Classifications

• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
  • B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
  • B21D39/00—Application of procedures in order to connect objects or parts, e.g. coating with sheet metal otherwise than by plating; Tube expanders
  • B21D39/04—Application of procedures in order to connect objects or parts, e.g. coating with sheet metal otherwise than by plating; Tube expanders of tubes with tubes; of tubes with rods
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
  • B25B—TOOLS OR BENCH DEVICES NOT OTHERWISE PROVIDED FOR, FOR FASTENING, CONNECTING, DISENGAGING OR HOLDING
  • B25B27/00—Hand tools, specially adapted for fitting together or separating parts or objects whether or not involving some deformation, not otherwise provided for
  • B25B27/02—Hand tools, specially adapted for fitting together or separating parts or objects whether or not involving some deformation, not otherwise provided for for connecting objects by press fit or detaching same
  • B25B27/10—Hand tools, specially adapted for fitting together or separating parts or objects whether or not involving some deformation, not otherwise provided for for connecting objects by press fit or detaching same inserting fittings into hoses

Definitions

• the present invention relates generally to apparatus for pressing fittings to 5 connect sections of pipe and, more particularly, apparatus for use in pressing such fittings.
• a compression fitting is typically a tubular sleeve containing seals.
• the fitting is compressed in radial directions to engage the ends of pipes.
• the io compression fittings form a leak resistant joint between the pipe ends.
• the joint has considerable mechanical strength and is self-supporting.
• a pressing tool is used.
• Pressing tools typically include a press tool containing a hydraulic cylinder with a piston and apparatus for converting the movement of the piston into forces that is are applied to a press fitting in order to press the fitting to the pipe segments to be joined.
• a press jaw is coupled to the press tool and the press jaw is placed about the fitting to be pressed.
• the hydraulic piston in the press tool will typically include rollers that roll along a linear path when the piston is actuated to contact arms of the press jaw.
• piston will move a fixed distance along a linear path to press the piston with its rollers against the arms.
• the rollers engage ends of the jaws in line engagement and cause them to pivot and press the compression fitting disposed between the jaws.
• An example of a press tool including a press jaw is provided in Figures 1 and 2.
• press rings or press slings are often used to facilitate the pressing operations.
• a press ring is placed about the fitting to be pressed and a press ring actuator is coupled to the press tool.
• the press ring actuator is similar to a press jaw, in that it includes
• pressing tools are designed such that each activation of the tool results in movement of the hydraulic piston along a fixed distance path.
• the linear distance the piston moves for a given tool is often referred to as the "stroke" of the tool.
• the force output of the piston as it moves along the stroke will depend on the sizing, geometry and other characteristics of the hydraulic cylinder and piston.
• the maximum amount of "work" output that a pressing tool can provide during a single stroke of the piston will correspond to the force output of the tool multiplied by the distance traveled by the piston upon actuation of the tool.
• the typical maximum work output from a tool capable of providing 32kN of force with a piston travel of 40 mm will be 1.280kN-m.
• it is not possible to utilize 100% of the maximum theoretical work output due to inherent system limitations such as clearance and combined tolerances between multiple components and operating conditions required to allow jaws to open with rollers retracted which can be on the order of 1.5 mm of wasted stroke.
• the present disclosure is directed to apparatus that allow press tools to efficiently and easily press fittings when the work required to press the fitting is greater than the work produced upon a single actuation of the press tool.
• the present disclosure is directed toward an apparatus allowing a press tool assembly to readily and easily press a fitting when the work required to press the fitting is greater than the work produced upon a single actuation of the tool or where a multi-step press is desired.
• FIGS 1 and 2 generally illustrate an exemplary pressing tool assembly 10, including a pressing tool 12 and a jaw assembly 14, constructed in accordance with certain teachings of the disclosure.
• Figure 3 generally illustrates the use of a press ring assembly to accomplish a press.
• Figure 4 illustrates a first exemplary press actuator assembly that may facilitate pressing where multiple actuations of a pressing tool are required.
• Figure 5 illustrates a cut-away view of an exemplary press ring assembly 50, and an actuator jaw 52 constructed in accordance with certain teachings of this disclosure to easily enable multi-step press operations.
• Figure 6, 7, 8A, 8B, 9, 10 and 11 generally illustrate alternate press ring assemblies that may be used to facilitate multi-step pressing.
• Figure 12 illustrates an exemplary pressing actuator assembly that uses a pin with an eccentric to enable multi-step pressing operations.
• Figure 13 illustrates a set of actuator jaws 130 that may be of beneficial use with respect to the press rings assemblies reflected in Figures 6-11 above, as well as other press rings assemblies, that include ramps designed to control the forces generated by the jaws.
• Figure 14 illustrates a press ring interlock concept that may be used with any multi-step press rings assemblies including, but not limited to the multi-step press rings assemblies discussed above in connection with Figures 6-11.
• Figure 15A and 15B illustrate a press ring assembly 150 that is particularly suited for multi-step pressing operations involving separate retention and seal bead press.
• Figure 16 illustrates a press ring assembly 160 that is similar to that previously described in connection with Figure 15A and 15B that tends to ensure that a seal bead press is performed prior to any retention presses.
• Figures 17A and 17B illustrates a press ring assembly 170 that is similar to that previously described in connection with Figure 15A and 15B that tends to ensure that the retention presses are preformed prior to the seal bead press.
• Figures 18A and 18B generally illustrates a hydraulic force multiplying device 180 that may be used to engage a press allowing a press tool to press a fitting when the work required to press the fitting is greater than the work produced upon a single actuation of the tool.
• the assembly 10 includes a pressing tool 12 and a jaw assembly 14.
• the press tool 12 comprises a generally gun-shaped device that includes a hydraulically actuated piston assembly (not shown in Figures 1 or 2) that is used to actuate the jaw assembly 14 in a manner known to those of ordinary skill in the art.
• the press tool 12 may be battery or cord powered. Examples of known press tools that may be used to practice the subject matter of the present disclosure include the Model CT-400 and Model 320-E press tools available from Ridge Tool Company.
• Figure 2 generally illustrates a side cutaway view of the assembly 10 depicted in Figure 1.
• the jaw assembly 14 defines at its peripheral end an opening 34 that is sized and shaped to engage a press fitting and to result in pressing of such fitting when the jaw assembly 14 is actuated.
• the press tool 12 includes a hydraulically actuated piston assembly 30 that includes rollers 32A and 32B.
• the hydraulically activated piston assembly 30 When the press tool 14 is activated, e.g., through the depression of a trigger or switch, the hydraulically activated piston assembly 30 will be moved towards the jaw assembly 14 along a path of travel causing the rollers 32A ad 32B to engaged the distal end of the jaws 16A and 16B, resulting in a closing of the jaws 16A and 16B and, if a press fitting was positioned in opening 34, a pressing or a partial pressing of the fitting.
• Figure 3 generally illustrates the use of a press ring assembly to accomplish a press connection.
• the pressing tool 12 is coupled to a press ring actuator assembly 30.
• the press ring actuator assembly is similar in construction to the press jaws 14 discussed above, with the primary difference being that the arms of the press ring actuator assembly 30 are designed to interface with the press ring assembly 32.
• press ring assembly 32 is formed of two generally half-round shaped sections that are coupled together at a pivot point. In operation, the press ring assembly 32 is placed about a press fitting 35 to be pressed, the tips of press ring actuator assembly 30 are placed within notches formed on the press ring assembly 32 and the pressing tool 12 is actuated. Actuation of the pressing tool causes movement of the arms of the press ring actuator assembly 30 and compression of the press ring assembly 32 and the fitting 35 about which it is placed.
• the press operation may not be completed using the same press tool, press ring actuator assembly, and press ring assembly without adjustments.
• the present disclosure provides for adjustable engagement surfaces of the press ring actuator assembly, press ring assembly, or a combination thereof that effectively adjusts spacing between the compression portions of the members that allow further compression with the same stroke of the press tool. The adjustments are used to obtain an increased work quantity beyond the normal capabilities of the members without the adjustments.
• FIG. 4 illustrates an exemplary press ring actuator assembly that may facilitate pressing where multiple actuations of the pressing tool are required.
• a press ring actuator assembly 40 is illustrated.
• the ring actuator assembly 40 is constructed, in general, in accordance with known practices for press ring actuator assemblies with the primary exception being that the press ring actuator assembly 40 includes replaceable tips 42.
• the replaceable tips include a first set of tips 42, having a particular geometry and construction and a second pair of tips 43 including a second geometry and construction that differs, in at least one respect from that of the first set.
• the replaceable tips are sized differently, the manner in which they interface with the press ring assembly will differ and it is possible to efficiently use the press ring actuator assembly of Figure 4 to readily perform a two-step pressing operation.
• the first set of tips 42 could be used to perform an initial press operation through use of the press ring actuator assembly 40 and a press ring assembly and a press tool in a conventional manner.
• the press ring actuator assembly 40 could then be removed from the press ring, the tips 43 could be substituted for tips 42, and the pressing tool could be coupled to the press ring assembly through the modified press ring actuator assembly 40. Actuation of the press tool a second time could then provide the necessary additional work to complete the press operation.
• the first step could be completed with two identical actuator tips 42 installed.
• one actuator tip could be replaced with a tip of a different geometry 43 and the second step completed.
• a third step could be completed using two identical actuator tips 43. Additional steps could be accomplished using more replaceable tips with differing geometry similar to the tips 43.
• the tips 42 and 43 are coupled to the actuator jaws via an interference fit assembly including a recessed opening in the arms of the actuator assembly 40 (not shown) that receives a projection extending from the tips 42 and 43.
• an interference fit assembly including a recessed opening in the arms of the actuator assembly 40 (not shown) that receives a projection extending from the tips 42 and 43.
• Figure 5 illustrates an alternate approach to facilitating rapid and convenient "two-step” pressing and in generally multi-step pressing.
• Figure 5 illustrates a cut-away view of an exemplary press ring assembly 50, and a press ring actuator assembly 52 constructed in accordance with certain teachings of this disclosure.
• the press ring assembly 50 is constructed in accordance with known techniques for constructing press ring assemblies.
• the recess in which the press ring actuator assembly is typically received includes two pin-like elements 54a and 54b.
• the tip of the jaws of the actuator assembly 52 is constructed so as to engage one of the elements 54a or 54b.
• a first pressing operation may be performed by having the press ring actuator assembly 52 engage the press ring assembly 50 at element 54a, and then after the tool to which actuator assembly 52 is coupled is actuated a first time, the tip of the press ring actuator assembly 52 may be repositioned to engage element 54b to provide a second pressing operation.
• a multi-step pressing operation may be easily facilitated, as little in the way of complex operator action is required.
• additional pin like elements 54A and 54B could be added to the assembly allowing a three or more step press process.
• Figure 6 illustrates an alternate press ring assembly 60 that may be used to facilitate multi-step pressing.
• the press ring assembly 60 includes recesses 62a and 62b for receiving the tips of a conventional press ring actuator. Positioned with the recesses 62a and 62b are movable elements 64a and 64b that can be rotated to fixed positions to adjust the geometries of the recess and the manner in which the pressing actuator engages the ring assembly 60. In this manner, the press ring may be configured for a first press operation by positioning the movable members 64a and 64b at a first position and then reconfigured for subsequent operations through movement or adjustment of the members 64a and 64b. [0032] It should be noted that the inner diameter profile 65 of the ring assembly 60 is machined to work with a particular press fitting.
• This inner diameter contour can be machined in a variety of shapes depending on the fitting being crimped.
• the contour could include provisions to press both the seal bead and retention press areas of the fitting simultaneously.
• the concept of a profiled inner diameter can be applied to all of the press rings discussed herein.
• Figure 7 illustrates an alternate embodiment to that of Figure 6.
• a press ring assembly 70 is illustrated that includes recesses 72a and 72b and movable members 74a and 74b.
• the movable members 72a and 72b may be adjusted to change the geometry of the recesses 72a and 72b to facilitate multi-step pressing operations.
• the movable members 74a and 74b are adjusted though linear movement (e.g., sliding).
• Figures 8A and 8B illustrate yet further embodiments in which the geometry of the recess in which the jaws of a press ring actuator assembly are received by a press ring assembly to facilitate multi-step pressing operations.
• movable elements defining surfaces for receiving the tips of the press ring actuator can be rotated into and out of a fixed position such that the press ring assembly can be operated in one configuration where the tip of the actuator assembly is received by the press ring assembly, but not the movable elements, and a second configuration where portions of the movable elements receive the jaws of the press ring actuator assembly.
• FIG. 8A illustrates yet another embodiment of movable elements where a press ring assembly 90 is provided with slidable elements 94a and 94b located in recesses 92a and 92b which move into positions to change the manner in which the press ring assembly 90 interfaces with a press ring actuator assembly applied to the ring assembly 90.
• Figure 10 illustrates an exemplary press ring assembly 100 having an alternative design of movable elements.
• the illustrated ring assembly includes movable elements 102a and 102b, each of which includes a recess 104a and 104b for receiving the tip of a press ring actuator assembly.
• the elements 102a and 102b are coupled to the main portions of press ring 100 via a ratcheting mechanism 106a and 106b.
• the positions of the elements 102a and 102b may be adjusted between pressing steps to change the manner in which the actuator jaws interface with the ring assembly 100. In this manner, multi-step presses are readily enabled.
• a release mechanism constructed in accordance with known techniques, may be provided to allow readjustment of the movable elements 102a and 102b.
• Figure 11 illustrates a press ring assembly 110 that includes recesses 112a and 112b for receiving tips of a press ring actuator.
• the two main sections of the press ring assembly 110 are coupled together by an adjustable hinge element 114 that includes a pin 116 having an eccentric cross section.
• the pin 116 is adjustable such that the point about which the two main elements of the press ring assembly 110 rotate relative to one another may be changed, depending on which position the pin 116 is placed.
• the press ring assembly may be configured to operate in a first configuration for a first press operation and then pin 116 may be repositioned to change the configuration of the ring assembly 110 for a subsequent press operation.
• Figure 12 illustrates a press ring actuator assembly 120 that, like the press ring assembly 110, uses a pin with an eccentric to enable multi-step pressing operations.
• the arms of the actuator are coupled together at two hinge points 122 A and 122B.
• Each hinge point includes a pin with an eccentric 124, where the pin can be adjusted to change the configuration of the press ring actuator assembly.
• a coupling element 126 is used to ensure that the pins associated with hinge points 122A and 122B rotate in tandem.
• Figure 13 illustrates a set of actuator jaws 130 that may be of beneficial use with respect to the press rings assemblies reflected in Figures 6-11 above, as well as other press ring assemblies.
• each of the press rings reflected in Figures 6-11 may be adjusted to provide multiple configurations such that the manner in which actuator arms engage the press rings is adjustable.
• the same set of press ring actuator assemblies may be beneficially used to perform a press operation in the various configurations.
• the actuator assembly 130 of Figure 13 attempts to accomplish this result by providing multiple cam elements 131 and 132 with the cam elements serving as locations where the rollers of a hydraulic piston will interact with the actuator assembly 130.
• Figure 14 illustrates a press ring interlock concept that may be used with any multi-step press ring assembly including, but not limited to the multi-step press ring assemblies discussed above in connection with Figures 6-11.
• the interlock feature involves the incorporation of a ratcheting mechanism 140 into the press ring assembly.
• the ratcheting assembly includes a toothed surface 142 formed on one of the main members of the press ring and a pivotable cog 144 coupled to another of the main member of the press ring.
• the cog is spring biased to engage the toothed surface 142.
• an engagement element of the cog 144 will move within the toothed surface 142 and tend to preclude the press ring assembly from re ⁇ opening once an initial press operation is completed.
• the press ring assembly will be "locked on” to the press fitting and not removable (absent manual release of the cog). This locking on may prevent users of any multi-step ring assembly including the same from completing the press operation.
• the cog 144 is configured and biased, and the toothed surface 142 is sized, such that, upon completion of the pressing processes, the cog will automatically disengage and allow opening and removal of the press ring assembly.
• the ratcheting mechanism 140 is repeated on both sides of the illustrated press ring assembly. Alternate embodiments are envisioned where the ratcheting mechanism is located on only one side of the press ring assembly.
• a pressing operation is performed wherein the pressing process is broken down into two or more discrete steps including at least one step where a press is performed to provide a retention press to retain the fitting on the pipe to which the fitting is applied and where at least one press is performed to press the seal bead to provide a snug seal.
• Figure 15A and 15B illustrate a press ring assembly 150 that is particularly suited to this fo ⁇ n of multi-step pressing.
• a press ring assembly is illustrated that includes six generally half-round shaped segments 152A-1, 152A-2, 152B-1, 152B-2, 152C-1 and 152C-2 forming multiple press ring sections coupled together to pivot about a common point 154.
• Each of the half-round shaped segments defines a pocket sized to receive the tips of a pair of actuator arms.
• the ring assembly 150 is sized and designed such that, in use, the ring assembly will be placed over a fitting to be pressed.
• segments 152A-1 and 152A-2 When so positioned, the segments 152A-1 and 152A-2 will be positioned over a part of the fitting to provide an initial retention press to one of the pipe elements to be coupled by the fitting; segments 152B-1 and 152B-2 will be positioned to press an area of the fitting to provide a sealing press of a seal bead; and segments 152C-1 and 152C-2 are positioned so as to provide a retention press for another pipe element to be coupled by the fitting.
• the tips of a pair of actuator jaws will be positioned within the pockets defined by segments 152A-1 and 152A-2 and the tool to which the jaws are coupled will be activated, thus producing a retention press securing the fitting at issue to one of the pipe elements to be coupled.
• the tool will then be moved such that the tips of the actuator arms are positioned in the pockets defined by segments 152B-1 and 152B-2 and the tool will be actuated providing a seal bead press.
• the tips of the actuator jaws will be moved to the pockets defined by segments 152C-1 and 152C-2 and actuated for a third time, providing a second retention press.
• press ring assembly 150 of Figures 15A and 15B is intended for use with press fittings that have areas for retention press located on both sides of the fitting a seal bead area positioned between the two areas for retention press. It should also be understood that additional half round pairs of ring sections could be added axially to accommodate other fitting designs requiring multiple retention press or seal bead locations allowing for multiple step crimping. Also, certain fittings may require rearrangement of the half round pairs. For example, a fitting could require retention presses side-by-side and a seal bead at the axial end of the fitting such as fittings available currently from Mapress or Yorkshire.
• the press for the seal bead was performed after a first retention press was completed. It should be understood that the described process was exemplary only and that other processes could be followed. For example, processes are envisioned wherein the seal bead press is performed first and the retention press are performed last or where the two retention presses are completed first and the bead seal press is performed as the last pressing operation.
• Figure 16 illustrates a press ring assembly 160 that is similar to that previously described in connection with Figure 15A and 15B.
• the outer segments 162A-1, 162A-2, 162C-1 and 162C-2 of ring sections are designed with notched segments 164, 165 and corresponding notched segments not illustrated in Figure 16 located on segments 162A-2 and 162C-2, that interface with the intermediate segment 162B-1 and 162B-2 to ensure that the center press operation (the seal bead press) must be performed first, that is, in sequence.
• the arrangement of the notches 164 and 165 is such that any attempts to provide a press using one of the outer segment pairs (162A-1 and 162A-2 or 162C-1 and 162C-2) prior to the completion of a press with the intermediate segment pair 162B-1 and 162B-2 will result in a failed press that should be visibly apparent to the user of the ring assembly or for which the tool will provide a indication to the user of a failed press.
• the failed press is ensured by the fact that the notches 164 and 165 (and the corresponding notches on the underside of the ring) are designed so that activation of the outer segments before activation of the intermediate segments will result in an engagement of the outer segments with the intermediate segments and, as such, a press of the outer segments before the press of the inner segments are complete will result in the actuator tool attempting to perform two pressing operations. Because, in the applications for which the ring assembly 160 will be used, the work output of the tool is insufficient to perform two press operations, the attempted press operation will fail. If the intermediary press is performed first, the intermediate segments 162B-1 and 162B-2 will tend to be closed or partially closed as a result of the deformation of the press fitting in that area.
• the ring assembly 160 provides a structure that tends to ensure that the intermediate press is performed in sequence prior to the completion of the external press.
• Figures 17A and 17B illustrate a press ring assembly similar to that discussed above in connection with Figures 15 A, 15B and 16.
• FIGS 17A and 17B is designed to ensure that the outer press operations
• the inner segments 172B-1 and 172B-2 are constructed with outwardly extending notched areas 174 and 175 that are designed to mate with a corresponding notched area on the outer segments 172A-1, 172A-2,
• the press ring assembly 170 tends to ensure that the outer press operations are performed prior to the pressing operation of the center press.
• the full work output of the tool with which the ring assembly 170 is used may be utilized, hi such a design, the work to press the fitting is not divided into three equal pieces, but rather into a first partial press operation, a second partial press operation and a third operation that not only results in a full third press operation, but also completes the first and second press operations.
• Figures 18A and 18B generally illustrates another device 180 that may be used to engage a press allowing a press tool to press a fitting when the work required to press the fitting is greater than the work produced upon a single actuation of the tool, hi general, Figures 18A and 18B illustrates a hydraulic force multiplier 180 that includes a first end 181 and a second end 182.
• the first end 181 is adapted for attachment to the end of a standard press tool and includes a first piston 183 within a first hydraulic cylinder that is moved by the piston of the press tool (not illustrated).
• Actuation of the press tool will cause the first piston 183 to move a distance corresponding the stroke of the tool and will force hydraulic fluid through a first check valve 184 into a second hydraulic cylinder.
• the introduction of fluid into the second hydraulic cylinder will cause a second piston 185 to move along a second stroke.
• the apparatus of Figures 18A and 18B will cause the second piston 185 to travel a stroke that is greater than the stroke of the pressing tool, resulting in a work output of the combined assembly of the pressing tool and the apparatus of Figures 18A and 18B that exceeds the maximum work output available from a single actuation of the press tool.
• the apparatus of Figures 18A and 18B is easy to use because, once the user starts the press operation with an initial actuation of the press tool the press tool will likely be locked on the press fitting until the pressure in the second cylinder is manually relieved or until the press is completed. Also, once the user starts the press, the user can keep their hands in one place; the only movement required of the user would be reactivation of the press tool (e.g., by pulling the trigger on a "gun-type" tool).
• both the first and the second pistons 183 and 185 are spring biased to return to a fixed starting point when the pressure behind the cylinder is relieved.
• a kick down relief valve 186 is provided to allow the second cylinder to automatically retract when the pressure in the second cylinder corresponds to a work output sufficient to achieve the desired pressing results.
• a similar kick down valve could be provided for the first cylinder. In place of kick down relief valves, standard relief valves could also be used with manual relief.
• the second cylinder is shown having both a diameter that is larger than that of the first cylinder and a stroke that is longer than that of the first cylinder.
• the effective work out form the pressing tool after multiple actuations of the tool is increased both because the force from the tool is effectively increased and because the stroke of the tool is increased.
• Alternate embodiments are envisioned where only the force or only the stroke are increased.
• the apparatus of Figures 18A and 18B has the potential benefit of enhancing the effective operation of a tool through the use of feedback sensors and the like.
• pressure and/or other sensors could be added to apparatus of Figures 18A and 18B to measure the pressure in the first and/or second cylinders and/or the actual travel of the first and/or second pistons.
• Such information could be provided external to the apparatus for use in confirming and/or diagnosing the pressing process.
• an "instrumented" element could convert a non-instrumented tool into instrumented tool.
• FIG. 18A and 18B A still further advantage the apparatus of Figures 18A and 18B is that it allows the use of main actuators other than a standard press tool to attain a desirable press.
• actuating elements other than a press tool could be used to achieve the desired movement of the first piston.
• Embodiments are envisioned where a feed screw was used to move the first piston.
• Such alternate embodiments could allow for the use of press fittings in situations where the costs of a full pressing tool are not justified and/or in situations where electricity is not available and/or undesirable to use.

Landscapes

• Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• Automatic Assembly (AREA)
• Press Drives And Press Lines (AREA)
• Manufacturing Of Electrical Connectors (AREA)
• Wire Processing (AREA)

Applications Claiming Priority (2)

Publications (1)

Family

ID=36000972

Family Applications (1)

Country Status (8)

Cited By (1)

Families Citing this family (16)

Family Cites Families (11)

• 2005
  • 2005-11-21 RU RU2007122629/02A patent/RU2007122629A/ru not_active Application Discontinuation
  • 2005-11-21 US US11/568,074 patent/US20080216543A1/en not_active Abandoned
  • 2005-11-21 EP EP05824980A patent/EP1838498A1/de not_active Withdrawn
  • 2005-11-21 CA CA002587769A patent/CA2587769A1/en not_active Abandoned
  • 2005-11-21 JP JP2007543350A patent/JP2008521612A/ja not_active Withdrawn
  • 2005-11-21 WO PCT/US2005/042151 patent/WO2006057962A1/en active Application Filing
  • 2005-11-21 CN CNA2005800403266A patent/CN101068660A/zh active Pending
  • 2005-11-23 TW TW094141041A patent/TWI288059B/zh active

Non-Patent Citations (1)

Also Published As

Similar Documents

Legal Events