS
- F16J15/00—Sealings
- F16J15/46—Sealings with packing ring expanded or pressed into place by fluid pressure, e.g. inflatable packings
- F16J15/48—Sealings with packing ring expanded or pressed into place by fluid pressure, e.g. inflatable packings influenced by the pressure within the member to be sealed
Definitions
- This invention relates to a high-pressure sealing ring.
- the invention particularly relates, but is not limited to, a high-pressure sealing ring suitable for use in seals for hydraulic assemblies.
- the invention can have particular application in hydraulic assemblies (such as hydraulic tensioning jacks or nuts) operating at high pressures and/or temperatures.
- the hydraulic assemblies which may employ the sealing ring included those used in the nuclear, electricity-generating, steam-generating and marine installations.
- the failure of the sealing rings forming the seals in high-pressure and/or high-temperature hydraulic assemblies is likely to have catastrophic consequences, including the release of radioactive materials, super-heated steam, hazardous liquids or gases (including acids and alkalis), other fluids (including oils and other petrochemical-based products); and/or may result in the mechanical failure of machinery.
- the present invention resides in a sealing ring for use in a hydraulic assembly of the type having a piston slidably received in a cylinder, the sealing ring including:
- the external heel has a convex profile to form a “rolling” line of sealing contact with a seat in a cylinder or piston to which the ring body is installed.
- the leg has a sealing protrusion intermediate an outer sealing face of the leg, the sealing protrusion having a cylindrical sealing face interposed between a pair of inclined ramp faces, the sealing protrusion and a distal portion of the outer sealing face forming two lines of sealing contact between the ring body and an adjacent cylinder or piston to which the ring body is installed.
- the foot has a toe portion with a relief angle a in the range of 1° to 5° relative to the central axis of the ring body.
- the sealing ring has a protrusion on an outer sealing face of the leg, or the external heel is, receivable in a recess in an adjacent cylinder or piston to cause the sealing ring to be “locked” in position.
- FIG. 1 is an isometric view of a hydraulic nut manufactured and sold by Technofast Industries Pty Ltd, of 2/677 Boundary Road, Richlands, Queensland 4077, Australia under the “TECHNOFAST” and “EziTite” Registered Trade Marks;
- FIG. 2 is a sectional side view of the hydraulic nut of FIG. 1 fitted with sealing rings in accordance with a first embodiment of the present invention
- FIG. 3 is a top plan view of the outer sealing ring in FIG. 2 ;
- FIG. 4 is a sectional side view of the sealing ring taken on section E-E on FIG. 3 ;
- FIG. 5 is a view, taken at view F on FIG. 4 , of the cross-section of the sealing ring, on an enlarged scale;
- FIG. 6 is a sectional side view, on an enlarged scale, of the inner sealing ring and of the associated cylinder and piston of FIG. 2 ;
- FIG. 7 is sectional side view, similar to FIG. 6 , of a sealing ring of a second embodiment of the present invention and of the associated cylinder and piston;
- FIG. 8 is a similar view of a sealing ring of a third embodiment of the present invention and of the associated cylinder and piston;
- FIG. 9 is a similar view of a sealing ring of a fourth embodiment of the invention and of the associated cylinder and piston;
- FIG. 10 is a sectional side view of a modified version of the hydraulic nut fitted with a pair of sealing rings of a fifth embodiment of the present invention.
- FIG. 11 is an enlarged view of one of the sealing rings of FIG. 10 .
- the hydraulic nut 10 is designed for high-pressure and/or high-temperature applications, including the securing of steam and gas turbines and other nuclear or fossil fuelled power generation plant.
- the hydraulic nut 100 has a tubular hydraulic nut body 1 having a screw-threaded bore 11 therethrough for releasable engagement with a bolt, nut or threaded component (not shown) to be tensioned.
- An annular extension 12 forms the cylinder wall 13 slidably received in the inner annular bore 21 of the body 22 of the piston 2 .
- the piston 2 is seated in a spherical washer 4 which bears against an adjacent component (not shown) to be secured by the tensioned bolt, nut or threaded component.
- An optional sacrificial ring (not shown) may be interposed between the body 22 of the piston 2 and the screw-threaded tubular body 31 of the lock ring 3 which is engaged with external screw-threads 14 about the nut body 1 .
- a nipple adaptor 8 and closure plug 9 are mounted on the external annular face 15 of the nut body 1 and are connected to ports 16 in the nut body 1 , which in turn are connected to the inner annular cavity 17 defined by the annular extension 12 in the nut body 1 and the inner annular bore 21 of the piston 2 .
- a nipple 10 in the nipple adaptor 8 connects the hydraulic nut 100 to a source of high-pressure hydraulic fluid (not shown).
- Outer and inner sealing rings 5 , 6 are located in the inner annular cavity 17 , and the outer annular cavity 18 (defined by a cylindrical wall 19 about the nut body 1 and the outer annular bore 23 of the piston 2 ), respectively. It will be noted that a circumferential flange 19 A about the nut body 1 retains the outer sealing ring 5 in the outer annular cavity 18 .
- outer and inner sealing rings 5 , 6 have the same sectional configuration, the detailed description thereof, with reference to FIGS. 3 to 5 , will be with respect to the inner sealing ring 6 .
- the inner sealing ring 6 is of annular configuration, having an annular body 61 in plan view, as illustrated in FIG. 3 .
- the ring body 61 is of “modified-L” cross-section, as illustrated in FIGS. 4 and 5 .
- the ring body 61 has a “leg” 62 and a “foot” 63 with a “valley” 64 on the inner side of the connection there-between.
- the foot 63 has a “toe” 63 A in sealing engagement with the cylindrical wall 13 of the annular extension 12 on the nut body 1 .
- the “toe” 63 A on the foot 63 has a relief angle a of e.g. 1°-5° from the central axis of the sealing ring 6 —see FIG. 5
- a curved i.e. convex “heel” 65 externally on the ring body 61 , interconnects the leg 62 and the foot 63 .
- the external outer sealing face 62 A of the leg 62 has an optional secondary sealing protrusion 66 with a (substantially cylindrical) sealing face 67 intermediate inclined ramp faces 68 , 69 .
- the convex heel 65 allows the sealing ring body 61 to “roll” on the support surface at the corner of the inner annular bore 21 in the piston 2 so that the distal portion of the outer sealing face 62 A of the leg 62 can be deflected into sealing contact with the cylindrical side wall of the inner annular bore.
- cylindrical sealing face 67 of the sealing protrusion 66 is also urged into sealing contact with the wall of the inner annular bore 21 in piston 2 , so that there are two ( 2 ) lines of sealing engagement between the leg 62 of the sealing ring body 61 and the inner annular bore 21 in the piston 2 .
- the annular end face 62 B on the leg 62 can be engaged by the corresponding abutting face of each component (eg FIG. 2 , 22 or 1 ) enable the sealing ring 6 to be fitted in the inner annular bore in piston 2 without the requirement for an insertion ring, as the engagement between the annular end face 62 B, and the insertion tool will not adversely effect the sealing engagement between the leg 62 and the inner annular bore 21 .
- the curved heel 65 provides a line of “rolling-contact” between the ring body 61 and the corner of the annular inner bore 21 which enables the leg 62 to move into, or out of, sealing contact with the piston 2 as the hydraulic pressure in annular cavity 17 is increased, or decreased, respectively. This ensures that when the hydraulic pressure is increased after the initial increase/decrease cycle, the leg 62 (and sealing protrusion 66 ) can again make effective sealing contact with the inner annular bore 21 in the piston 2 .
- the selection of the material(s) for the manufacture of the sealing ring 6 , and the dimensions and/or configurations of the respective portions of the sealing ring body 61 , will be selected to suit the particular intended application of the hydraulic assembly to which the sealing ring 6 is the be fitted.
- two or more of the sealing rings 5 , 6 may be fitted to a single hydraulic assembly, such as the hydraulic nut 100 .
- the secondary sealing protrusion 66 may be received within a recess 24 in the outer annular bore 23 of the piston 2 .
- the recess 24 has an inclined abutment face 25 which is engageable by the upper ramp face 69 on the secondary sealing protrusion 656 to “lock”, or at least locate, the sealing ring 6 relative to the piston 2 . (The contact between the secondary sealing protrusion 66 and the recess 24 also increases the area of sealing contact between the sealing ring 6 and piston 2 .)
- FIG. 7 illustrates a second embodiment of the sealing ring 106 , where the secondary sealing protrusion 166 is provided in the form of an external circumferential flange about the leg 162 ; and the upper face 169 of the secondary sealing protrusion can engage, and be restrained by, a complementary abutment face 125 of recess 124 in the piston 102 .
- the abutment face 125 extends perpendicular to a cylindrically floor 126 of the recess 124 , the floor 126 being connected to a lower ramp face 127 .
- the recess 224 is of reduced height relative to recess 124 ; and the secondary sealing protrusion 266 has an upper face 269 engageable with an abutment face 225 similar to the abutment face 125 of the recess 124 .
- the secondary sealing protrusion has the profile of a right-angle triangle.
- the distal portions of the legs 162 , 262 of the sealing rings 106 , 206 are of thicker cross-section than the portions intermediate the secondary sealing portions 166 , 266 and the heel portions 165 , 265 during assembly procedures.
- FIG. 9 illustrates a fourth embodiment of the sealing ring 306 , where the secondary sealing protrusion is omitted from the leg 362 , but where the heel portion 365 is received in a recess 324 to locate and restrain the sealing ring 306 in the piston 302 .
- the location of the heel portion 365 in the recess 324 will still enable the line of “rolling-contact” to be maintained between the ring body 361 and the recess 324 of the piston 302 ; and the foot 363 remains in sealing contact with the nut body 301 ; whether or not the leg 362 moves into, or out of, sealing contact with the piston 302 ; as the hydraulic pressure on the annular cavity 317 is increased, or decreased.
- FIGS. 10 and illustrate sealing rings 405 , 406 of a fifth embodiment, which are closely related to the sealing rings 6 of the first embodiment—with particular reference to FIG. 6 .
- the sealing ring 406 has a ring body 461 with a leg 462 and foot 463 .
- the toe 463 A has a relief angle ⁇ of e.g. 1°-3° relative to the adjacent wall 413 of the nut body 401 .
- the annular bore 423 of the piston 402 is inwardly tapered in a downwards direction, and the portion 465 A of the ring body 461 has a corresponding “taper” down to the curved heel 465 .
- the sealing rings of the present invention produce an initial sealing action from the action of spring force generated by slight elastic bending of the sealing ring as it is inserted into place. This bending forces the ‘heel’ of the sealing ring into its respective seat and the ‘sealing edge’ (of the toe) against the cylinder wall. As hydraulic pressure is increased in the sealed chamber, the sealing mechanism will be further enhanced by increasing inner and outer radial thrust generated as the sealing ring flexes and rolls on its ‘heel’ to follow outward radial movement of the cylinder wall.
- the alternative designs of the embodiments described and illustrated predict and allow a degree of bending of the seal body to continually align the ‘sealing edge’ (of the toe) against the cylinder wall.
- sealing of the (leg of the) sealing ring to the ‘seal carrier’ side of the seal retaining groove can be made in the upper portion (or the leg) of the “L” shape of the seal.
- mechanisms to physically retain the sealing ring can be incorporated as illustrated in FIGS. 7 to 9 . These mechanisms can also combine a sealing function in the upper portion (or the leg) of the “L” shape of the sealing ring, together with the mechanical location function.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Architecture (AREA)
- Fluid Mechanics (AREA)
- Geometry (AREA)
- Sealing Devices (AREA)
- Pistons, Piston Rings, And Cylinders (AREA)
- Actuator (AREA)
- Sealing With Elastic Sealing Lips (AREA)
Abstract
Description
- 1. Field of the Invention
- This invention relates to a high-pressure sealing ring.
- The invention particularly relates, but is not limited to, a high-pressure sealing ring suitable for use in seals for hydraulic assemblies. The invention can have particular application in hydraulic assemblies (such as hydraulic tensioning jacks or nuts) operating at high pressures and/or temperatures.
- The hydraulic assemblies which may employ the sealing ring included those used in the nuclear, electricity-generating, steam-generating and marine installations.
- 2. Prior Art
- The failure of the sealing rings forming the seals in high-pressure and/or high-temperature hydraulic assemblies is likely to have catastrophic consequences, including the release of radioactive materials, super-heated steam, hazardous liquids or gases (including acids and alkalis), other fluids (including oils and other petrochemical-based products); and/or may result in the mechanical failure of machinery.
-
FIGS. 2A to 2Q of International Publication WO 2005/080837 (=International Patent Application PCT/AU2005/000253) (Bucknell, John Wentworth), and the accompany description, disclosed a number of alternative profiles for sealing rings in hydraulic assemblies, including the use of the sealing rings in hydraulic fasteners and nuts. - U.S. Pat. No. 6,494,465 (Bucknell) (=International Publication WO 98/00660 =International Patent Application PCT/AU97/00425) further discloses earlier sealing rings suitable for high-pressure and/or high-temperature Applications.
- Problems with the existing sealing rings referred to above include:
- a) the requirement for difficult and precise assembly procedures, including selective heating and/or cooling of the pistons and/or cylinders to enable the installation of the sealing rings;
- b) the requirement for insertion rings, interposed between the sealing rings and the insertion tools (e.g. a press)—where the insertion rings may lie in, and extend above, recesses in the upper faces of the sealing rings and which are left in situ; and/or
- c) the requirement for complete replacement of the sealing rings, due to failure to achieve acceptable resealing between the (pre-used) sealing rings and the cylinder walls if attempted after disassembly and reassembly e.g. for maintenance or repair.
- It is an object of the present invention to provide a sealing ring which ameliorates, or at least, minimises the problems of the Prior Art sealing rings.
- Other preferred objects of the present invention will become apparent from the following description.
- In a broad aspect, the present invention resides in a sealing ring for use in a hydraulic assembly of the type having a piston slidably received in a cylinder, the sealing ring including:
- an annular ring body of “substantially L” cross-section, with a leg portion and a foot portion interconnected by an external heel having a curved profile.
- Preferably, the external heel has a convex profile to form a “rolling” line of sealing contact with a seat in a cylinder or piston to which the ring body is installed.
- In one preferred embodiment, the leg has a sealing protrusion intermediate an outer sealing face of the leg, the sealing protrusion having a cylindrical sealing face interposed between a pair of inclined ramp faces, the sealing protrusion and a distal portion of the outer sealing face forming two lines of sealing contact between the ring body and an adjacent cylinder or piston to which the ring body is installed.
- Preferably, the foot has a toe portion with a relief angle a in the range of 1° to 5° relative to the central axis of the ring body.
- Preferably, the sealing ring has a protrusion on an outer sealing face of the leg, or the external heel is, receivable in a recess in an adjacent cylinder or piston to cause the sealing ring to be “locked” in position.
- To enable the invention to be fully understood, preferred embodiments will be described with reference to the accompanying drawings, in which:
-
FIG. 1 is an isometric view of a hydraulic nut manufactured and sold by Technofast Industries Pty Ltd, of 2/677 Boundary Road, Richlands, Queensland 4077, Australia under the “TECHNOFAST” and “EziTite” Registered Trade Marks; -
FIG. 2 is a sectional side view of the hydraulic nut ofFIG. 1 fitted with sealing rings in accordance with a first embodiment of the present invention; -
FIG. 3 is a top plan view of the outer sealing ring inFIG. 2 ; -
FIG. 4 is a sectional side view of the sealing ring taken on section E-E onFIG. 3 ; -
FIG. 5 is a view, taken at view F onFIG. 4 , of the cross-section of the sealing ring, on an enlarged scale; -
FIG. 6 is a sectional side view, on an enlarged scale, of the inner sealing ring and of the associated cylinder and piston ofFIG. 2 ; -
FIG. 7 is sectional side view, similar toFIG. 6 , of a sealing ring of a second embodiment of the present invention and of the associated cylinder and piston; -
FIG. 8 is a similar view of a sealing ring of a third embodiment of the present invention and of the associated cylinder and piston; -
FIG. 9 is a similar view of a sealing ring of a fourth embodiment of the invention and of the associated cylinder and piston; -
FIG. 10 is a sectional side view of a modified version of the hydraulic nut fitted with a pair of sealing rings of a fifth embodiment of the present invention; and -
FIG. 11 is an enlarged view of one of the sealing rings ofFIG. 10 . - NB: Any dimensions and/or annotations on the drawings are by way of illustration only and are not limiting in any way to the scope of the invention.
- Referring to
FIGS. 1 and 2 , thehydraulic nut 10 is designed for high-pressure and/or high-temperature applications, including the securing of steam and gas turbines and other nuclear or fossil fuelled power generation plant. - The
hydraulic nut 100 has a tubularhydraulic nut body 1 having a screw-threadedbore 11 therethrough for releasable engagement with a bolt, nut or threaded component (not shown) to be tensioned. Anannular extension 12 forms thecylinder wall 13 slidably received in the innerannular bore 21 of thebody 22 of thepiston 2. - The
piston 2 is seated in aspherical washer 4 which bears against an adjacent component (not shown) to be secured by the tensioned bolt, nut or threaded component. - An optional sacrificial ring (not shown) may be interposed between the
body 22 of thepiston 2 and the screw-threaded tubular body 31 of thelock ring 3 which is engaged with external screw-threads 14 about thenut body 1. - A
nipple adaptor 8 and closure plug 9 are mounted on the external annular face 15 of thenut body 1 and are connected toports 16 in thenut body 1, which in turn are connected to the innerannular cavity 17 defined by theannular extension 12 in thenut body 1 and the innerannular bore 21 of thepiston 2. Anipple 10 in thenipple adaptor 8 connects thehydraulic nut 100 to a source of high-pressure hydraulic fluid (not shown). - Outer and
inner sealing rings annular cavity 17, and the outer annular cavity 18 (defined by a cylindrical wall 19 about thenut body 1 and the outerannular bore 23 of the piston 2), respectively. It will be noted that a circumferential flange 19A about thenut body 1 retains theouter sealing ring 5 in the outerannular cavity 18. - As the outer and
inner sealing rings FIGS. 3 to 5 , will be with respect to theinner sealing ring 6. - Referring now to
FIGS. 3 to 5 , theinner sealing ring 6 is of annular configuration, having anannular body 61 in plan view, as illustrated inFIG. 3 . - The
ring body 61 is of “modified-L” cross-section, as illustrated inFIGS. 4 and 5 . - The
ring body 61 has a “leg” 62 and a “foot” 63 with a “valley” 64 on the inner side of the connection there-between. - The
foot 63 has a “toe” 63A in sealing engagement with thecylindrical wall 13 of theannular extension 12 on thenut body 1. The “toe” 63A on thefoot 63 has a relief angle a of e.g. 1°-5° from the central axis of the sealingring 6—seeFIG. 5 - A curved i.e. convex “heel” 65, externally on the
ring body 61, interconnects theleg 62 and thefoot 63. - The external
outer sealing face 62A of theleg 62 has an optionalsecondary sealing protrusion 66 with a (substantially cylindrical) sealingface 67 intermediate inclined ramp faces 68, 69. - In use, the
convex heel 65 allows the sealingring body 61 to “roll” on the support surface at the corner of the innerannular bore 21 in thepiston 2 so that the distal portion of theouter sealing face 62A of theleg 62 can be deflected into sealing contact with the cylindrical side wall of the inner annular bore. - In addition, the
cylindrical sealing face 67 of thesealing protrusion 66 is also urged into sealing contact with the wall of the innerannular bore 21 inpiston 2, so that there are two (2) lines of sealing engagement between theleg 62 of the sealingring body 61 and the innerannular bore 21 in thepiston 2. - The
annular end face 62B on theleg 62 can be engaged by the corresponding abutting face of each component (egFIG. 2 , 22 or 1) enable thesealing ring 6 to be fitted in the inner annular bore inpiston 2 without the requirement for an insertion ring, as the engagement between theannular end face 62B, and the insertion tool will not adversely effect the sealing engagement between theleg 62 and the innerannular bore 21. - As stated above, the
curved heel 65 provides a line of “rolling-contact” between thering body 61 and the corner of the annularinner bore 21 which enables theleg 62 to move into, or out of, sealing contact with thepiston 2 as the hydraulic pressure inannular cavity 17 is increased, or decreased, respectively. This ensures that when the hydraulic pressure is increased after the initial increase/decrease cycle, the leg 62 (and sealing protrusion 66) can again make effective sealing contact with the innerannular bore 21 in thepiston 2. - The selection of the material(s) for the manufacture of the sealing
ring 6, and the dimensions and/or configurations of the respective portions of the sealingring body 61, will be selected to suit the particular intended application of the hydraulic assembly to which thesealing ring 6 is the be fitted. - As illustrated in
FIG. 2 , two or more of the sealing rings 5, 6 may be fitted to a single hydraulic assembly, such as thehydraulic nut 100. - As illustrated in enlarged scale in
FIG. 6 , thesecondary sealing protrusion 66 may be received within arecess 24 in the outer annular bore 23 of thepiston 2. Therecess 24 has aninclined abutment face 25 which is engageable by the upper ramp face 69 on the secondary sealing protrusion 656 to “lock”, or at least locate, the sealingring 6 relative to thepiston 2. (The contact between thesecondary sealing protrusion 66 and therecess 24 also increases the area of sealing contact between the sealingring 6 andpiston 2.) -
FIG. 7 illustrates a second embodiment of the sealingring 106, where thesecondary sealing protrusion 166 is provided in the form of an external circumferential flange about theleg 162; and theupper face 169 of the secondary sealing protrusion can engage, and be restrained by, acomplementary abutment face 125 ofrecess 124 in the piston 102. Theabutment face 125 extends perpendicular to acylindrically floor 126 of therecess 124, thefloor 126 being connected to alower ramp face 127. - In the third embodiment illustrated in
FIG. 8 , therecess 224 is of reduced height relative to recess 124; and thesecondary sealing protrusion 266 has anupper face 269 engageable with anabutment face 225 similar to theabutment face 125 of therecess 124. The secondary sealing protrusion has the profile of a right-angle triangle. - In both the second and third embodiments, the distal portions of the
legs secondary sealing portions heel portions -
FIG. 9 illustrates a fourth embodiment of the sealingring 306, where the secondary sealing protrusion is omitted from theleg 362, but where theheel portion 365 is received in arecess 324 to locate and restrain thesealing ring 306 in thepiston 302. - The skilled addressee will appreciate the location of the
heel portion 365 in therecess 324 will still enable the line of “rolling-contact” to be maintained between thering body 361 and therecess 324 of thepiston 302; and thefoot 363 remains in sealing contact with thenut body 301; whether or not theleg 362 moves into, or out of, sealing contact with thepiston 302; as the hydraulic pressure on theannular cavity 317 is increased, or decreased. -
FIGS. 10 and illustrate sealingrings FIG. 6 . - The sealing
ring 406 has a ring body 461 with a leg 462 andfoot 463. Thetoe 463A has a relief angle α of e.g. 1°-3° relative to theadjacent wall 413 of thenut body 401. - The
annular bore 423 of thepiston 402 is inwardly tapered in a downwards direction, and theportion 465A of the ring body 461 has a corresponding “taper” down to thecurved heel 465. - As the
heel 465 rolls as the hydraulic pressure is increased, thetoe 463A moves towards full contact with thewall 413 to increase the sealing there-between. This corresponding “taper” allows the seal to be automatically preloaded by the action of pressing components (egFIGS. 2 ; 1 and 22) together, eliminating the need for heating/cooling and introductory tapers on sliding contact faces. - As hereinbefore discussed with respect to the PRIOR ART, previous designs proposed a two part sealing mechanism. The first sealing mechanism was created by the action of the lips of the seal acting against both static and sliding contacts of the seal retaining groove. The second sealing mechanism was then generated by the ability of the seal body to slide to fill and seal the ‘seal extrusion gap’ created as the cylinder wall moved radially outwards in response to increasing hydraulic pressure in the sealed
- The sealing rings of the present invention produce an initial sealing action from the action of spring force generated by slight elastic bending of the sealing ring as it is inserted into place. This bending forces the ‘heel’ of the sealing ring into its respective seat and the ‘sealing edge’ (of the toe) against the cylinder wall. As hydraulic pressure is increased in the sealed chamber, the sealing mechanism will be further enhanced by increasing inner and outer radial thrust generated as the sealing ring flexes and rolls on its ‘heel’ to follow outward radial movement of the cylinder wall. The alternative designs of the embodiments described and illustrated predict and allow a degree of bending of the seal body to continually align the ‘sealing edge’ (of the toe) against the cylinder wall.
- As illustrated in the embodiment of
FIG. 6 , sealing of the (leg of the) sealing ring to the ‘seal carrier’ side of the seal retaining groove can be made in the upper portion (or the leg) of the “L” shape of the seal. - In addition, mechanisms to physically retain the sealing ring can be incorporated as illustrated in
FIGS. 7 to 9 . These mechanisms can also combine a sealing function in the upper portion (or the leg) of the “L” shape of the sealing ring, together with the mechanical location function. - The skilled addressee will appreciate the following additional advantages of the sealing rings of the present invention:
- A) The shape of sealing ring enables easy insertion, to thereby obviate the need for complex assembly procedures.
- B) It is not necessary to have a permanently installed, but loose, insertion ring rattling about inside the hydraulic nut or other hydraulic assembly—the insertion ring is an integral part of this seal construction.
- C) The method of sealing as related to shape of sealing ring. The sealing ring is ‘preloaded’ for use simply by insertion into place. Sealing is then maintained and improved by predicted and controlled flexing of the sealing ring in response to the hydraulic charge pressure.
- D) The reusability of the sealing ring as a function of the design. No part of the sealing ring is overstressed during operation. Therefore, it can be cleaned and reassembled.
- Various changes and modifications may be made to the embodiments described and illustrated without departing from the present invention.
Claims (6)
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
AU2011900324A AU2011900324A0 (en) | 2011-02-02 | High-pressure sealling ring | |
PCT/AU2012/000088 WO2012103586A1 (en) | 2011-02-02 | 2012-02-02 | High-pressure sealing ring |
Related Parent Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/AU2012/000088 A-371-Of-International WO2012103586A1 (en) | 2011-02-02 | 2012-02-02 | High-pressure sealing ring |
Related Child Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US15/829,277 Continuation US10801625B2 (en) | 2011-02-02 | 2017-12-01 | High-pressure sealing ring |
Publications (1)
Publication Number | Publication Date |
---|---|
US20140042714A1 true US20140042714A1 (en) | 2014-02-13 |
Family
ID=46602011
Family Applications (2)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US13/982,789 Abandoned US20140042714A1 (en) | 2011-02-02 | 2012-02-02 | High-pressure sealing ring |
US15/829,277 Active 2033-01-06 US10801625B2 (en) | 2011-02-02 | 2017-12-01 | High-pressure sealing ring |
Family Applications After (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US15/829,277 Active 2033-01-06 US10801625B2 (en) | 2011-02-02 | 2017-12-01 | High-pressure sealing ring |
Country Status (8)
Country | Link |
---|---|
US (2) | US20140042714A1 (en) |
EP (1) | EP2671004B1 (en) |
JP (1) | JP5802765B2 (en) |
KR (2) | KR102002520B1 (en) |
CN (1) | CN103380320B (en) |
AU (1) | AU2012212396B2 (en) |
CA (1) | CA2863581C (en) |
WO (1) | WO2012103586A1 (en) |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN107420542A (en) * | 2016-05-24 | 2017-12-01 | 欧涅斯公司 | High pressure static seals |
USD884130S1 (en) * | 1997-04-15 | 2020-05-12 | Swagelok Company | Back ferrule |
US20210322995A1 (en) * | 2018-10-09 | 2021-10-21 | Technofast Industries Pty. Ltd. | Hydraulic Mantle Assembly System for a Gyratory Rock Crusher |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN108518380B (en) * | 2018-06-01 | 2024-04-30 | 苏州好特斯模具有限公司 | Quick-change three-dimensional cooling hydraulic cylinder |
Citations (13)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3218087A (en) * | 1962-07-09 | 1965-11-16 | Boeing Co | Foot seal |
US4306727A (en) * | 1980-07-24 | 1981-12-22 | Reed Rock Bit Company | Dynamic seal for rolling cutter drill bit |
US4566702A (en) * | 1985-03-18 | 1986-01-28 | W. S. Shamban & Company | Seal assembly with improved low pressure sealing ring |
US5653452A (en) * | 1995-05-16 | 1997-08-05 | Uponor B.V. | Socket joint for plastic pipes |
US20040262845A1 (en) * | 2002-01-21 | 2004-12-30 | Shingo Matsui | Seal device |
US20060012133A1 (en) * | 2004-07-15 | 2006-01-19 | Temper Corporation | Rings for mounting structures to shafts and methods of using such rings |
US20060119047A1 (en) * | 2004-12-07 | 2006-06-08 | Riley William M | Spline shaft seal assembly |
US7252293B2 (en) * | 2005-02-04 | 2007-08-07 | Press-Seal Gasket Corporation | Two-part gasket for pipe-to-pipe connections |
US20090258715A1 (en) * | 2004-07-15 | 2009-10-15 | Temper Corporation | Method of mounting a structure to a shaft |
US7866669B2 (en) * | 2004-09-17 | 2011-01-11 | Nippon Valqua Industries, Ltd. | Composite sealing material |
US20110233925A1 (en) * | 2010-03-25 | 2011-09-29 | Tenaris Connections Limited | Threaded joint with elastomeric seal flange |
US8371585B2 (en) * | 2007-06-13 | 2013-02-12 | Federal-Mogul Burscheid Gmbh | Oil wiper ring |
US8714556B2 (en) * | 2008-12-12 | 2014-05-06 | Flowserve Management Company | Pump seal |
Family Cites Families (21)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB648434A (en) * | 1948-09-01 | 1951-01-03 | Gen Electric Co Ltd | Improvements in or relating to joint-making packing |
US3463044A (en) * | 1967-05-05 | 1969-08-26 | Joseph J Rossman | Hydraulic holding devices |
US3955834A (en) * | 1972-02-11 | 1976-05-11 | Aktiebolaget Svenska Flaktfabriken | Apparatus for connecting ducts with a self-sealing joint |
GB1475312A (en) * | 1973-10-12 | 1977-06-01 | Angus Co Ltd G | Piston or like sealing or packing |
US4121838A (en) * | 1973-11-17 | 1978-10-24 | Nippon Piston Ring Co., Ltd. | Shaft seal structure |
US4262915A (en) * | 1978-04-17 | 1981-04-21 | Commercial Shearing, Inc. | Low friction drag seals |
US4231578A (en) * | 1979-04-23 | 1980-11-04 | W. S. Shamban & Co. | Seal assembly |
FR2501322A1 (en) * | 1981-03-05 | 1982-09-10 | Mdpa | ANNULAR SEAL WITH SEVERAL FUNCTIONS USED IN SMOOTH AXIS AND CONCENTRIC CYLINDER DEVICES |
JPS57167563A (en) * | 1981-04-06 | 1982-10-15 | Nissan Motor Co Ltd | Sealing device |
US4421330A (en) * | 1982-02-08 | 1983-12-20 | Greene, Tweed & Co., Inc. | Antifriction fluid seal assembly |
ATE108360T1 (en) * | 1987-09-29 | 1994-07-15 | John Wentworth Bucknell | POWER GENERATOR. |
AUPO076596A0 (en) * | 1996-07-02 | 1996-07-25 | Bucknell, John Wentworth | Seals for hydraulic assemblies |
NL1012801C2 (en) * | 1999-08-10 | 2001-02-23 | Ihc Holland Nv | Bulkhead lead-through, such as in particular for passing a propeller shaft through a watertight bulkhead. |
AU2002352942A1 (en) * | 2001-11-30 | 2003-06-17 | Westinghouse Electric Company Llc | Method of closing a pressure vessel |
US20110068543A1 (en) * | 2004-02-25 | 2011-03-24 | John Wentworth Bucknell | Seals for Hydraulic Assemblies |
US8556557B2 (en) * | 2004-07-08 | 2013-10-15 | Gordon Britton | Hydraulic nut and improved seals therefor |
US7341258B2 (en) * | 2004-09-24 | 2008-03-11 | Greene, Tweed Of Delaware, Inc. | Cammed seal assembly with sealing ring having an angled leg portion and foot portion with elastomeric energizer element |
FR2890717B1 (en) * | 2005-09-15 | 2007-11-23 | Aldes Aeraulique Sa | ANNULAR JOINT SEAL FOR CONNECTING FLUID CIRCULATION PIPES, SUCH AS AIR DUCTS |
GB0718993D0 (en) * | 2007-09-28 | 2007-11-07 | Ge Healthcare Bio Sciences Ab | Sealing assembly for a chromatography column |
DE102009022334B4 (en) * | 2009-05-13 | 2023-01-05 | Parker Hannifin Gmbh | Gasket with L-shaped cross-section |
WO2013131132A1 (en) * | 2012-03-06 | 2013-09-12 | Technofast Industries Pty Ltd | High-capacity radial fit coupling bolts |
-
2012
- 2012-02-02 KR KR1020197003905A patent/KR102002520B1/en active IP Right Grant
- 2012-02-02 US US13/982,789 patent/US20140042714A1/en not_active Abandoned
- 2012-02-02 CA CA2863581A patent/CA2863581C/en active Active
- 2012-02-02 WO PCT/AU2012/000088 patent/WO2012103586A1/en active Application Filing
- 2012-02-02 KR KR1020137023209A patent/KR20140044301A/en active Search and Examination
- 2012-02-02 JP JP2013552064A patent/JP5802765B2/en active Active
- 2012-02-02 EP EP12742478.6A patent/EP2671004B1/en active Active
- 2012-02-02 CN CN201280007570.2A patent/CN103380320B/en active Active
- 2012-02-02 AU AU2012212396A patent/AU2012212396B2/en active Active
-
2017
- 2017-12-01 US US15/829,277 patent/US10801625B2/en active Active
Patent Citations (14)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3218087A (en) * | 1962-07-09 | 1965-11-16 | Boeing Co | Foot seal |
US4306727A (en) * | 1980-07-24 | 1981-12-22 | Reed Rock Bit Company | Dynamic seal for rolling cutter drill bit |
US4566702A (en) * | 1985-03-18 | 1986-01-28 | W. S. Shamban & Company | Seal assembly with improved low pressure sealing ring |
US5653452A (en) * | 1995-05-16 | 1997-08-05 | Uponor B.V. | Socket joint for plastic pipes |
US20040262845A1 (en) * | 2002-01-21 | 2004-12-30 | Shingo Matsui | Seal device |
US20090258715A1 (en) * | 2004-07-15 | 2009-10-15 | Temper Corporation | Method of mounting a structure to a shaft |
US7563050B2 (en) * | 2004-07-15 | 2009-07-21 | Temper Corporation | Rings for mounting structures to shafts and methods of using such rings |
US20060012133A1 (en) * | 2004-07-15 | 2006-01-19 | Temper Corporation | Rings for mounting structures to shafts and methods of using such rings |
US7866669B2 (en) * | 2004-09-17 | 2011-01-11 | Nippon Valqua Industries, Ltd. | Composite sealing material |
US20060119047A1 (en) * | 2004-12-07 | 2006-06-08 | Riley William M | Spline shaft seal assembly |
US7252293B2 (en) * | 2005-02-04 | 2007-08-07 | Press-Seal Gasket Corporation | Two-part gasket for pipe-to-pipe connections |
US8371585B2 (en) * | 2007-06-13 | 2013-02-12 | Federal-Mogul Burscheid Gmbh | Oil wiper ring |
US8714556B2 (en) * | 2008-12-12 | 2014-05-06 | Flowserve Management Company | Pump seal |
US20110233925A1 (en) * | 2010-03-25 | 2011-09-29 | Tenaris Connections Limited | Threaded joint with elastomeric seal flange |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
USD884130S1 (en) * | 1997-04-15 | 2020-05-12 | Swagelok Company | Back ferrule |
CN107420542A (en) * | 2016-05-24 | 2017-12-01 | 欧涅斯公司 | High pressure static seals |
US20210322995A1 (en) * | 2018-10-09 | 2021-10-21 | Technofast Industries Pty. Ltd. | Hydraulic Mantle Assembly System for a Gyratory Rock Crusher |
US11969738B2 (en) * | 2018-10-09 | 2024-04-30 | Technofast Industries Pty. Ltd. | Hydraulic mantle assembly system for a gyratory rock crusher |
Also Published As
Publication number | Publication date |
---|---|
JP2014508900A (en) | 2014-04-10 |
JP5802765B2 (en) | 2015-11-04 |
KR102002520B1 (en) | 2019-07-23 |
CA2863581C (en) | 2019-04-02 |
KR20190018029A (en) | 2019-02-20 |
EP2671004A1 (en) | 2013-12-11 |
US20180080565A1 (en) | 2018-03-22 |
CN103380320B (en) | 2016-06-15 |
AU2012212396B2 (en) | 2016-11-03 |
EP2671004B1 (en) | 2020-04-22 |
US10801625B2 (en) | 2020-10-13 |
EP2671004A4 (en) | 2017-02-08 |
KR20140044301A (en) | 2014-04-14 |
CA2863581A1 (en) | 2012-08-09 |
WO2012103586A1 (en) | 2012-08-09 |
CN103380320A (en) | 2013-10-30 |
AU2012212396A1 (en) | 2013-09-05 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
US10801625B2 (en) | High-pressure sealing ring | |
CN101625026B (en) | Resilient high pressure metal-to-metal seal and method | |
CA2685398C (en) | Threaded joint with pressurizable seal | |
KR102502375B1 (en) | Gaskets and Fluid Couplings for Fluid Couplings | |
CN209925622U (en) | Sealing washer and sealed frock of nodular cast-in-place pipe pressure testing | |
CN103016867A (en) | Combined gasket | |
US10359135B2 (en) | Gasket for quick couplers and quick coupler comprising said gasket | |
US9239114B2 (en) | Compressable sealing ring assembly | |
KR101289874B1 (en) | A ball valve with a seat contacting structure using an elastic means and a flowing liquid pressure | |
US20170089162A1 (en) | External Locking Mechanism for Seal Energizing Ring | |
US9816614B2 (en) | Seals for hydraulic assemblies | |
CA2964040A1 (en) | Assembly for compressing a ball-valve seat | |
CN107061781A (en) | A kind of double graphite hard seal ball valves of low torque all-metal | |
US20220390015A1 (en) | Under-Balanced Seal Ring | |
US2409764A (en) | Piston ring | |
RU77934U1 (en) | ROTARY PIPELINE CONNECTION | |
CN104390021A (en) | Wet chlorine special valve | |
RU2280210C1 (en) | Detachable joint | |
CN113550710A (en) | Metal sealing element for wellhead of deepwater Christmas tree |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
AS | Assignment |
Owner name: TECHNOFAST INDUSTRIES PTY LTD, AUSTRALIA Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:BUCKNELL, JOHN WENTWORTH;REEL/FRAME:031401/0237 Effective date: 20131011 |
|
AS | Assignment |
Owner name: TECHNOFAST INDUSTRIES PTY LTD, AUSTRALIA Free format text: CORRECTIVE ASSIGNMENT TO CORRECT THE SUPPORTING ASSIGNMENT DOCUMENT PREVIOUSLY RECORDED ON REEL 031401 FRAME 0237. ASSIGNOR(S) HEREBY CONFIRMS THE ASSIGNMENT;ASSIGNOR:BUCKNELL, JOHN WENTWORTH;REEL/FRAME:044717/0625 Effective date: 20131011 |
|
STCB | Information on status: application discontinuation |
Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION |