Source: http://www.freepatentsonline.com/9458847.html
Timestamp: 2017-10-22 06:42:23
Document Index: 83336417

Matched Legal Cases: ['Application No. 2006800398775', 'Application No. 06816736', 'Application No. 201210193771', 'Application No. 2012101939569', 'Application No. 201210193956', 'Application No. 201210193771']

Scroll compressor having biasing system - Emerson Climate Technologies, Inc.
Scroll compressor having biasing system
United States Patent 9458847
A compressor may include non-orbiting scroll, an orbiting scroll, and a bearing housing. The non-orbiting scroll may include a recess. The orbiting scroll may be intermeshed with the non-orbiting scroll to from a plurality of compression pockets therebetween. The orbiting scroll may include first and second apertures. The first aperture may communicate with one of the compression pockets. The second aperture may communicate with the recess. The bearing housing may support the orbiting scroll and cooperate with the orbiting scroll to define a chamber therebetween. The chamber may communicate with the first and second apertures.
Ignatiev, Kirill M. (Sidney, OH, US)
Fogt, James F. (Sidney, OH, US)
Akei, Masao (Miamisburg, OH, US)
14/319756
Emerson Climate Technologies, Inc. (Sidney, OH, US)
F03C2/00; F03C4/00; F04C18/00; F04C18/02; F04C23/00; F04C27/00; F04C29/00; F04C29/02
418/55, 418/57, 418/270, 417/310
Download PDF 9458847 PDF help
7837452 Scroll compressor including deflection compensation for non-orbiting scroll 2010-11-23 Ignatiev et al.
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Passasge / Definition of Passage by Merriam-Webster—http://www.merriam-webster.com/dictionary/passage—Mar. 20, 2016.
Aperture / Definition of Aperture by Merriam-Webster—http://www.merriam-webster.com/dictionary/aperture—Mar. 20, 2016.
Non-Final Office Action issued by U.S. Patent and Trademark Office dated Apr. 25, 2008 from related U.S. Appl. No. 11/259,237, filed Oct. 26, 2005, entitled “Scroll Compressor” (10 pages).
Final Office Action issued by U.S. Patent and Trademark Office dated Oct. 31, 2008 from related U.S. Appl. No. 11/259,237, filed Oct. 26, 2005, entitled “Scroll Compressor” (8 pages).
Office Action issued by U.S. Patent and Trademark Office dated Feb. 18, 2010 from related U.S. Appl. No. 12/420,519, filed Apr. 8, 2009, entitled “Scroll Compressor Including Deflection Compensation for Non-Orbiting Scroll” (15 pages).
Non-final Office Action regarding U.S. Appl. No. 12/938,848 mailed Jan. 6, 2012.
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Second Office Action received from the State Intellectual Property Office of People's Republic of China, dated Jan. 20, 2012, regarding Application No. 2006800398775. Translation provided by Unitalen Attorneys at Law.
U.S. Office Action regarding U.S. Appl. No. 13/528,285 mailed Jul. 1, 2013.
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First Office Action and Search Report issued by the State Intellectual Property Office (SIPO) regarding China Application No. 201210193771.8 dated Apr. 1, 2014. Translation provided by Unitalen Attorneys at Law.
First Office Action and Search Report issued by the State Intellectual Property Office (SIPO) regarding China Application No. 2012101939569 dated Apr. 1, 2014. Translation provided by Unitalen Attorneys at Law.
Second Office Action regarding China Application No. 201210193956.0 dated Dec. 3, 2014. Translation provided by Unitalen Attorneys at Law.
Second Office Action regarding China Application No. 201210193771.8 dated Dec. 18, 2014. Translation provided by Unitalen Attorneys at Law.
This application is a continuation of U.S. patent application Ser. No. 13/528,285 filed on Jun. 20, 2012, which is a continuation of U.S. patent application Ser. No. 12/938,848 filed on Nov. 3, 2010, now U.S. Pat. No. 8,226,387, which is a continuation of U.S. patent application Ser. No. 12/420,519 filed on Apr. 8, 2009, now U.S. Pat. No. 7,837,452, which is a continuation of U.S. patent application Ser. No. 11/259,237 filed on Oct. 26, 2005, now abandoned. The disclosure of each of the above applications is incorporated herein by reference.
1. A compressor comprising: a non-orbiting scroll including a first recess; an orbiting scroll intermeshed with said non-orbiting scroll to form a plurality of compression pockets therebetween, said orbiting scroll including first and second passages, said first passage communicating with one of said compression pockets, said second passage communicating with said first recess; and a bearing housing supporting said orbiting scroll and defining a second recess adjacent to said orbiting scroll, said second recess communicating with said first and second passages.
2. The compressor of claim 1, further comprising a shell assembly defining a suction-pressure zone, wherein said first recess is intermittently in communication with said suction-pressure zone via said second passage.
3. The compressor of claim 2, wherein said first recess is intermittently in communication with said second recess when said first recess is fluidly isolated from said suction-pressure zone.
4. The compressor of claim 1, wherein said first recess is disposed in an axial end of said non-orbiting scroll that faces said orbiting scroll.
5. The compressor of claim 4, wherein said first recess is disposed radially outward relative to a spiral wrap of said non-orbiting scroll.
6. The compressor of claim 1, wherein said second passage is disposed radially outward relative to a spiral wrap of said orbiting scroll.
7. The compressor of claim 1, further comprising a floating seal disposed within said second recess and sealing against said orbiting scroll and axially extending walls of said second recess.
8. The compressor of claim 1, further comprising a shell assembly defining a suction-pressure zone, wherein said second recess receives pressurized working fluid from said compression pocket to axially bias said orbiting scroll.
9. The compressor of claim 1, wherein said orbiting scroll is axially movable relative to said bearing housing and said non-orbiting scroll.
10. The compressor of claim 9, wherein said non-orbiting scroll is fixedly secured to said bearing housing.
11. The compressor of claim 1, wherein said non-orbiting scroll includes a plurality of first recesses, and wherein said orbiting scroll includes a plurality of second passages communicating with said second recess, wherein all of said plurality of first recesses are disposed radially outward relative to a spiral wrap of said non-orbiting scroll and are disposed in an axial end of said non-orbiting scroll that faces said orbiting scroll, each of said plurality of first recesses communicating with said second passages and intermittently communicating with a suction-pressure zone of the compressor.
12. A compressor comprising: a non-orbiting scroll including a first recess; an orbiting scroll intermeshed with said non-orbiting scroll and including an end plate having a passage extending therethrough, said passage communicating with said first recess, said first recess intermittently communicating with a suction-pressure zone of the compressor via said passage; and a bearing housing supporting said orbiting scroll and defining a second recess containing pressurized working fluid biasing said orbiting scroll toward said non-orbiting scroll, said second recess intermittently communicating with said passage.
13. The compressor of claim 12, further comprising another passage in said orbiting scroll communicating with said second recess and a compression pocket defined by spiral wraps of said orbiting and non-orbiting scrolls.
14. The compressor of claim 12, wherein said first recess is intermittently in communication with said second recess when said first recess is fluidly isolated from said suction-pressure zone.
15. The compressor of claim 12, wherein said first recess is disposed in an axial end of said non-orbiting scroll that faces said orbiting scroll.
16. The compressor of claim 15, wherein said first recess is disposed radially outward relative to a spiral wrap of said non-orbiting scroll.
17. The compressor of claim 12, wherein said passage is disposed radially outward relative to a spiral wrap of said orbiting scroll.
18. The compressor of claim 12, further comprising a floating seal disposed within said second recess and sealing against said orbiting scroll and axially extending walls of said second recess.
19. The compressor of claim 12, wherein said non-orbiting scroll is fixedly secured to said bearing housing.
20. The compressor of claim 12, wherein said non-orbiting scroll includes a plurality of first recesses, and wherein said orbiting scroll includes a plurality of passages communicating with said second recess, wherein all of said plurality of first recesses are disposed radially outward relative to a spiral wrap of said non-orbiting scroll and are disposed in an axial end of said non-orbiting scroll that faces said orbiting scroll, each of said plurality of first recesses communicating with said passages and intermittently communicating with said suction-pressure zone of the compressor.
A compressor may include a shell assembly, a first scroll member located within the shell assembly and including a first end plate and a first spiral wrap extending from the first end plate, and a second scroll member located within the shell assembly, supported for orbital movement relative to the first scroll member and including a second end plate and a second spiral wrap extending from the second end plate and meshingly engaged with the first spiral wrap to form compression pockets. The first scroll member may define a fluid injection port and the second scroll member may define a passage in communication with the fluid injection port and at least one of the compression pockets to provide pressurized vapor from the fluid injection port to the at least one of the compression pockets.
The compressor may additionally include a drive shaft engaged with the second scroll member and the fluid injection port may extend through the first end plate and the passage may extend through the second end plate and may be intermittently in communication with the fluid injection port. Initial communication between the fluid injection port and the passage may occur just after an outermost one of the compression pockets is formed by being sealed off from a suction pressure region of the shell assembly. Communication between the fluid injection port and the passage may be terminated after ninety degrees of rotation of the drive shaft after the initial communication between the fluid injection port and the passage occurs. Communication between the fluid injection port and the passage may be terminated after ninety degrees of rotation of the drive shaft after an outermost one of the compression pockets is formed by being sealed off from a suction pressure region of the shell assembly. The first scroll member may be axially fixed relative to the shell assembly and the second scroll member may be axially displaceable relative to the shell assembly and the first scroll member.
The passage may include a first axial passage extending partially through the second end plate and in communication with the fluid injection port, a radial passage extending from the first axial passage through the second end plate and a second axial passage extending from the radial passage and in communication with the at least one of the compression pockets. The compressor may include a third axial passage extending from the radial passage and in communication with another one of the compression pockets.
The compressor may additionally include a vapor injection system having a pressurized vapor source in communication with the fluid injection port. The shell assembly may include an end cap and the vapor injection system may include a fluid line extending through the end cap and providing the pressurized vapor source to the fluid injection port. The compressor may include a drive shaft engaged with the second scroll member and the fluid injection port may extend through the first end plate and the passage may extend through the second end plate and may be intermittently in communication with the fluid injection port. Initial communication between the fluid injection port and the passage may occur just after an outermost one of the compression pockets is formed by being sealed off from a suction pressure region of the shell assembly. Communication between the fluid injection port and the passage may be terminated after ninety degrees of rotation of the drive shaft after the initial communication between the fluid injection port and the passage occurs. Communication between the fluid injection port and the passage may be terminated after ninety degrees of rotation of the drive shaft after an outermost one of the compression pockets is formed by being sealed off from a suction pressure region of the shell assembly. The first scroll member may be axially fixed relative to the shell assembly and the second scroll member may be axially displaceable relative to the shell assembly and the first scroll member.
In another form, the present disclosure provides a compressor that includes a non-orbiting scroll, an orbiting scroll, and a bearing housing. The non-orbiting scroll may include a recess. The orbiting scroll may be intermeshed with the non-orbiting scroll to from a plurality of compression pockets therebetween. The orbiting scroll may include first and second apertures. The first aperture may communicate with one of the compression pockets. The second aperture may communicate with the recess. The bearing housing may support the orbiting scroll and cooperate with the orbiting scroll to define a chamber therebetween. The chamber may communicate with the first and second apertures.
FIG. 3a is an enlarged view of the biasing system illustrated in FIG. 1;
FIG. 3b is an enlarged view of a biasing system in accordance with another embodiment of the present invention;
FIGS. 4a-4c are plan views of the scroll members and the biasing system illustrated in FIG. 3a;
FIGS. 7a-7c are plan views of the scroll members and the vapor injection system illustrated in FIG. 6;
FIG. 11a is a plan view of a force diagram for the orbiting scroll member of the present invention;
FIG. 11b is a side view force diagram for the orbiting scroll member taken along the radial axis;
FIG. 11c is a side view force diagram for the orbiting scroll member taken along the tangential axis;
FIGS. 19a-19d illustrate the relationship between the passages, the recesses and the sealing lip for the scroll compressor illustrated in FIG. 10;
Referring now to FIGS. 1-3a, orbiting scroll member 56 and non-orbiting scroll member 70 are illustrated in greater detail. Non-orbiting scroll member 70 is fixedly secured to two-piece upper bearing housing 26 by a plurality of bolts 80 which prohibit all movement of non-orbiting scroll member 70 with respect to upper bearing housing 26. Orbiting scroll member 56 is disposed between non-orbiting scroll member 70 and upper bearing housing 26. Orbiting scroll member 56 can move radially as described above in relation to the radially compliant drive for compressor 10. Orbiting scroll member 56 can also move axially by means of a floating thrust seal 82 disposed within annular recess 54.
Referring now to FIG. 3b, a biasing system in accordance with another embodiment of the present invention is disclosed. FIG. 3b illustrates floating thrust seal 82′ which is the same as floating thrust seal 82 except that annular valve body 84 is replaced by a three piece annular body 84a, 84b and 84c.
Floating thrust seal 82′ comprises annular valve bodies 84a, 84b and 84c, an inner lip seal 86 and an outer lip seal 88. Annular valve body 84a defines an inner face seal 90 and an outer face seal 92 which are urged against end plate 60 of orbiting scroll member 56 by fluid pressure supplied to recess 54 through a plurality of passages 94 extending through annular valve body 84a. Inner lip seal 86 is located between annular valve body 84a and 84b and it seals against an inner wall of recess 54, outer lip seal 88 is located between annular valve body 84a and 84c and it seals against an outer wall of recess 54 and face seals 90 and 92 seal against end plate 60 of orbiting scroll member 56 to isolate recess 54 from suction pressure refrigerant within shell 12. The use of the three piece annular valve bodies 84a, 84b and 84c allows lip seals 86 and 88 to operate independently from each other. The design parameters for floating thrust seal 82 are selected in such a way that, under internal pressurization, annular valve body 84a stays in constant contact with end plate 60 or orbiting scroll member 56 by means of face seals 90 and 92. The majority of the axial biasing load applied to orbiting scroll member 56 is supplied by the refrigerant gas pressure within recess 54 rather than by mechanical contact between face seals 90 and 92 and end plate 60 of orbiting scroll member 56. This reduces mechanical friction and wear of face seals 90 and 92 and the corresponding surface of end plate 60 of orbiting scroll member 56. Pressurization of recess 54 is achieved using one or more passages 96 which extend from an area of end plate 60 open to recess 54 through end plate 60 and through scroll wrap 58 of orbiting scroll member 56.
During orbiting motion of orbiting scroll member 56 with respect to non-orbiting scroll member 70, the end of the one or more passages 96 extending through scroll wrap 58 connects to one of the moving pockets defined by scroll wraps 58 and 72 by means of a recess 98 which is machined into end plate 74 of non-orbiting scroll member 70. The location, size and shape of the one or more passages 96 and recess 98 will determine the opening and closing of gas communication between the compressed gas in the moving pocket and recess 54. In addition, the transition time of the pressure equalization between the moving pocket and recess 54 is controlled by the location, size and shape of the one or more passages 96 and recess 98. The timing of the opening and closing in conjunction with the transition time can be selected such that it will minimize excessive axial force applied to end plate 60 of orbiting scroll member 56 but at the same time the axial force will keep orbiting scroll member 56 in constant contact with non-orbiting scroll member 70. FIG. 4a illustrates the beginning of the opening of communication, FIG. 4b illustrates an opened communication and FIG. 4c illustrates the closing of communication between recess 98 and one passage 96.
Referring now to FIGS. 6 and 7a-7c, a vapor injection system 120 in accordance with the present invention is illustrated. The source for vapor injection is located external to compressor 10 and it is supplied from a fluid line (not shown) which extends through cap 14. Non-orbiting scroll member 70 defines a fluid injection port 122 to which the fluid line is attached to supply the pressurized vapor to scroll members 56 and 70. Fluid injection port 122 is in communication with an axial passage 124 in orbiting scroll member 56. Axial passage 124 is in communication with a radial passage 126 which is in turn in communication with a pair of axial passages 128 which open into the moving fluid pockets defined by scroll wraps 58 and 72. In order to achieve the necessary amount of vapor introduced into the moving pockets, opening and closing of communication between port 122 and passage 124 must be controlled. The opening of port 122 to passage 124 should begin just after the moving pocket is formed by being sealed from the suction area of compressor 10. The closing of port 122 to passage 124 should happen after approximately ninety degrees of rotation of orbiting scroll member 56. Because of the relative orbiting motion of orbiting scroll member 56 with respect to non-orbiting scroll member 70, the proper selection of relative locations of port 122, passage 124 and passages 128 make it possible to control the opening and closing of vapor injection system 120. Opening and closing of vapor injection system 120 to provide vapor to the moving pockets can be achieved by either lowering and uncovering passages 128 on end plate 60 of orbiting scroll member 56 by scroll wrap 72 of non-orbiting scroll member or by opening and closing communication between port 122 and passage 124 or by a combination of both.
FIG. 7a illustrates scroll members 56 and 70 corresponding to the point where the moving pockets defined by scroll wraps 58 and 72 are initially sealed off from the suction area of compressor 10. Communication between port 122 and passage 124 is just starting to take place and passages 128 are just beginning to be uncovered by scroll wrap 72. FIG. 7b illustrates scroll members 56 and 70 corresponding to the position forty-five degrees of rotation after the initial sealing point illustrated in FIG. 7a. Port 122 is open to passage 124 and passages 128 are not covered by scroll wrap 72 to provide for vapor injection. FIG. 7c illustrates scroll members 56 and 70 corresponding to the position ninety degrees of rotation after the initial sealing paint illustrated in FIG. 7a. Port 122 has just closed communication with passage 124 to stop vapor injection by vapor injection system 120.
Floating thrust seal 382 comprises a pair of annular valve bodies 384 with one annular body 384 sealingly engaging the interior wall of recess 54 at 386 and the other annular body 384 sealingly engaging the exterior wall of recess 54 at 388. Annular valve bodies 384 define an inner face seal 390 and an outer face seal 392 which are urged against end plate 360 of orbiting scroll member 356 by fluid pressure supplied to recess 54. The seal at 386 seals against the inner wall of recess 54, the seal at 388 seals against the outer wall of recess 54 and face seals 390 and 392 seal against end plate 360 of orbiting scroll member 356 to isolate recess 54 from suction pressure refrigerant within shell 12. The design parameters for floating thrust seal 382 are selected in such a way that, under internal pressurization, annular valve bodies 384 stay in constant contact with end plate 360 of orbiting scroll member 356 by means of face seals 390 and 392. The majority of the axial biasing load applied to orbiting scroll member 356 is supplied by the refrigerant gas pressure within recess 54 rather than by mechanical contact between face seals 390 and 392 and end plate 360 of orbiting scroll member 356. This reduces mechanical friction and wear of face seals 390 and 392 and the corresponding surface of end plate 360 of orbiting scroll member 356. While not illustrated in FIG. 10, pressurization of recess 54 is achieved using one or more passages 96 which extend from an area of end plate 360 open to recess 54 through end plate 360 to one or more of the compression chambers formed by wraps 358 and 372 as shown in FIGS. 1-4c. Also, scroll compressor 10 can include the optional oil injection system 212 illustrated above for compressor 210.
There is another circumstance which requires an unwanted excessive force. This is due to the presence of the “scroll particular” over-turning moment which is schematically illustrated in FIGS. 11a-11c. Since the separation force FSP and the holding force FHOLD are separately placed by a half of the orbiting radius ROR, the centroid of the excessive force FTH needs to occur at the opposite side of the axis (shown in X) in order to balance out the moment from the two forces FSP and FHOLD. As seen in FIG. 11b, the force balance in the axial direction can be represented by the following equation [1].
FHOLD=FTH+FSP [1]
The location X illustrated in FIG. 11b becomes off setting from the central axis with which the holding force FHOLD gets close to the separation force FSP to eliminate the excessive force and its location can be represented by the following equation [2].
X=ROR2·FSP-C·FRADFTH+ROR[2]
X=ROR2·FSP-C·FRADFHOLD-FSP+ROR[3]
Y·FTH=C·FTAN [4]
Y=C·FTANFTH[5]
Y=C·FTANFHOLD-FSP[6]
As indicated, the Y location also becomes off from the central axis by minimizing the excessive force (FHOLD-FSP). For most of scroll compressors, the FTH positions near the tangential line, which is extended from the center of the orbiting scroll toward the rotation direction of the orbit. As the tangential and radial axes rotate, FTH moves along the tangential axis resulting in drawing a closed loop trajectory as illustrated in FIG. 12 by the dashed line. If no axial surface is provided between the mating scroll members at the location of FTH, the orbiting scroll member will tilt over and thus result in the scroll compressor being inoperative. Therefore, the excessive force is allowed to be reduced only within the range of which FTH does not go across the outer edge of the axial surface between the mating scrolls.
Preferably, four passages 396a-d are arranged circumferentially around end plate 360 at a ninety degree interval at a diameter of CBH from the center of orbiting scroll member 356. The diameter DBH for each passage 396 is preferred, but not limited to be matched to a seal width of outer face seal 392. Preferably four recesses 398a-d are arranged circumferentially around end plate 374 at a diameter CGR. The four recesses 398 are not interconnected with each other and thus they can each be treated as an independent volume. The depth of each recess tGR is preferred, but not limited to be considerably small such as less than a millimeter. Recesses 398 are arranged at ninety degree interval on diameter CGR from the center of non-orbiting scroll member 370. Recesses 398 are preferred but are not limited for each to have a width LGR which is equal to or greater than twice the orbiting radius ROR. The diameter CGR is preferred to be the same size of diameter CBH of passage 396. Also, the diameter CGR is preferred, but not limited to be the same as the diameter CSEAL of outer face seal 392. The matching of diameters CGR and CSEAL permit the fabrication of the plurality of passages 396 by a simple vertical drilling operation.
FIGS. 19a-19d show the positional relationship between the passages 396, the recesses 398 and the outer sealing surface of outer face seal 392 at each ninety degree rotation of orbiting scroll member 356 with respect to non-orbiting scroll member 370. The relative position of each passage 396 and the outer sealing surface of outer face seal 392 are successively changed as the center Oos of orbiting scroll member 356 orbits on the orbiting circle COR around the center OFS of non-orbiting scroll member 370. Each passage 396 comes across the axial sealing surface of outer face seal 392 twice during one revolution of orbiting scroll member 356. Thus, the bottoms of passages 396 are repeatedly and alternately exposed to high pressure (e.g., discharge pressure) and low pressure (e.g., suction pressure) refrigerant environments. The exposure of each passage 396 becomes phase-delayed by ninety degrees such that the exposures occur on respective passages 396 one after another during the orbital motion.
In the crank position illustrated in FIG. 19a, passage 396a is located at the ending position of the exposure to the inside of recess 54 which holds a higher pressure than the suction area of scroll compressor 310. Thus, at this crank position, the pressure within recess 398a reaches its maximum, generating a peak force to counteract the excessive force FTH, which is generated by the overturning moment. Since the pressure within recess 398 is uniform, the location of the force should be represented by the centroid of the recesses axial area, which is shown in FIG. 16 as FGRA.
As the orbital motion proceed from the crank position illustrated in FIG. 19a to that illustrated in 19b, passage 396a comes across the outer sealing surface of outer face seal 392 and will be exposed to the suction area of scroll compressor 310. The pressure within recess 398a will start to decrease and thus reduce the counteracting from recess 398a. On the next recess 398b, however, the respective passage 396b is approaching the end position of the exposure to the inside of pressurized recess 54 which is increasing the pressure within recess 398b. In the middle position between FIGS. 19a and 19b, therefore, both recesses 398a and 398b hold an intermediate pressure which generates intermediate counteracting forces at both FGRA and FGRB. These two forces can also be represented by the centroid of the two recesses which is located between the two centroids of the two recesses. The location of the counteracting force therefore moves circumferentially in the direction of the orbital motion and follows the movement of FTH which is illustrated in FIG. 12 by the dashed line. FIGS. 19c and 19d each illustrate an additional ninety degrees of orbital motion.
The passages 396a-d are illustrated as vertical and straight on the premise of which diameter of the concentric circles of recesses CGR matches with the diameter of the sealing face of outer face seal 392. This premise sometimes cannot be met due to layout restrictions in relation to the other components. Passages 396 can be replaced with passage 396′ illustrated in FIG. 21 so that the bottom of passages 396′ are still exposed to the inside and outside of recess 54 repeatedly and alternately. As illustrated in FIG. 22, the angular orientation of recesses 398 can be modified within forty-five degrees from the case of the preferred embodiment with the symmetric axis of each groove coinciding with the radial direction of the respective passage 396. This will allow shifting of the centroid of the respective recesses 398 in the circumferential direction and further minimizing the distance between the excessive force FTH and the counteracting force FGR. While FIG. 22 illustrated modification in a clockwise direction, it is within the scope of the present invention to modify recesses 398 in a counter-clockwise direction if desired.
Preferably four separate recesses 504a-d are provided on thrust surface 502 of non-orbiting scroll member 470. Recesses 504a-d are located circumferentially to surround scroll wrap 472. By using separate recesses 504a-d, the capability to carry the eccentric bias-load which scroll members normally generate will be enhanced. Each recess has its own throttling device 506 to provide each recess 504 with its own independent oil carrying capacity. This feature is also necessary for the eccentric load. The land of each recess 504 is adjusted in height to be flush with the tip surface of non-orbiting scroll wrap 472.
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