The present invention pertains to shock and vibration dampers, and in particular to a hydraulic shock absorber having regressive characteristics.
Vehicles that traverse a roadway must deal with irregularities in the roadway such as bumps and depressions. Many wheeled vehicles incorporate damped suspensions. The damping force levels are usually a compromise between low speed damping support of the vehicle body movements and high speed damping of bumps and depressions. Too much low speed damping for improved body control can result in a harsh ride at higher speeds with hydraulic dampers, because the hydraulic damping force is a function of the velocity of the piston and this force typically increases as the velocity increases.
What is needed is a damper that provides adequate low speed damping for improved body control, without increasing the harshness of the vehicle ride at higher speeds. The present invention does this in novel and unobvious ways.
The present invention pertains to improvements in gas and fluid dampers that provide a regressive damping characteristic in both compression and extension. One aspect of some embodiments of the apparatus is to produce a damping characteristic during damper movement in one direction in which the resistance created at low shaft velocities is greater than the damping resistance created at higher shaft velocities. In some embodiments, this regressive characteristic (in which the damping force at a high velocity is lower than the damping force at a low velocity) occurs in compression of the shock absorber, whereas in other embodiments this characteristic occurs in extension or rebound. Some embodiments of the present invention pertain to hydraulic dampers that include a hydraulic switching device that increases the flow area of a restriction in an internal flowpath during moderate velocity operation. The flow area is not increased during low velocity operation, and the increased flow area is maintained during high velocity operation.
Yet another embodiment of the present invention pertains to a damper having multiple flowpaths in parallel across the main piston of the damper. The first flowpath includes multiple fixed restrictions. The second flowpath includes one or more one-way valves. A first, higher pressure drop fixed restriction provides fluid communication during all compression operation of the damper. A second, lower pressure drop restriction is operative above a predetermined pressure differential across the main piston.
Yet another embodiment of the present invention pertains to a hydraulic damper including a first piston slidable within a first housing, and a second piston slidable within a second housing, the second housing being located within one of the chambers defined by the first piston. The second piston is operable to create multiple flowpaths between the volume defined by the first piston, with one flowpath being more restrictive than another flowpath.
Yet another embodiment of the present invention pertains to a hydraulic damper including a first piston slidable within a first housing, and a second piston slidable within a second housing, the second housing being located within one of the chambers defined by the first piston. The second piston is biased to a position by a spring, and slides between two positions based on the pressure drop across the second piston.
Yet another embodiment of the present invention pertains to a retrofit kit for a hydraulic damper. The kit includes a housing that can be coupled to either the piston or rod of the damper. The housing includes a piston slidable within an interior chamber. A spring biases the piston toward one end of the chain.
Yet another embodiment of the present invention pertains to an assembly for modifying the damping characteristics of a shock absorber. In one embodiment, the apparatus is located within a housing that is not within the cylindrical body of the shock absorber. This housing includes an inner valve assembly, the valve assembly containing a spring loaded poppet or piston. The piston or poppet is slidable relative to the inner housing in which it is located. One end of the housing has a fluid port that is in fluid communication with the inlet of the valve housing. Preferably, the housing further includes a second fluid port that is in fluid communication with the outlet of the valve housing. The piston and valve housing coact to form at least two flowpaths from the inlet to the outlet. Preferably, the first, at-rest position of the valve housing relative to the piston provides a first, more restrictive flowpath from inlet to outlet. In yet other embodiments, the second position of the piston relative to the valve housing opens a second, additional flowpath from inlet to outlet. The inlet and outlet are in fluid communication with different ones of the rebound volume or compression volume within the cylinder, and can therefore provide, in one orientation of the assembly, a regressive force characteristic during rebound, and in the opposite orientation provide a regressive force characteristic in compression.
Yet another embodiment of the present invention pertains to a head valve for a shock absorber, the head valve including a valve assembly that provides regressive forcing characteristics. Preferably, the head valve including the valve assembly are mounted on one end of the fluid and nitrogen reservoir that compensate for hydraulic fluid expansion, hydraulic volume displaced by the central rod, or other characteristics.
In yet another embodiment of the present invention, there is an externally adjustable valve that provides the user one or more adjustments by which a regressive forcing characteristic can be modified without taking the shock absorber apart. In one embodiment, there is a first adjustment that changes the preload on a spring that biases a piston toward a first position. In some embodiments, there is a second adjustment that modifies the higher velocity portion of the regressive forcing characteristic. In some embodiments, there is a third adjustment that modifies the lower velocity portion of the regressive forcing characteristic.
These and other features and aspects of different embodiments of the present invention will be apparent from the claims, specification, and drawings.
For the purposes of promoting an understanding of the principles of the invention, reference will now be made to the embodiments illustrated in the drawings and specific language will be used to describe the same. It will nevertheless be understood that no limitation of the scope of the invention is thereby intended, such alterations and further modifications in the illustrated device, and such further applications of the principles of the invention as illustrated therein being contemplated as would normally occur to one skilled in the art to which the invention relates.
The use of an N-series prefix for an element number (NXX) refers to an element that is the same as the non-prefixed element (XX), except as shown and described thereafter. Although various specific quantities (spatial dimensions, temperatures, pressures, times, force, resistance, current, voltage, concentrations, etc.) may be stated herein, such specific quantities are presented as examples only, and are not to be construed as limiting.
One embodiment of the present invention pertains to a damper having regressive characteristics in both rebound and compression. As one example, during compression of the damper at low velocity, the force required to compress the damper progressively increases as the compressive velocity of the damper increases. During operation at moderate compressive velocities, the force required to compress the damper regressively decreases as the velocity increases. At still higher compressive velocities, the damping force progressively increases with increased compressive velocity.
One embodiment of the present invention pertains to a damper having regressive characteristics. During extension of the damper at low velocity, the force required to extend the damper progressively increases as the extensive velocity of the damper increases. During operation at moderate extensive velocities, the force required to extend the damper regressively decreases as the velocity increases. At still higher extensive velocities, the damping force progressively increases with increased extensive velocity.
In order to compensate for changes in the density of hydraulic fluid 20.1 and shaft-displaced fluid, shock absorber 20 includes a nitrogen chamber separated by a reservoir piston 38 from the fluid-wetted volume of cylinder 26.
Shock absorber 20 is typically used with the suspension of a vehicle. Rod 24 includes a first suspension attachment 26.3, and end cap 26.2 of cylinder 26 includes a second suspension attachment 26.3. These suspension attachments 26.3 permit the pivotal connection of shock absorber 20 to a portion of the vehicle suspension on one end, and on the other end to a portion of the vehicle frame. It is well known to use shock absorbers on many types of vehicles, including motorcycles, buses, trucks, automobiles, and airplanes. Further, although shock absorber 20 has been referred to for being used on a vehicle, shock absorbers are also known to be used in other applications where it is beneficial to dampen the movement of one object relative to another object, such as dampers for doors.
Compression flowpath 32 includes a fluid passageway interconnecting volumes 26.4 and 26.5 with a one-way valve in the flowpath 32. This one-way valve can be one or more annular shims which are prevented from flexing in one direction (and thus substantially restricting flow), but able to flex in a different direction (and thus allow flow in this opposite direction). Likewise, rebound flowpath 34 provides fluid communication between volumes 26.4 and 26.5 through a one-way valve. Often, the one-way valve of the compression flowpath 32 has different characteristics than the one-way valve of rebound flowpath 34.
Shock absorber 20′ includes means for varying the fluid resistance of a flowpath interconnecting compression volume 26.4′ and rebound volume 26.5′. Rod 24′ includes an internal passage 24.1′ that extends out one end of shaft 24′, and extends in the opposite direction towards attachment 26.3′. The open end of internal passage 24.1′ is in fluid communication with one or more orifices 24.4′ that extend from internal passage 24.1′ to rebound volume 26.5′. The flow of fluid through this internal passageway between the compression and rebound volumes is restricted by a metering needle 24.3′ received within internal passage 24.1′. The position of metering needle 24.3′ can be altered by a pushrod 24.6′ also extending within internal passage 24.1′. Push rod 24.6′ includes an end 24.7′ that is adapted and configured to mate with an internal adjustment screw 24.5′. The inward adjustment of screw 24.5′ acts on the angled interface to push rod 24.6′ and adjustment needle 24.3′ toward a position of increased resistance in the internal flowpath.
Piston 22″ includes a pair of shim sets 36″, each shim set shown including 4 individual washers. During operation in compression (i.e., movement in
Although what has been shown described is a shock absorber 20 that is linear in operation, the prior art of shock absorbers further includes rotary dampers, such as the toroidal damper disclosed in U.S. Pat. No. 7,048,098, incorporated herein by reference. In addition, although
As used herein, the word compression refers to the action and direction of the shock absorber during compression of the wheel suspension, this term being synonymous with the term jounce. Therefore, the end of the shock absorber referred to as a compression end is the end which has a reduction in internal volume (due to movement of the piston relative to the cylinder) during compression of the vehicle suspension. The rebound end of the shock absorber is the end that is opposite of the compression end.
A spring 170 biases piston 160 toward one end of the internal chamber. Spring 170 is received within a spring pocket defined at one end by a pocket 152.2 in the first part 152 of housing 150, and defined at the other end by a spring receiving pocket or spring-receiving surface 160.8 of piston 160. When first part 152 and second part 154 of housing 150 are threadably coupled together, spring 170 is adapted and configured to place a predetermined force on the underside surface 160.8, such that piston 160 is preloaded toward one end of its range of travel.
Preferably, housing assembly 150 is threadably coupled to the end of rod 124 in place of, or proximate to, a coupling nut (not shown). In one embodiment, housing 150 is threadably coupled to rod 124 proximate to main piston 122. However, the present invention also contemplates those embodiments in which housing 150 is further integrated with piston 122, including those embodiments in which secondary piston 160 and spring 170 are incorporated within the main piston.
Referring to
In some embodiments of the present invention, piston 160 includes a central orifice 160.2 that provides fluid communication between compression volume 126.4 and rebound volume 126.5 by way of internal passage 124.1 of rod 124 during all operation of the damper. However, the present invention also contemplates those embodiments in which a similar flowpath is established through main piston 122, and also those embodiments in which there is no fixed restriction between the compression volume and rebound volume that is operable during all operation of the damper.
Housing assembly 150 is generally exposed to hydraulic pressure within the compression volume 126.4 of shock 120. Therefore, this hydraulic pressure is communicated to a portion 160.6 of piston 160 that is in fluid communication with aperture 154.3. Hydraulic pressure within compression volume 126.4 coacts with the portion 160.6 of the surface area of piston 160 to apply a force to piston 160 that tends to push piston 160 away from second housing part 154.
The pressure force on piston 160 described above is opposed by a spring force. Spring 170 is adapted and configured to be preloaded when installed within housing 150. Spring 170, located within a pocket 152.2 of first housing part 152, applies a biasing force to push piston 160 toward the first position. There is hydraulic pressure applied to the underside 160.10 of piston 160. This underside pressure is communicated from orifices 124.4 in rod 124 into internal passage 124.1. The hydraulic pressure within internal passage 124.1 is also influenced by hydraulic fluid that flows between compression volume 126.4 and rebound volume 126.5 by way of main orifice 160.2. This pressure is communicated to the volume of the internal chamber generally bounded by spring pocket 152.2 and the underside 160.10 of piston 160.
This pressure within passage 124.1 is further communicated through a plurality of peripheral orifices 160.3 in the body of piston 160. These orifices communicate this underside hydraulic pressure to the front side of piston 160 (i.e., the volume between the opposing planar surfaces of piston 160 and housing part 154). Because of communication through orifices 160.3, the pressure force on piston 160 in the first position results from the coaction of the difference in pressures between compression volume 126.4 and the pressure within internal passage 124.1, acting on the portion of surface area of piston 160 that projects from aperture 154.3.
Piston 160 is slidably received within the inner cylindrical circumferential wall 154.2 of housing part 154. In some embodiments, the outer diameter 160.1 of piston 160 discourages leakage flow within the internal chamber by way of a close fit between the outer diameter 160.1 of piston 160 and the walls 154.2 of housing 154. However, in some embodiments piston 160.6 includes a seal to discourage leakage flow, such as a Teflon® seal backed up by a spring.
Leakage flow of hydraulic fluid from compression volume 126.4 into the third internal volume of internal chamber 156 is discouraged by a close fit between a portion of the outer diameter of projection 160.9 and the side walls of aperture 154.3. In one embodiment, projection 160.9 includes a generally cylindrical portion for sealing purposes, and also a scalloped portion which maintains guidance of the projection within the aperture, the scalloped portions also permitting flow of hydraulic fluid after the sealing portion of projection 160.9 moves out of aperture 154.3. This flow past the scalloped portion occurs when piston 160 moves toward its second position.
The operation of a valve assembly 150 having a slidable, sealed piston preloaded by a spring 170 within threadably coupled members 154 and 152 can be adapted to provide regressive forcing characteristics for both compression and extension (or rebound) of a shock absorber. Further, the general operation of a regressive valve assembly as previously described can be adapted in various other configurations of apparatus as will now be shown and described.
A spring 270 biases piston 260 toward one end of the internal chamber. Spring 270 is received within a spring pocket defined at one end by a pocket 252.2 in the first part 252 of housing 250, and defined at the other end by a spring receiving pocket or surface 260.8 of piston 260. When first part 252 and second part 254 of housing 250 are threadably coupled, spring 270 is adapted and configured to place a predetermined force on the underside surface 260.8, such that piston 260 is preloaded toward one end of its range of travel.
Preferably, housing assembly 250 is threadably coupled to the end of rod 224 in place of, or proximate to, a coupling nut (not shown). In one embodiment, housing 250 is threadably coupled to rod 224 proximate to main piston 222. However, the present invention also contemplates those embodiments in which housing 250 is further integrated with piston 222, including those embodiments in which secondary piston 260 and spring 270 are incorporated within the main piston.
Piston 260 is slidable within an internal chamber formed by the coupling of housing first part 252 to housing second part 254. Piston 260 is shown in the first position, as would be experienced during rebound operation of shock absorber 220 and also during low velocity compression operation. A projection 260.9 of piston 260 projects as a plateau from a substantially planar face of piston 260, and further extends into contact with the face and edge of an aperture 254.3 of second housing part 254.
In some embodiments of the present invention, piston 260 includes a central orifice 260.2 that provides fluid communication (and in some embodiments a first flowpath) between compression volume 226.4 and rebound volume 226.5 by way of internal passage 224.1 of rod 224 during all operation of the damper. However, the present invention also contemplates those embodiments in which a similar flowpath is established through main piston 222, and also those embodiments in which there is no fixed restriction between the compression volume and rebound volume that is operable during all operation of the damper.
Housing assembly 250 is generally exposed to hydraulic pressure within the compression volume 226.4 of shock 220. Therefore, this hydraulic pressure is communicated to a portion 260.6 within plateau 260.9 of piston 260 that is in fluid communication with aperture 254.3. Hydraulic pressure within compression volume 226.4 coacts with the surface of portion 260.6 to apply a force to piston 260 that tends to push piston 260 away from second housing part 254.
The force on piston 260 described above is opposed by a pressure and spring force. Spring 270, located within a pocket 252.2 of first housing part 252, applies a biasing force to push piston 260 toward the first position. There is hydraulic pressure is applied to the underside 260.10 of piston 260. This underside pressure is communicated from orifices 224.4 in rod 224 into internal passage 224.1. The hydraulic pressure within internal passage 224.1 is also influenced by hydraulic fluid that flows between compression volume 226.4 and rebound volume 226.5 by way of a main orifice 260.2. This pressure is communicated to the volume of the internal chamber generally bounded by spring pocket 252.2 and the underside 260.10 of piston 260.
This pressure within passage 124.1 is further communicated through a plurality of peripheral orifices 260.3 in the body of piston 260. These orifices communicate this underside hydraulic pressure to the front side of piston 260 (i.e., the volume between the opposing planer surface of piston 260 and housing part 254. Because of communication through orifices 260.3, the pressure force on piston 260 in the first position results from the coaction of the difference in pressures between compression volume 226.4 and the pressure within internal passage 224.1, acting on the surface area of piston 160 that projects from aperture 254.3.
Piston 260 is slidably received within the cylindrical circumferential wall 254.2 of housing part 254. In some embodiments, the outer diameter 260.1 of piston 260 discourages leakage flow within the internal chamber by way of a close fit between the outer diameter 260.1 of piston 260 and the walls 254.2 of housing 254. However, in some embodiments piston 260.6 includes a slidable seal to discourage leakage flow, such as a Teflon® seal backed up by a spring.
Leakage flow of hydraulic fluid from compression volume 226.4 into the third internal volume of internal chamber 256 is discouraged by a face seal between a portion of the outer diameter of projection 260.9 and the edge of aperture 254.3. In one embodiment, projection 260.9 includes a generally cylindrical plateau for sealing purposes. The abutting faces of plateau 260.9 and the edge of aperture 254.3 are smooth and coplanar to form the face seal. In yet other embodiments, one or both of these abutting surfaces can include a resilient face seal, such as a elastomeric seal molded or placed within a groove on plateau 260.9.
During regressive operation of shock absorber 220, Piston 260 moves toward the second position. When the pressure differential between the pressure in compression volume 226.4 and the pressure within passage 224.1 coact with the surface area of projection 260.9, is sufficient to overcome the biasing force of spring 270, piston 260 moves away from the first position, and the face seal between projection 260.9 and the edge of aperture 254.3 no longer discourages flow into the internal chamber of housing 250. Movement of piston 260 toward the second position creates a gap between the formerly abutting surfaces into which hydraulic fluid flows from compression volume 226.4. Such movement of piston 260 is similar to the movement of piston 160 shown in
During lower velocity compression of shock absorber 220, hydraulic fluid flows from compression volume 226.4 into rebound volume 226.5 through central orifice 260.2 of piston 260, and also through a one way valve 236 of main piston 222. Referring to
At moderate compressive velocities, the pressure force acting on piston 260 causes it to move from a first, sealing position toward a second, open position. This movement of piston 260 results in the ability of hydraulic fluid from compression volume 226.4 to flow through secondary orifices 260.3 of piston 260, as well as through central orifice 260.2. This additional flow area results in a reduction in pressure within compression volume 226.4, such that the pressure drop across main piston 222 is reduced and the damping force is reduced. Operation in this regime is depicted by the regressive portion 112 of damping curves 110.
However, this reduction in pressure does not result in piston 260 moving back to the first position, since the pressure of compression volume 226.4 is communicated to a larger surface area in the second position. Therefore, the coaction of a reduced pressure differential with an increased surface area results in a pressure force capable of maintaining piston 260 in the second position.
At still higher relative higher compressive velocities (as depicted by the second progression portion 113 of damping curve 110), the regressive contribution of housing assembly 250 remains relatively constant, and the overall damping characteristics of the shock absorber are dictated primarily by the one way valves 236 of piston 222, as well as any metering needles 224.3, or other flow components of piston 220. The resultant combined characteristic in compressive flow is thus that of a higher pressure drop fixed restriction in parallel with a one way valve at low velocities, and a lower pressure drop fixed restriction in parallel with a one way valve the same one way valve at higher velocities. There is an initial progressive characteristic, followed by a regressive characteristic, which is followed by a second progressive characteristic that is substantially parallel to an extension of the first progressive characteristic. This second progressive characteristic provides a damping characteristic at higher rod velocities.
In one illustrative embodiment, the initial progressive characteristic extends up to about 4 inches/second. The regressive characteristic extends from about 5 to 6 inches/second. The second progressive characteristic extends from about 7 inches/second. In one illustrative embodiment, the second progressive characteristic is about 75 lbf lower than a substantially parallel extension of the first progressive characteristic.
Valve housing assembly 350 is similar to valve housing 150 and 250 as previously described, except for the changes discussed and shown herein.
Valve housing 350 includes a piston or poppet 360 that is slidably movable relative to first members 352 and 354. Piston 360 includes an internally threaded bore that is threadably received on the end of rod 324. Piston 360 thus moves with rod 324. A spring 370 is captured between a spring pocket 352.2 of member 352 and spring pocket 360.8 of piston 360. Spring 370 biases piston 360 relative to threadably couple the members 352 and 354 such that surface 360.4 of piston 360 is in sealing contact with face sealing surface 354.4 of member 354.
During extension of damper 320 at lower stroking velocities, rod 324 moves downward and to the left as viewed in
In addition to this flowpath, the fluid within rebound volume 326.5 being displaced by movement of rod 324 is also able to flow through a plurality of feed apertures 324.4 into a central internal passage 324.1. This fluid can flow through the restriction provided by orifice 354.3 that is provided within member 354. As shown in
Referring to
In comparing
After fluid has flowed through the circumferential apertures of member 694a and adjustment member 692, it is received within an inner flow area where it acts on the center of a slidable piston 660. Piston 660 is slidable within and sealed to the inner diameter of a chamber defined by valve member 694a. A spring 670 is received within a pocket formed on the underside of piston 660. Spring 670 is further biased against a second member 694b that is threadably received by member 694a. Spring 670 is thereby captured within a housing defined by attached members 694a and 694b, and biases piston 660 away from member 694b.
The other, downstream end of member 694b is threadably received within a static member 695. Static member 695 is threadably coupled to the holding structure of head valve assembly 690, and further locates by threads a static flow member 696. One end of flow member 696 includes a conically shaped portion 696.1 that extends into a downstream portion of valve member 694b. As flow from flowpaths 680 and 682 exit member 694, they pass through an annular restriction formed by the conical nose of member 696 and the end of the inner passage of member 694b.
The restriction between the conical portion of member 696 and the exit of member 694b coact to form an adjustable high velocity restriction for the high velocity flowpath 682. As external adjustment member 691 is rotated, valve assembly 694a/694b, which is threadably received within static member 695, moves axially either closer or further from the conical seat of static member 696. With this action, an annular restriction is formed which provides a pressure drop for flowpaths 680 and 682. However, since the magnitude of the high speed flow 682 is generally greater than the flow along path 680, adjustment of the restriction formed by the conical member tends to be more restrictive under high stroking velocity operation.
Head valve 690 further includes means for adjusting the preload on the spring, and in this way provides an adjustment that modifies the force at which the low speed portion of the regressive curve ends and the intermediate velocity portion (the portion transitioning to the high velocity regime) begins. Referring to
Piston 660 includes a central orifice 660.2 that provides most of the low velocity restriction of head valve 690. The low speed flowpath 680 (through central orifice 660.2) and the high velocity flowpath 682 (around the face seal formed by surfaces 660.4 and 692.1 during high velocity operation) are both provided fluid from pathway 639. However, fluid from passage 639 is further in communication with an annular passage within static valve 695 (and further evident in
For both characteristics C and D, the poppet force occurs at a velocity of approximately 0.1. From this low poppet velocity to the high speed characteristic at about 0.7, the piston X60 is moving from its first, spring-preloaded position to its second position. In this intermediate speed regime the low speed flowpath x80 is open, but the second, high speed flowpath x82 is at a position between fully closed and fully open.
Located within external housing 551 is a valve assembly 550 that is substantially the same as valve assembly 350 of
As is the case with valve assembly 350, when pressure on piston 550 is sufficiently high to overcome the preload force exerted by spring 570, fluid is free to flow through flowpath 582 around the face seal between piston 560 and member 554. This second flowpath 582 is in parallel with the first flowpath 580, which is also the case in valve assembly 350.
As can be understood from the drawings and description given herein, shock absorber 520 can have either regressive characteristics in compression or extension based on the orientation of head valve 551. In the orientation as shown in
At the innermost end of shaft 793 there is a bull nose projection that is received within a central aperture of piston 760. An annular restriction is formed between the bull nose projection and the central aperture. Fluid from passageway 739 flows through this annular restriction as the low velocity flowpath 780. By rotating shaft 793 relative to collar 792, the bull nose projection is moved axially within the central aperture of piston 760. Since the outer surface of the bull nose projection is contoured, moving the projection upward (referring to
In one embodiment, the high velocity regressive adjustment of member 794b relative to conical projection 796.1 includes positive means for establishing the relative rotational positions of member 794b and the static structure of head valve 790, such as a detent mechanism. As shown in
Preferably, there is a detent mechanism or other method of positively establishing the relative rotational positions of adjustment collar 792 and member 794a, such as a detent mechanism. Further, in some embodiments, there is a detent mechanism establishing positively the relative rotational positions of shaft 793 and collar 792.
Although what has been shown and described in
Further, although some embodiments such as valve assembly 150 are shown attached to the end of rod 124, the present invention also contemplates those embodiments in which the valve assembly X50 is attached to piston X22.
While the inventions have been illustrated and described in detail in the drawings and foregoing description, the same is to be considered as illustrative and not restrictive in character, it being understood that only the preferred embodiment has been shown and described and that all changes and modifications that come within the spirit of the invention are desired to be protected.
This application is a continuation of U.S. patent application Ser. No. 12/144,530, filed Jun. 23, 2008, now issued as U.S. Pat. No. 9,494,209, on Nov. 15, 2016, which claims the benefit of priority of U.S. Provisional Patent Application Ser. No. 60/945,365, filed Jun. 21, 2007, all of which are incorporated herein by reference.
Number | Date | Country | |
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60945365 | Jun 2007 | US |
Number | Date | Country | |
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Parent | 12144530 | Jun 2008 | US |
Child | 15347096 | US |