The present invention relates generally to chucks for use with drills or with electric or pneumatic power drivers. More particularly, the present invention relates to a chuck of the keyless type which may be tightened or loosened by hand or actuation of the driver motor.
Both hand and electric or pneumatic tool drivers are well known. Although twist drills are the most common tools on such drivers, the tools may also comprise screw drivers, nut drivers, burrs, mounted grinding stones, and other cutting or abrading tools. Since the tool shanks may be of varying diameter or of polygonal cross section, the device is usually provided with a chuck adjustable over a relatively wide range. The chuck may be attached to the driver by a threaded or tapered bore.
A variety of chucks have been developed in the art. In an oblique jawed chuck, a chuck body includes three passageways disposed approximately 120° apart from each other. The passageways are configured so that their center lines meet at a point along the chuck axis forward of the chuck. The passageways constrain three jaws which are movable in the passageways to grip a cylindrical or polygonal tool shank displaced approximately along the chuck center axis. The chuck includes a nut that rotates about the chuck center and that engages threads on the jaws so that rotation of the nut moves the jaws in either direction within the passageways. The body is attached onto the drive shaft of a driver and is configured so that rotation of the body in one direction with respect to the nut forces the jaws into gripping relationship with the tool shank, while rotation in the opposite direction releases the gripping relationship. The chuck may be keyless if it is rotated by hand. Examples of such chucks are disclosed in U.S. Pat. Nos. 5,125,673 and 5,193,824, the entire disclosures of which are incorporated by reference herein. Various configurations of keyless chucks are known in the art and are desirable for a variety of applications.
The present invention recognizes and addresses the foregoing considerations, and others, of prior art constructions and methods.
An embodiment of the present invention includes a chuck for use with a manual or powered driver having a rotatable drive shaft. The chuck includes a generally cylindrical body having a nose section and a tail section, the tail section being configured to rotate with the drive shaft and the nose section having an axial bore formed therein. A plurality of jaws are movably disposed with respect to said body in communication with said axial bore. A sleeve is rotatably mounted about the body in operative communication with the jaws so that rotation of the sleeve in a closing direction moves the jaws toward a longitudinal axis of the axial bore and rotation of the sleeve in an opening direction moves the jaws away from the longitudinal axis. A bearing has a first race adjacent the body, a second race adjacent the sleeve and at least one bearing element disposed between the first race and the second race. One of the first race and the second race define a ratchet and the other of the first race and the second race defines a pawl biased toward the ratchet, and a biasing element disposed between the pawl and the sleeve. The biasing element exerts a biasing force on said pawl toward said ratchet and wherein said ratchet and said pawl are configured so that when said pawl engages said ratchet, said ratchet and pawl prevent said second race from rotating in said opening direction with respect to said first race.
Another embodiment of the invention provides a chuck for use with a manual or powered driver having a rotatable drive shaft. The chuck includes a generally cylindrical body having a nose section and a tail section, the tail section being configured to rotate with the drive shaft and the nose section having an axial bore formed therein. A plurality of passageways are formed therethrough and intersect the axial bore. A plurality of jaws are movably disposed in said passageways. A generally cylindrical first sleeve is rotatably mounted about the body and in operative communication with the jaws so that rotation of the first sleeve in a closing direction moves the jaws toward a longitudinal axis of the axial bore and rotation of the first sleeve in an opening direction moves the jaws away from the longitudinal axis. A bearing has a first race adjacent the body, a second race adjacent the first sleeve and a plurality of bearing elements disposed between the first race and the second race. The first race defines a ratchet, the second race defines a deflectable first pawl biased toward the ratchet, the ratchet and the first pawl being configured so that when the first pawl engages the ratchet, the ratchet and first pawl permit the second race to rotate in the closing direction with respect to the first race but prevent the second race from rotating in the opening direction with respect to the first race. A biasing element is disposed between the second race and the first sleeve, and the biasing element is configured to bias the first pawl toward said ratchet.
The accompanying drawings, which are incorporated in and constitute a part of this specification, illustrate one or more embodiments of the invention and, together with the description, serve to explain the principles of the invention.
A full and enabling disclosure of the present invention, including the best mode thereof to one of ordinary skill in the art, is set forth more particularly in the remainder of the specification, which makes reference to the accompanying figures, in which:
Repeat use of reference characters in the present specification and drawings is intended to represent same or analogous features or elements of the invention.
Reference will now be made in detail to presently preferred embodiments of the invention, one or more examples of which are illustrated in the accompanying drawings. Each example is provided by way of explanation of the invention, not limitation of the invention. In fact, it will be apparent to those skilled in the art that modifications and variations can be made in the present invention without departing from the scope or spirit thereof. For instance, features illustrated or described as part of one embodiment may be used on another embodiment to yield a still further embodiment. Thus, it is intended that the present invention covers such modifications and variations as come within the scope of the present disclosure.
Referring to
Body 14 defines three passageways 40 to accommodate the three jaws. Each jaw is separated from the adjacent jaw by an arc of approximately 120°. The axes of passageways 40 and jaws 22 are angled with respect to the chuck center axis 30 such that each passageway axis travels through axial bore 34 and intersects axis 30 at a common point ahead of the chuck body. The jaws form a grip that moves radially toward and away from the chuck axis to grip a tool, and each jaw 22 has a tool engaging face 42 generally parallel to the axis of chuck body 14. Threads 44, formed on the jaw's opposite or outer surface, may be constructed in any suitable type and pitch. As shown in
As illustrated in
Body tail section 26 includes a knurled surface 54 that receives an optional rear sleeve 12 in a press fit at 55. Rear sleeve 12 could also be retained by press fit without knurling, by use of a key or by crimping, staking, riveting, threading or any other suitable securing mechanism. Further, the chuck may be constructed with a single sleeve having no rear sleeve.
Nose piece 20 retains nut 16 against forward axial movement. The nose piece is press fit to body nose section 24. It should be understood, however, that other methods of axially securing the nut on the body may be used. For example, the nut may be a two-piece nut held on the body within a circumferential groove on the outer circumference of the body. Nose piece 20 may be coated with a non-ferrous metallic coating to prevent rust and to enhance its appearance. Examples of suitable coatings include zinc or nickel, although it should be appreciated that any suitable coating could be utilized.
The outer circumferential surface of front sleeve 18 may be knurled or may be provided with longitudinal ribs 77 or other protrusions to enable the operator to grip it securely. In like manner, the circumferential surface of rear sleeve 12, if employed, may be knurled or ribbed as at 79 if desired.
Front sleeve 18 is secured from movement in the forward axial direction by an annular shoulder 91 on nose piece 20. A frustoconical section 95 at the rearward end of the nose piece facilitates movement of jaws 22 within the chuck.
The front and rear sleeves may be molded or otherwise fabricated from a structural plastic such as polycarbonate, a filled polypropylene, for example a glass filled polypropylene, or a blend of structural plastic materials. Other composite materials such as, for example, graphite filled polymerics may also be suitable in certain environments. As should be appreciated by one skilled in the art, the materials from which the chuck is fabricated will depend on the end use of the chuck.
Nut 16 has threads 56 for mating with jaw threads 44. Nut 16 is positioned about the body in engagement with the jaw threads so that when the nut is rotated with respect to body 14, the jaws will be advanced or retracted depending on the nut's rotational direction.
As illustrated in
Nut 16 also defines a plurality of grooves formed as flats 68 about the nut's outer circumference. Flats 68 receive respective tabs 70 extending forward from an inner race 72 of a bearing assembly 74. The engagement of tabs 70 and flats 68 rotationally fix the inner race to the nut, although it should be understood that there may be a slight rotational tolerance between the two.
Inner race 72 receives a plurality of bearing elements, in this case bearing balls 76, disposed between it and an outer race 78 seated on thrust ring ledge 50 (
Returning to the prior art chuck in
Each tooth 84 has a first side with a slope approaching 90° with the periphery of the outer race. A second side of each tooth 84 has a lesser slope. First pawl 86 is deflectable and is generally disposed in alignment with the slope of the second side. Thus, rotation of inner race 72 in a closing direction 90 with respect to outer race 78 moves first pawl distal ends 88 repeatedly over teeth 84, causing a clicking sound each as end 88 falls against each subsequent tooth second side. This configuration of teeth and first pawls 86, however, prevents the inner race's rotation in an opposite opening direction 92. Application of rotational force to the inner race in this direction forces distal ends 88 into the steep-sloped first sides of teeth 84. Since pawl 86 is generally perpendicular to the first sides, it does not deflect inward to permit rotation. As discussed below, direction 90 corresponds to the chuck's closing direction, while direction 92 corresponds to the chuck's opening direction. Accordingly, when pawls 86 engage ratchet teeth 84, the teeth permit the inner race's movement in the chuck's closing direction 90 but prevent its movement in the opening direction 92.
A second deflectable pawl 94 extends from the other side of each tab 70. Like first pawls 86, each second pawl 94 is biased radially outward. Unlike first pawls 86, however, second pawls 94 do not engage the outer race ratchet.
First and second pawls 86 and 94 include tabs 96 and 98, respectively, at their distal ends. Referring also to
Referring now to
As described in more detail below, when sleeve 18 rotates in opening direction 92 so that the inner race moves from the position shown in
In operation and referring to
The wedge between the nut threads and jaw threads increasingly resists the nut's rotation. When the operator continues to rotate sleeve 18 and the resistance overcomes the hold provided by tabs 98 in recesses 100, sleeve 18 rotates with respect to nut 16 and inner bearing race 72. This moves drive dogs 64 from sides 111 of grooves 62 to sides 108 and pushes tabs 98 out of recesses 100 into recesses 102. Simultaneously, cam surfaces 106 rotate away from tabs 96 so that the tabs are released into recesses 104, thereby engaging distal ends 88 of first pawls 86 with ratchet teeth 84, as shown in
Inner race 72, and therefore nut 16, may, however, still rotate with respect to outer race 78, and therefore body 14, in the chuck's closing direction. During such rotation, sleeve 18 drives nut 16 through drive dogs 64 against groove sides 108, as well as through inner race 72. This continues to tighten the chuck and as described above and produces a clicking sound to notify the operator that the chuck is in a fully tightened position.
To open the chuck, the operator rotates sleeve 18 in opening direction 92. Sleeve 18 transfers this torque to inner race 72 at the engagement of tabs 96 and 98 in recesses 104 and 102, respectively. Because pawls 86 engage outer race 78, which is rotationally fixed to the body, the inner race cannot rotate with the sleeve. Thus, upon application of sufficient torque in opening direction 92, sleeve 18 moves with respect to the inner race and the nut. This moves tab 96 back up onto cam surface 106, thereby disengaging first pawl 86 from ratchet teeth 84. Tab 98 moves from second recess 102 into first recess 100, and drive dogs 64 move from sides 108 to sides 111 of grooves 62. Thus, the sleeve moves to its first position with respect to the nut, as shown in
The pawls and ratchet may be formed in any suitable configuration. Furthermore, the chuck may be realized in a variety of configurations whereby a bearing having a ratchet configuration is disposed between a sleeve, for example a nut or other suitable configuration, and the chuck body. For example, a chuck may include a body, a nut that is rotationally fixed to and axially movable with respect to the body, and an outer sleeve that threadedly engages the nut so that rotation of the sleeve moves the nut axially on the body. The jaws may be axially fixed to the nut and received in body passageways so that the nut's axial movement drives the jaws towards and away from the chuck's axis. In this configuration, an outer sleeve may be permitted to rotate over a limited angular distance with respect to a second sleeve. A bearing including a ratchet configuration as discussed above may be disposed between the second sleeve and the chuck body. Depending on the chuck's configuration, the pawls and ratchet may be interchanged as appropriate.
Body 14 defines three passageways 40 to accommodate the three jaws. Each jaw is separated from the adjacent jaw by an arc of approximately 120°. The axes of the jaw passageways and jaws 22 are angled with respect to the chuck center axis such that each passageway axis travels through the forward axial bore in the body and intersects the chuck axis at a common point. The jaws form a grip that moves radially toward and away from the chuck axis to grip a tool, and each jaw 22 has a tool engaging face 42 generally parallel to the axis of chuck body 14. Threads 44, formed on each jaw's opposite or outer surface, may be constructed in any suitable type and pitch. As also indicated in
As illustrated in
Body tail section 26 includes a knurled surface 54 that receives a dust cover 13 in a press fit. Dust cover 13 could also be retained by press fit without knurling, by use of a key or by crimping, staking, riveting, threading or any other suitable securing mechanism. Further, the chuck may be constructed with two hand-actuatable sleeves, as shown in
Front sleeve 18 is secured from movement in the forward axial direction by an annular shoulder 91 on nose piece 20. A frustoconical section 95 at the rearward end of the nose piece facilitates movement of jaws 22 within the chuck.
The outer circumferential surface of front sleeve outer part 19 may knurled or may be provided with longitudinal ribs or other protrusions to enable the operator to grip it securely. Outer front sleeve part 19 and metal insert 17 (
Generally, the outer surface of inner part 21 conforms to the inner surface of outer part 19. However, polymer inner part 21 defines a plurality of flanges 23 that extend forward from the main portion of the inner sleeve part. Flanges 23 include front edges 25 that extend radially outward to thereby define a groove 27 between edges 25 and the front edge of the inner sleeve part's main portion. The segmented arrangement of flanges 23 allows the flanges to flex inward as the outer part is assembled over the inner part. A front edge 29 of outer sleeve part 19 extends radially inward and is notched to receive flanges 23. Thus, at the notches, front edge 29 extends radially inward into groove 27, while flanges 23 extend through the notches. Thus, groove 27 retains outer sleeve part 19 in the axially forward and rearward directions between the tabs' front edges 25 and the forward edge of the main portion of sleeve inner part 21. Sleeve outer part 19 rotationally drives sleeve inner part 21 through the interengagement of front edge 29 and flanges 23 and through a plurality of spaced-apart dogs (not shown) extending radially inward from the outer sleeve part's inner circumferential surface into corresponding notches 31 in the front outer surface of inner sleeve part 21. It should be understood that the two-part sleeve shown in
Nut 16 has threads 56 for mating with jaw threads 44 and is positioned about the body in engagement with the jaw threads so that when the nut is rotated with respect to body 14, the jaws will be advanced or retracted depending on the nut's rotational direction.
The nut's forward axial face includes recesses 62 that receive respective drive dogs 64 extending from the inner surface of inner sleeve part 21. Recesses 62 and drive dogs 64 are constructed as described above with respect to
Nut 16 also defines a plurality of grooves, formed as flats 68 about the nut's outer circumference, that receive respective tabs 70 extending forward from an inner race 72 of a bearing assembly 74. The engagement of tabs 70 and flats 68 rotationally fix the inner race to the nut, although it should be understood that there may be a slight rotational tolerance between the two.
Inner race 72 receives a plurality of bearing elements, in this case bearing balls 76, disposed between it and an outer race 78 seated on thrust ring ledge 50. Outer race 78 is rotationally fixed to body 14 by a plurality of tabs 80 received in corresponding grooves 82 in the thrust ring ledge, as is described above with respect to
As discussed above with respect to outer race 78 in
A second deflectable pawl 94 extends from the other side of each tab 70. Like first pawls 86, each second pawl 94 is biased radially outward. Unlike first pawls 86, second pawls 94 do not engage the outer race ratchet. Pawls 86 and 94 are constructed identically to pawls 86 and 94 as described above with respect to
In drill chuck 10 as shown in
As shown in
The diameter defined by shoulder 130 on either side of groove 138 is approximately 1.244 inches, while the diameter of a circle defined by the trough of groove 138 is approximately 1.200 inches. Thus, O-ring 140 stretches when installed into groove 138, and its outer diameter becomes approximately 1.325 inches. A radius defined from the axis of chuck body 14 to any of pawls 86 and 94 in their positions as shown in
It will also be recognized that the increased radially outward bias increases the force necessary to be applied by the user in moving the sleeve between the locking mechanism's two operative positions. Thus, it should be understood that the materials and geometry of O-ring 140 may be selected to dampen vibrations in a power driver having a given power rating while still permitting effective manual operation by the user. For example, it is expected that a drill chuck as described above with respect to
In another preferred embodiment, groove 138 is formed into shoulder 130 in a square cross section, and O-ring 140 is formed in a correspondingly square cross section. The dimensions of the nut and O-ring otherwise remain the same.
It should also be understood that various materials may be used to construct O-ring 140. For example, materials include various suitable elastomers such as acrylonitrile-butadiene (NBR, buna N, or nitrile rubber), chloroprene rubber (CR, or neoprene), polyacrilic rubber, silicone rubber, butyl rubber (ITR), styrene-butadiene (SBR, or buna S rubber), chlorosulfonated polyethelene (CSM, commercially available under the name HYPALON), or polysulfide rubber (T, or thiokol polymer) or thermoplastics such as suitable fluorocarbons (e.g. Teflon TFE or FEP), impact grade polystyrenes comprising polystyrene and rubber, and polyamide resins (nylon). O-rings made from commercially available materials such as the fluoroelastomers and perfluoroelastomers VITON, KALREZ, SIMRIZ, CHEMRAZ and AFLAS, and HYPALON (chlorosulfonated polyethylene), are available from Marco Rubber & Plastic Products, Inc. of North Andover, Mass.
The shape of O-ring 140 may vary as desired. For example, O-ring 140 maybe molded into a shape that conforms at its inner diameter to the outer surface of shoulder 130 (with or without a groove 138) and that conforms at its outer circumference to the surfaces of pawls 86 and 94 that face the nut. The molded O-ring is preferably made by compression molding and can be formed from any of the above-described materials suitable for compression or injection molding. The O-ring can be molded as a separate component or can be molded directly around the nut.
To determine whether a given dampening structure, whether an O-ring of a selected material and geometry or any other selected resilient device, will sufficiently dampen vibrations for a given chuck configuration on a given driver, the structure may be assembled on a chuck and tested with the driver. Referring to the drill chuck as shown in
The construction of the pawls and ratchet teeth contribute to the resistance of the locking mechanism to vibrations and, consequently, to the degree to which a supplemental outward bias is desirable. For example, the depth of pawl teeth 84 constructed as described above contributes to the effectiveness of the primary outward bias and, in a preferred embodiment as shown in
It should also be understood that mechanisms other than O-rings may be used to apply additional bias to the pawls. In another preferred embodiment, for example, groove 138 in shoulder 130 may be omitted, so that shoulder 130 has a smooth surface as in
In a further preferred embodiment, shoulder 130 is again smooth, and O-ring 140 is replaced by a layer of silicone RTV (room-temperature vulcanized) rubber, for example 732 multi-purpose silicone RTV sealant made by Dow Corning Corporation and available from IDG Corporation of Belmont, N.C. The RTV sealant may be applied manually or automatically. For a construction as shown in
In a preferred embodiment in which shoulder 130 defines a diameter of approximately 1.244 inches, a total of approximately 0.7 grams of RTV sealant is disposed on the shoulder. It should be understood, however, that the amount of RTV sealant may vary as desired, with the lower end of the desirable range being the point at which the RTV sealant fails to provide sufficient resilient force for a given chuck and driver, and the upper end of the desirable range being the point at which RTV sealant extends beyond an operative space between shoulder 130 and the pawls and thereby fails to contribute to the additional bias force. In the arrangement (with a smooth shoulder 130) as described above with respect to
While one or more preferred embodiments of the present invention have been described above, it should be understood that any and all equivalent realizations of the present invention are included within the scope and spirit thereof. Thus, the depicted embodiments are presented by way of example only and are not intended as limitations on the present invention. It should be understood that aspects of the various one or more embodiments may be interchanged both in whole or in part. Therefore, it is contemplated that any and all such embodiments are included in the present invention as may be fall within the literal or equivalent scope of the present disclosure.
This application is a continuation of U.S. patent application Ser. No. 13/706,524, filed Dec. 6, 2012, now U.S. Pat. No. 8,678,400, which is a continuation of U.S. patent application Ser. No. 13/186,296, filed Jul. 19, 2011, now U.S. Pat. No. 8,328,205, which is a continuation of U.S. patent application Ser. No. 12/772,413, filed May 3, 2010, now U.S. Pat. No. 7,984,913, which is a continuation of U.S. patent application Ser. No. 11/435,405, filed May 17, 2006, entitled “Locking Chuck,” now U.S. Pat. No. 7,708,288, which claims priority to U.S. Provisional Application No. 60/682,615, filed May 18, 2005, the entire disclosures of which are incorporated by reference herein.
Number | Name | Date | Kind |
---|---|---|---|
573189 | Vogel | Dec 1896 | A |
4213623 | Rohm | Jul 1980 | A |
4302021 | Rohm | Nov 1981 | A |
4583751 | Rohm | Apr 1986 | A |
4840387 | McCarthy | Jun 1989 | A |
5014143 | Mori et al. | May 1991 | A |
5044643 | Nakamura | Sep 1991 | A |
5125673 | Huff et al. | Jun 1992 | A |
5145192 | Rohm | Sep 1992 | A |
5145193 | Rohm | Sep 1992 | A |
5172923 | Nakamura | Dec 1992 | A |
5193824 | Salpaka | Mar 1993 | A |
5215317 | Jordan et al. | Jun 1993 | A |
5232230 | Lin | Aug 1993 | A |
5234223 | Sakamaki | Aug 1993 | A |
5261679 | Nakamura | Nov 1993 | A |
5322303 | Nakamura | Jun 1994 | A |
5348317 | Steadings et al. | Sep 1994 | A |
5348318 | Steadings et al. | Sep 1994 | A |
5411275 | Huff et al. | May 1995 | A |
5431419 | Mack | Jul 1995 | A |
5458345 | Amyot | Oct 1995 | A |
5499829 | Rohm | Mar 1996 | A |
5499830 | Schnizler | Mar 1996 | A |
5501473 | Barton et al. | Mar 1996 | A |
5615899 | Sakamaki | Apr 1997 | A |
5741016 | Barton et al. | Apr 1998 | A |
5775704 | Wilson et al. | Jul 1998 | A |
5816582 | Steadings et al. | Oct 1998 | A |
5816583 | Middleton | Oct 1998 | A |
5826888 | Weaver et al. | Oct 1998 | A |
5829761 | Rohm | Nov 1998 | A |
5882153 | Mack et al. | Mar 1999 | A |
5913524 | Barton | Jun 1999 | A |
5957469 | Miles et al. | Sep 1999 | A |
6260856 | Temple-Wilson | Jul 2001 | B1 |
6390481 | Nakamuro | May 2002 | B1 |
6502836 | Marriott | Jan 2003 | B1 |
6554289 | Lin | Apr 2003 | B1 |
6572310 | Temple-Wilson | Jun 2003 | B2 |
6581942 | Rohm | Jun 2003 | B2 |
6659474 | Sakamaki et al. | Dec 2003 | B2 |
6824141 | Sakamaki et al. | Nov 2004 | B1 |
6843485 | Sakamaki et al. | Jan 2005 | B2 |
6902171 | Sakamaki et al. | Jun 2005 | B2 |
7185895 | Cachod et al. | Mar 2007 | B2 |
7296803 | Yang et al. | Nov 2007 | B2 |
7360770 | Luckenbaugh et al. | Apr 2008 | B2 |
7451990 | Young | Nov 2008 | B2 |
7472913 | Gong et al. | Jan 2009 | B2 |
7497444 | Sakamaki et al. | Mar 2009 | B2 |
7527273 | Bordeianu | May 2009 | B2 |
7845651 | Yaksich | Dec 2010 | B2 |
7900937 | Yaksich | Mar 2011 | B2 |
20050087937 | Zhou | Apr 2005 | A1 |
20080042375 | Yaksich | Feb 2008 | A1 |
20090045594 | Yaksich | Feb 2009 | A1 |
20120126495 | Garber et al. | May 2012 | A1 |
Number | Date | Country |
---|---|---|
4238503 | Nov 1993 | DE |
19506708 | Mar 1996 | DE |
29600727 | Mar 1996 | DE |
4438991 | May 1996 | DE |
0618029 | Oct 1994 | EP |
0677348 | Oct 1995 | EP |
0710518 | May 1996 | EP |
0710519 | May 1996 | EP |
0710520 | May 1996 | EP |
0519412 | Mar 1997 | EP |
0785041 | Feb 2001 | EP |
2645056 | Oct 1990 | FR |
4365504 | Dec 1992 | JP |
Entry |
---|
International Preliminary Search Report for PCT/US2006/019419, dated Mar. 19, 2009. |
European Search Report dated Sep. 29, 2009, for co-pending European Patent Application No. EP 06 760 169.0 filed on May 18, 2006. |
Number | Date | Country | |
---|---|---|---|
20140203525 A1 | Jul 2014 | US |
Number | Date | Country | |
---|---|---|---|
60682615 | May 2005 | US |
Number | Date | Country | |
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Parent | 13706524 | Dec 2012 | US |
Child | 14223247 | US | |
Parent | 13186296 | Jul 2011 | US |
Child | 13706524 | US | |
Parent | 12772413 | May 2010 | US |
Child | 13186296 | US | |
Parent | 11435405 | May 2006 | US |
Child | 12772413 | US |