Patent Grant
8475140
The present invention relates to generally to scroll machines. More particularly, the present invention relates to a dual volume ratio scroll machine, having a multi-function seal system which utilizes flip or flip seals.
A class of machines exists in the art generally known as scroll machines which are used for the displacement of various types of fluids. Those scroll machines can be configured as an expander, a displacement engine, a pump, a compressor, etc., and the features of the present invention are applicable to any one of these machines. For purposes of illustration, however, the disclosed embodiments are in the form of a hermetic refrigerant compressor.
Scroll-type apparatus have been recognized as having distinct advantages. For example, scroll machines have high isentropic and volumetric efficiency, and hence are small and lightweight for a given capacity. They are quieter and more vibration free than many compressors because they do not use large reciprocating parts (e.g. pistons, connecting rods, etc.). All fluid flow is in one direction with simultaneous compression in plural opposed pockets which results in less pressure-created vibrations. Such machines also tend to have high reliability and durability because of the relatively few moving parts utilized, the relatively low velocity of movement between the scrolls, and an inherent forgiveness to fluid contamination.
Generally speaking, a scroll apparatus comprises two spiral wraps of similar configuration, each mounted on a separate end plate to define a scroll member. The two scroll members are interfitted together with one of the scroll wraps being rotationally displaced 180 degrees from the other. The apparatus operates by orbiting one scroll member (the orbiting scroll member) with respect to the other scroll member (the non-orbiting scroll) to produce moving line contacts between the flanks of the respective wraps. These moving line contacts create defined moving isolated crescent-shaped pockets of fluid. The spiral scroll wraps are typically formed as involutes of a circle. Ideally, there is no relative rotation between the scroll members during operation, the movement is purely curvilinear translation (no rotation of any line on the body). The relative rotation between the scroll members is typically prohibited by the use of an Oldham coupling.
The moving fluid pockets carry the fluid to be handled from a first zone in the scroll machine where a fluid inlet is provided, to a second zone in the scroll machine where a fluid outlet is provided. The volume of the sealed pocket changes as it moves from the first zone to the second zone. At any one instant of time, there will be at least one pair of sealed pockets, and when there are several pairs of sealed pockets at one time, each pair will have different volumes. In a compressor, the second zone is at a higher pressure than the first zone and it is physically located centrally within the machine, the first zone being located at the outer periphery of the machine.
Two types of contacts define the fluid pockets formed between the scroll members. First, there is axially extending tangential line contacts between the spiral faces or flanks of the wraps caused by radial forces (“flank sealing”). Second, there are area contacts caused by axial forces between the plane edge surfaces (the “tips”) of each wrap and the opposite end plate (“tip sealing”). For high efficiency, good sealing must be achieved for both types of contacts, however, the present invention is concerned with tip sealing.
To maximize efficiency, it is important for the wrap tips of each scroll member to sealingly engage the end plate of the other scroll so that there is minimum leakage therebetween. One way this has been accomplished, other than using tip seals (which are very difficult to assembly and which often present reliability problems) is by using fluid under pressure to axially bias one of the scroll members against the other scroll member. This of course, requires seals in order to isolate the biasing fluid at the desired pressure. Accordingly, there is a continuing need in the field of scroll machines for axial biasing techniques—including improved seals to facilitate the axial biasing.
One aspect of the present invention provides the art with several unique sealing systems for the axial biasing chamber of a scroll-type apparatus. The seals of the present invention are embodied in a scroll compressor and suited for use in machines which use discharge pressure alone, discharge pressure and an independent intermediate pressure, or solely an intermediate pressure, in order to provide the necessary axial biasing forces to enhance tip sealing. In addition, the seals of the present invention are suitable particularly for use in applications which bias the non-orbiting scroll member towards the orbiting scroll member.
A typical scroll machine which is used as a scroll compressor for an air conditioning application is a single volume ratio device. The volume ratio of the scroll compressor is the ratio of the gas volume trapped at suction closing to the gas volume at the onset of discharge opening. The volume ratio of the typical scroll compressor is “built-in” since it is fixed by the size of the initial suction pocket and the length of the active scroll wrap. The built-in volume ratio and the type of refrigerant being compressed determine the single design pressure ratio for the scroll compressor where compression lossed due to pressure ratio mismatch is avoided. The design pressure ratio is generally chosen to closely match the primary compressor rating point, however, it may be biased towards a secondary rating point.
Scroll compressor design specifications for air conditioning applications typically include a requirement that the motor which drives the scroll members must be able to withstand a reduced supply voltage without overheating. While operating at this reduced supply voltage, the compressor must operate at a high-load operating condition. When the motor is sized to meet the reduced supply voltage requirement, the design changes to the motor will generally conflict with the desire to maximize the motor efficiency at the primary compressor rating point. Typically, the increasing of motor output torque will improve the low voltage operation of the motor but this will also reduce the compressor efficiency at the primary rating point. Conversely, any reduction that can be made in the design motor torque while still being able to pass the low-voltage specification allows the selection of a motor which will operate at a higher efficiency at the compressor primary rating point.
Another aspect of the present invention improves the operating efficiency of the scroll compressor through the existence of a plurality of built-in volume ratios and their corresponding design pressure ratios. For exemplary purposes, the present invention is described in a compressor having two built-in volume ratios and two corresponding design pressure ratios. It is to be understood that additional built-in volume ratios and corresponding design pressure ratios could be incorporated into the compressor if desired.
Other advantages and objects of the present invention will become apparent to those skilled in the art from the subsequent detailed description, appended claims and drawings.
Further areas of applicability of the present invention will become apparent from the detailed description provided hereinafter. It should be understood that the detailed description and specific examples, while indicating the preferred embodiment of the invention, are intended for purposes of illustration only and are not intended to limit the scope of the invention.
The present invention will become more fully understood from the detailed description and the accompanying drawings, wherein:
Although the principles of the present invention may be applied to many different types of scroll machines, they are described herein, for exemplary purposes, embodied in a hermetic scroll compressor, and particularly one which has been found to have specific utility in the compression of refrigerant for air conditioning and refrigeration systems.
The following description of the preferred embodiment(s) is merely exemplary in nature and is in no way intended to limit the invention, its application, or uses. Referring now to the drawings in which like reference numerals designate like or corresponding parts throughout the several views, there is shown in
A drive shaft or crankshaft 30 having an eccentric crank pin 32 at the upper end thereof is rotatably journaled in a bearing 34 in main bearing housing 24 and a second bearing 36 in lower bearing housing 26. Crankshaft 30 has at the lower end a relatively large diameter concentric bore 38 which communicates with a radially outwardly inclined smaller diameter bore 40 extending upwardly therefrom to the top of crankshaft 30. Disposed within bore 38 is a stirrer 42. The lower portion of the interior shell 12 defines an oil sump 44 which is filled with lubricating oil to a level slightly above the lower end of a rotor 46, and bore 38 acts as a pump to pump lubricating fluid up the crankshaft 30 and into passageway 40 and ultimately to all of the various portions of the compressor which require lubrication.
Crankshaft 30 is rotatively driven by an electric motor including stator 28, windings 48 passing therethrough and rotor 46 press fitted on crankshaft 30 and having upper and lower counterweights 50 and 52, respectively.
The upper surface of main bearing housing 24 is provided with an annular flat thrust bearing surface 54 on which is disposed an orbiting scroll member 56 having the usual spiral vane or wrap 58 extending upward from an end plate 60. Projecting downwardly from the lower surface of end plate 60 of orbiting scroll member 56 is a cylindrical hub having a journal bearing 62 therein and in which is rotatively disposed a drive bushing 64 having an inner bore 66 in which crank pin 32 is drivingly disposed. Crank pin 32 has a flat on one surface which drivingly engages a flat surface (not shown) formed in a portion of bore 66 to provide a radially compliant driving arrangement, such as shown in assignee's U.S. Pat. No. 4,877,382, the disclosure of which is hereby incorporated herein by reference. An Oldham coupling 68 is also provided positioned between orbiting scroll member 56 and bearing housing 24 and keyed to orbiting scroll member 56 and a non-orbiting scroll member 70 to prevent rotational movement of orbiting scroll member 56.
Non-orbiting scroll member 70 is mounted for limited axial movement with respect to orbiting scroll member 56 and is also provided having a wrap 72 extending downwardly from an end plate 74 which is positioned in meshing engagement with wrap 58 of orbiting scroll member 56. Non-orbiting scroll member 70 has a centrally disposed discharge passage 76 which communicates with an upwardly open recess 78 which in turn is in fluid communication with a discharge muffler chamber 80 defined by cap 14 and partition 22. A first and a second annular recess 82 and 84 are also formed in non-orbiting scroll member 70. Recesses 82 and 84 define axial pressure biasing chambers which receive pressurized fluid being compressed by wraps 58 and 72 so as to exert an axial biasing force on non-orbiting scroll member 70 to thereby urge the tips of respective wraps 58, 72 into sealing engagement with the opposed end plate surfaces of end plates 74 and 60, respectively. Outermost recess 82 receives pressurized fluid through a passage 86 and innermost recess 84 receives pressurized fluid through a plurality of passages 88. Disposed between non-orbiting scroll member 70 and partition 22 are three annular pressure actuated flip seals 90, 92 and 94. Seals 90 and 92 isolate outermost recess 82 from a suction chamber 96 and innermost recess 84 while seals 92 and 94 isolate innermost recess 84 from outermost recess 82 and discharge chamber 80.
Muffler plate 22 includes a centrally located discharge port 100 which receives compressed refrigerant from recess 78 in non-orbiting scroll member 70. When compressor 10 is operating at its full capacity or at its highest design pressure ratio, port 100 discharges compressed refrigerant to discharge chamber 80. Muffler plate 22 also includes a plurality of discharge passages 102 located radially outward from discharge port 100. Passages 102 are circumferentially spaced at a radial distance where they are located above innermost recess 84. When compressor 10 is operating at its reduced capacity or at its lower design pressure ratio, passages 102 discharge compressed refrigerant to discharge chamber 80. The flow of refrigerant through passages 102 is controlled by a valve 104 mounted on partition 22. A valve stop 106 positions and maintains valve 104 on muffler plate 22 such that it covers and closes passages 102.
Referring now to
When the pressurized gas within recess 84 is vented, annular seal 92 will lose sealing because it, like seals 90 and 94, are energized in part by the pressure differential between adjacent recesses 82 and 84. The loss of pressurized fluid in recess 84 will thus cause fluid to leak between recess 82 and recess 84. This will result in the removal of the axial biasing force provided by pressurized fluid within recesses 82 and 84 which will in turn allow separation of the scroll wrap tips with the opposing end plate resulting in a leakage path between discharge chamber 80 and suction chamber 96. This leakage path will tend to prevent the build up of excessive temperatures within compressor 10.
Pressure relief system 112 comprises an axially extending passage 128, a radially extending passage 130 and a pressure relief valve assembly 132. Axial passage 128 intersects with radial passage 130 to connect recess 84 with suction chamber 96. Pressure relief valve assembly 132 is located within a circular bore 134 located at the outer end of passage 130. Pressure relief valve assembly 132 is well known in the art and will therefore not be described in detail. When the pressure of refrigerant within recess 84 exceeds a predetermined pressure, pressure relief valve assembly 132 will open to allow fluid flow between recess 84 and suction chamber 96. The venting of fluid pressure by valve assembly 132 will affect compressor 10 in the same manner described above for temperature protection system 110. The leakage path which is created by valve assembly 132 will tend to prevent the build-up of excessive pressures within compressor 10. The response of valve assembly 132 to excessive discharge pressures is improved if the compressed pocket that is in communication with recess 84 is exposed to discharge pressure for a portion of the crank cycle. This is the case if the length of the active scroll wraps 58 and 72 needed to compress between an upper design pressure ratio 140 and a lower design pressure 142 (
Referring now to
Thus, if the operating point for compressor 10 is above lower design pressure ratio 142, the gas within the scroll pockets is compressed along the full length of wraps 58 and 72 in the normal manner to be discharged through passage 76, recess 78 and port 100. If the operating point for compressor 10 is at or below lower design pressure ratio 142, the gas within the scroll pockets is able to discharge through passages 102 by opening valve 104 before reaching the inner ends of scroll wraps 58 and 72. This early discharging of the gas avoids losses due to compression ratio mismatch.
Outermost recess 82 acts in a typical manner to offset a portion of the gas separating forces in the scroll compression pockets. The fluid pressure within recess 82 axially bias the vane tips of non-orbiting scroll member 70 into contact with end plate 60 of orbiting scroll member 56 and the vane tips of orbiting scroll member 56 into contact with end plate 74 of non-orbiting scroll member 70. Innermost recess 84 acts in this typical manner at a reduced pressure when the operating condition of compressor 10 is below lower design pressure ratio 142 and at an increased pressure when the operating condition of compressor 10 is at or above lower design pressure ratio 142. In this mode, recess 84 can be used to improve the axial pressure balancing scheme since it provides an additional opportunity to minimize the tip contact force.
In order to minimize the re-expansion losses created by axial passages 88 and 102 used for early discharge end, the volume defined by innermost recess 84 should be held to a minimum. An alternative to this would be to incorporate a baffle plate 150 into recess 84 as shown in
Referring now to
Referring now to
Referring now to
Referring now to
Referring now to
While not specifically illustrated, it is within the scope of the present invention to configure each of valves 404 such that they perform the function of both opening passages 402 and minimize the re-expansion losses created through passages 88 in a manner equivalent to that of baffle plate 150.
With reference to
Center flip seal 92 is disposed within a groove 204 located within non-orbiting scroll member 70. One leg of flip seal 92 extends into groove 204 while the other leg extends generally horizontal, as shown in
Inner flip seal 94 is disposed within a groove 208 located within non-orbiting scroll member 70. One leg of flip seal 94 extends into groove 208 while the other leg extends generally horizontal, as shown in
Seals 90, 92 and 94 therefore provide three distinct seals; namely, an inside diameter seal of seal 94, an outside diameter seal of seal 90, and a middle diameter seal of seal 92. The sealing between muffler plate 22 and seal 94 isolates fluid under intermediate pressure in recess 84 from fluid under discharge pressure. The sealing between muffler plate 22 and seal 90 isolates fluid under intermediate pressure in recess 82 from fluid under suction pressure. The sealing between muffler plate 22 and seal 92 isolates fluid under intermediate pressure in recess 84 from fluid under a different intermediate pressure in recess 82. Seals 90, 92 and 94 are pressure activated seals as described below.
Grooves 200, 204 and 208 are all similar in shape. Groove 200 will be described below. It is to be understood that grooves 204 and 208 include the same features as groove 200. Groove 200 includes a generally vertical outer wall 240, a generally vertical inner wall 242 and an undercut portion 244. The distance between walls 240 and 242, the width of groove 200, is designed to be slightly larger than the width of seal 90. The purpose for this is to allow pressurized fluid from recess 82 into the area between seal 90 and wall 242. The pressurized fluid within this area will react against seal 90 forcing it against wall 240 thus enhancing the sealing characteristics between wall 240 and seal 90. Undercut 244 is positioned to lie underneath the generally horizontal portion of seal 90 as shown in
The unique installed L-shaped configuration of seals 90, 92 and 94 of the present invention are relatively simple in construction, easy to install and inspect, and effectively provide the complex sealing functions desired. The unique sealing system of the present invention comprises three flip seals 90, 92 and 94 that are Astretched≅into place and then pressure activated. The unique seal assembly of the present invention reduces overall manufacturing costs for the compressor, reduces the number of components for the seal assembly, improves durability by minimizing seal wear and provides room to increase the discharge muffler volume for improved damping of discharging pulse without increasing the overall size of the compressor.
The seals of the present invention also provide a degree of relief during flooded starts. Seals 90, 92 and 94 are designed to seal in only one direction. These seals can then be used to relieve high pressure fluid from the intermediate chambers or recesses 82 and 84 to the discharge chamber during flooded starts, thus reducing inter-scroll pressures and the resultant stress and noise.
Referring now to
Referring now to
Referring now to
Non-orbiting scroll member 470 includes scroll wrap 72 and it defines an annular recess 484, an outer seal groove 486 and an inner seal groove 488. Annular recess 484 is located between outer seal groove 486 and inner seal groove 488 and it is provided compressed fluid through fluid passage 88 which opens to a fluid pocket defined by non-orbiting scroll wrap 72 of non-orbiting scroll member 470 and orbiting scroll wrap 58 of orbiting scroll member 56. The pressurized fluid provided through fluid passage 88 is at a pressure which is intermediate or in between the suction pressure and the discharge pressure of the compressor. The fluid pressure within annular recess 484 biases non-orbiting scroll member 470 towards orbiting scroll member 56 to enhance the tip sealing characteristics between the two scroll members.
A flip seal 490 is disposed within outer seal groove 486 and a flip seal 492 is disposed within inner seal groove 488. Flip seal 490 sealingly engages non-orbiting scroll member 470 and partition 422 to isolate annular recess 484 from suction pressure. Flip seal 492 sealing engages non-orbiting scroll member 470 and partition 422 to isolate annular recess 484 from discharge pressure. While not illustrated in
Referring now to
Non-orbiting scroll member 570 includes scroll wrap 72 and it defines an annular recess 584, an outer seal groove 586 and an inner seal groove 588. Annular recess 584 is located between outer seal groove 586 and inner seal groove 588 and it is provided with compressed fluid through fluid passage 88 which opens to a fluid pocket defined by non-orbiting scroll wrap 72 of non-orbiting scroll member 570 and orbiting scroll wrap 58 of orbiting scroll member 56. The pressurized fluid provided through fluid passage 88 is at a pressure which is intermediate or in between the suction pressure and the discharge pressure of the compressor. The fluid pressure within annular recess 586 biases non-orbiting scroll member 570 towards orbiting scroll member 56 to enhance the tip scaling characteristics between the two scroll members.
A flip seal 590 is disposed within outer seal groove 586 and a flip seal 592 is disposed within inner seal groove 588. Flip seal 590 sealingly engages non-orbiting scroll member 570 and partition 522 to isolate annular recess 584 from suction pressure. Flip seal 592 sealingly engages non-orbiting scroll member 570 and partition 522 to isolate annular recess 584 from discharge pressure. While not specifically illustrated in
Referring now to
Non-orbiting scroll member 670 includes scroll wrap 72 and it defines an annular recess 684. Partition 622 defines an outer seal groove 686 and an inner seal groove 688. Annular recess 684 is located between outer seal groove 686 and inner seal groove 688 and it is provided compressed fluid through fluid passage 88 which opens to a fluid pocket defined by non-orbiting scroll wrap 72 of non-orbiting scroll member 670 and orbiting scroll wrap 58 of orbiting scroll member 56. The pressurized fluid provided through fluid passage 88 is at a pressure which is intermediate or in between the suction pressure and the discharge pressure of the compressor. The fluid pressure within recess 684 biases non-orbiting scroll member 270 towards orbiting scroll member 56 to enhance the tip sealing characteristics between the two scroll members.
A flip seal 690 is disposed within outer seal groove 686 and a flip seal 692 is disposed within inner seal groove 608. Flip seal 690 sealingly engages non-orbiting scroll member 670 and partition 622 to isolate annular recess 684 from suction pressure. Flip seal 692 sealing engages non-orbiting scroll member 670 and partition 622 to isolate annular recess 684 from discharge pressure. While not specifically illustrated in
Referring now to
Non-orbiting scroll member 770 includes scroll wrap 72 and it defines an annular recess 784, an outer seal groove 786 and an inner seal groove 788. A passage 782 interconnects annular recess 784 with outer seal groove 786. Annular chamber 784 is located between outer seal groove 786 and inner seal groove 788 and it is provided compressed fluid through fluid passage 88 which opens to a fluid pocket defined by non-orbiting scroll wrap 72 of non-orbiting scroll member 770 and orbiting scroll wrap 58 of orbiting scroll member 56. The pressurized fluid provided through fluid passage 88 is at a pressure which is intermediate or in between the suction pressure and the discharge pressure of the compressor. The fluid pressure within annular chamber 784 biases non-orbiting scroll member 770 towards orbiting scroll member 56 to enhance the tip sealing characteristics between the two scroll members.
A flip seal 790 is disposed within outer seal groove 786 and a flip seal 792 is disposed within inner seal groove 788. Flip seal 790 sealing engages non-orbiting scroll member 770 and cap 714 to isolate annular recesses 784 from suction pressure. Flip seal 792 sealingly engages non-orbiting scroll member 770 and cap 714 to isolate annular recesses 784 from discharge pressure. While not illustrated in
Referring now to
Referring now to
Non-orbiting scroll member 870 includes scroll wrap 72 and it defines an annular chamber 884. Partition 822 defines an outer seal groove 886 and an inner seal groove 888. Annular chamber 884 is located between outer seal groove 886 and inner seal groove 888 and it is provided compressed fluid through fluid passage 88 which opens to a fluid pocket defined by non-orbiting scroll wrap 72 of non-orbiting scroll member 870 and orbiting scroll wrap 58 of orbiting scroll member 56. The pressurized fluid provided through fluid passage 88 is at a pressure which is intermediate or in between the suction pressure and the discharge pressure of the compressor. The fluid pressure within annular chamber 884 biases non-orbiting scroll member 870 towards orbiting scroll member 56 to enhance the tip sealing characteristics between the two scroll members.
A flip seal 890 is disposed within outer seal groove 886 and a flip seal 892 is disposed within inner seal groove 888. Flip seal 890 engages non-orbiting scroll member 870 and partition 822 to isolate annular chamber 884 from suction pressure. Flip seal 892 sealingly engages non-orbiting scroll member 870 and partition 822 to isolate annular chamber 884 from discharge pressure. While not illustrated in
Referring now to
Non-orbiting scroll member 970 includes scroll wrap 72 and it defines an annular recess 984. Disposed within annular recess 984 is a floating seal 950. The basic concept for floating seal 950 with axial pressure biasing is disclosed in much greater detail in Assignee's U.S. Pat. No. 4,877,382, the disclosure of which is incorporated herein by reference. Floating seal 950 comprises a base ring 952, a sealing ring 954, an outer flip seal 990 and an inner flip seal 992. Flip seals 990 and 992 are sandwiched between rings 952 and 954 and are held in place by a plurality of posts 956 which are an integral part of base ring 952. Sealing ring 954 includes a plurality of holes 958 which correspond with the plurality of posts 956. Once base ring 952, seals 990 and 992 and sealing ring 954 are assembled, posts 956 are mushroomed over to complete the assembly of floating seal 950. While seals 990 and 992 are described as being separate components, it is within the scope of the present invention to have a single piece component provide seals 990 and 992 with this single piece component including a plurality of holes which correspond with the plurality of posts 956.
Annular recess 984 is provided compressed fluid through fluid passage 88 which opens to a fluid pocket defined by non-orbiting scroll wrap 72 of non-orbiting scroll member 970 and orbiting scroll wrap 58 of orbiting scroll member 56. The pressurized fluid provided through fluid passage 88 is at a pressure which is intermediate or in between the suction pressure and the discharge pressure of the compressor. The fluid pressure within annular recess 984 biases non-orbiting scroll member 970 towards orbiting scroll member 56 to enhance the tip sealing characteristics between the two scroll members. In addition, fluid pressure within annular recess 984 biases floating seal member 950 against upper cap 914 of the compressor. Sealing ring 954 engages upper cap 914 to seal the suction pressure area of the compressor from the discharge area of the compressor. Flip seal 990 sealingly engages non-orbiting scroll member 970 and rings 952 and 954 to isolate annular recess 984 from suction pressure. Flip seal 992 sealingly engages non-orbiting scroll member 970 and rings 952 and 954 to isolate annular recess 984 from discharge pressure. While not specifically illustrated in
Referring now to
Referring now to
Referring now to
While not specifically illustrated, vapor injection systems 730 and 930 can be designed to provide for delayed suction closing instead of vapor injection. When designed for delayed suction closing, system 730 and 930 would extend between one of the closed pockets defined by the scroll wraps and the suction area of the compressor. The delayed suction closing systems provide for capacity modulation as is well known in the art and can also be operated in a pulse width modulation manner. In addition, the vapor injection system illustrated in
While the above detailed description describes the preferred embodiment of the present invention, it should be understood that the present invention is susceptible to modification, variation and alteration without deviating from the scope and fair meaning of the subjoined claims.
This application is a continuation of U.S. patent application Ser. No. 11/435,386 filed May 16, 2006, which is a continuation of U.S. patent application Ser. No. 10/726,713 filed Dec. 3, 2003 which is a continuation of U.S. patent application Ser. No. 10/195,280 filed Jul. 15, 2002 which is a continuation-in-part of U.S. patent application Ser. No. 09/688,549 filed on Oct. 16, 2000. The disclosure of the above application is incorporated herein by reference.
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| Number | Date | Country | |
|---|---|---|---|
| Parent | 11435386 | May 2006 | US |
| Child | 11750783 | US | |
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| Child | 10726713 | US |
| Number | Date | Country | |
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| Parent | 09688549 | Oct 2000 | US |
| Child | 10195280 | US |
