Lubricant pump with magnetic and centrifugal traps

Information

  • Patent Grant
  • 6484847
  • Patent Number
    6,484,847
  • Date Filed
    Thursday, November 30, 2000
    24 years ago
  • Date Issued
    Tuesday, November 26, 2002
    22 years ago
Abstract
A hermetic compressor assembly includes a compressor housing having a quantity of liquid lubricant therein. A compressor mechanism is provided within the compressor housing and a drive shaft is selectively rotatable and operably connected to the compressor mechanism. A liquid lubricant displacement element is engaged to the drive shaft and a support member is attached to the compressor housing. A pivotable magnetic member is provided between the liquid lubricant displacement element and the support member and includes a suction port provided therein. The liquid lubricant displacement element is in fluid communication with the quantity of liquid lubricant through the suction port in the magnetic member. At least a portion of any ferrous particles contained in the liquid lubricant are attracted to and retained by the magnetic member as the liquid lubricant is passed through the suction port of the magnetic member.
Description




BACKGROUND OF THE INVENTION




1. Field of the Invention




The present invention relates to hermetic compressors having positive displacement liquid lubricant pumps to supply liquid lubricant to bearing surfaces. More specifically, the present invention relates to compressors including liquid lubricant pumps having cavities disposed within the pump and drive shaft to trap debris by magnetic and centrifugal force.




2. Description of the Related Art




Compressor lubrication systems often include a positive displacement lubrication pump to supply liquid lubricant to bearing surfaces within the compressor. Liquid lubricant, or oil, often contains debris in the form of metallic particles circulating throughout the lubrication system. The particles detrimentally affect bearing surfaces by causing premature wear, and consequently, compressor performance is compromised. It is known to provide cartridge type or screen filters to capture debris, however an inherent disadvantage of cartridge and screen filters is that they clog and consequently block circulation of oil to bearing surfaces which significantly shortens the life of the compressor. Responsive to this clogged filter effect, compressor assemblies have been adapted with bypass valving, for example, which routes the oil around the filter when the filter becomes clogged to effectively maintain an adequate oil supply to the bearing surfaces. However, the circulating oil remains debris-laden which may cause an abrasive attack on the bearing surfaces resulting in bearing seizure and imminent failure of the compression mechanism.




Hermetic compressor assemblies are susceptible to oil-entrained debris, the most destructive being the fine powdered debris, which may not be captured by standard cartridge and filtering methods. The fine powders entrained in the oil are often composed of ferrous material which is attracted to a magnet. While previous compressor assemblies have utilized magnets to attract entrained metallic particles, these compressors have proven to do so inefficiently. Typically, magnets are randomly placed within the interior of the compressor housing, producing marginal particle accumulation performance. Therefore, the marginal benefits provided by these types of compressors, in view of the substantial costs associated with installing magnets to attract ferrous particles, have limited their practicality.




Further, with evolving and more demanding environmental standards, the hydrocarbon based oils and refrigerants traditionally used are yielding to environmental friendly substitutes. However, it is not fully understood whether these substitute lubricants are equally effective in providing comparable levels of lubrication and durability to the compressor mechanism. Thus, improving the ability to remove foreign particles from liquid lubricant, without a substantial compressor assembly cost increase, would be highly desirable.




Yet another problem associated with the use of impeller type pumps in compressor assemblies is one of drive shaft misalignment, relative to the pump housing, during the assembly process. Traditionally, misalignment of the drive shaft and pump housing was avoided by providing the pump housing, compressor mechanism assembly and impeller pump assembly with precise tolerances. A significant labor and handling cost is associated with parts having precise tolerances. What is desired is an impeller type pump assembly structure which requires significantly less labor to manufacture and assemble compared to previously employed structures.




An inexpensive oil pump assembly which includes the ability to trap debris suspended in the oil while continuously providing an ample supply of oil to bearing surfaces is highly desired. Further, an oil pump assembly which provides further cost reduction attributable to avoiding precise part tolerances in preventing drive shaft and pump housing misalignment is desired.




SUMMARY OF THE INVENTION




The present invention overcomes the disadvantages of prior compressor assemblies by providing a hermetic compressor assembly which includes a compressor housing including a quantity of liquid lubricant therein, a compressor mechanism provided within the compressor housing, a drive shaft selectively rotatable and operably connected to the compressor mechanism, a liquid lubricant displacement element engaged to the drive shaft and a support member attached to the compressor housing, a pivotable magnetic member provided between the liquid lubricant displacement element and the support member provided with a suction port therein. The liquid lubricant displacement element is in fluid communication with the quantity of liquid lubricant through the suction port in the magnetic member. At least a portion of any ferrous particles contained in the liquid lubricant are attracted to and retained by the magnetic member as the liquid lubricant is passed through the suction port of the magnetic member.




The present invention further provides a hermetic compressor assembly including a compressor mechanism and a quantity of liquid lubricant provided in a compressor housing, a selectively operable drive shaft driveably connected to the compressor mechanism, a liquid lubricant displacement element supported by a support member and engaged to the drive shaft. The compression mechanism and the liquid lubricant displacement element are in fluid communication through a passage provided in the drive shaft. A centrifugal particle trap cavity is defined by a wall of the passage within the drive shaft and a portion of the liquid lubricant displacement element. A magnetic member is pivotably supported by the support member and a thrust member is superposed with the magnetic member. A magnetic particle trap cavity is provided within a lateral face of the thrust member and is partially enclosed by a lateral surface of the magnetic member. The liquid lubricant is urged from the sump to the compression mechanism through the passage in the drive shaft and any debris in the liquid lubricant is successively retained by the magnetic particle trap cavity and the centrifugal particle trap cavity prior to the lubricants introduction to the compression mechanism.











BRIEF DESCRIPTION OF THE DRAWINGS




The above-mentioned and other features and advantages of this invention, and the manner of attaining them, will become more apparent and the invention itself will be better understood by reference to the following description of embodiments of the invention taken in conjunction with the accompanying drawings, wherein:





FIG. 1

is a sectional view of a hermetic compressor assembly provided with an oil pump assembly in accordance with the present invention;





FIG. 2A

is an exploded view of a first embodiment of an oil pump assembly in accordance with the present invention, viewing the pump from the bottom;





FIG. 2B

is an exploded view of the thrust plate and magnetic disk assembly of a second embodiment of an oil pump assembly in accordance with the present invention, viewing the assembly from the bottom;





FIG. 3A

is an exploded view of the oil pump assembly of

FIG. 2A

, viewing the pump from the top;





FIG. 3B

is an exploded view of the thrust plate and magnetic disk assembly of

FIG. 2B

, viewing the assembly from the top;





FIG. 4

is a sectional view of the oil pump assembly taken along line


4





4


of

FIG. 11

, however shown in an operational mode, illustrating a flow of oil therethrough and particles being trapped in respective magnetic and centrifugal traps;





FIG. 5

is a sectional view of the oil pump assembly taken along lines


5





5


of

FIG. 11

, however shown in a non-operational mode;





FIG. 6

is a plan view of the bottom of the impeller of the oil pump of

FIG. 2A

, showing the plurality of impeller blades;





FIG. 7

is a plan view of the bottom of the thrust plate of the oil pump of

FIG. 2A

, showing the pair of arcuate slots and the magnetic particle trap cavity;





FIG. 8

is a plan view of the bottom of the magnetic disk of the oil pump of

FIG. 2A

;





FIG. 9

is a plan view of the top of the pump housing of the oil pump of

FIG. 3A

;





FIG. 10A

is a fragmentary sectional view of the oil pump assembly according to the present invention enclosed within the circular portion shown as line


10


A—


10


A of

FIG. 11

, showing the engagement between the frustoconical surfaces of the pump housing and magnetic disk;





FIG. 10B

is a fragmentary sectional view of a third embodiment of the oil pump assembly according to the present invention showing the engagement between the spherical surfaces of the pump housing and magnetic disk; and





FIG. 11

is a bottom view of the oil pump assembly of FIG.


2


A.











Corresponding reference characters indicate corresponding parts throughout the several views. Although the drawings represent embodiments of the present invention, the drawings are not necessarily to scale and certain features may be exaggerated in order to better illustrate and explain the present invention. The exemplifications set out herein illustrate embodiments of the invention, and such exemplifications are not to be construed as limiting the scope of the invention in any manner.




DETAILED DESCRIPTION OF THE INVENTION




Referring to

FIG. 1

, compressor assembly


10


includes hermetically sealed housing


12


, having base


17


provided at a lower end thereof. Motor assembly


14


, enclosed within housing


12


, includes rotor


11


and stator


13


and is directly connected to, and operatively drives, compression mechanism


15


. Compression mechanism


15


may constitute a reciprocating piston-type compression mechanism, as shown, which includes cylinder block


16


having reciprocating piston


18


therein. Alternatively, compression mechanism


15


may be a rotary or scroll type mechanism. Drive shaft or crankshaft


20


is driveably coupled to motor assembly


14


and extends vertically from a lowermost portion of compressor assembly


10


upwardly towards compression mechanism


15


. Upper end of crankshaft


20


is rotatably supported by main bearing


22


and is generally hollow, including inner passage


23


extending axially, and continuously, along the length of crankshaft


20


. Arrows


25


illustrate flow of liquid lubricant (e.g., oil), which is directed through passage


23


of crankshaft


20


, to supply oil to bearing surfaces, such as rod bearing


24


, and to wrist pin


27


, as shown. Oil pump assembly


42


is positioned at lower end


36


of crankshaft


20


to urge oil from oil sump


30


to upper end


38


of crankshaft


20


. Support member


43


, provided within lower portion


28


of housing


12


to support pump


42


, includes a plurality of arms


33


equidistantly spaced and radially extended between pump


42


and inner surface


35


of housing


12


. Oil sump


30


, formed by lower portion


28


of housing


12


, contains surplus oil to supply pump assembly


42


with oil. Oil level


32


within sump


30


is preferably maintained above oil pump assembly


42


, as shown, such that a continuous supply of oil is pumped to bearing surfaces by pump assembly


42


.




Referring to

FIGS. 2A and 3A

, shown is oil pump assembly


42


, engaged with lower end


36


of crankshaft


20


. Lower end


36


of crankshaft


20


includes end face


50


and outer surface


46


. Lower end


36


of crankshaft is attached to oil displacement element or impeller


52


. Alternatively, oil displacement element


52


may include a gerotor or gear type element to transfer oil from sump


30


to compression mechanism


15


(FIG.


1


). It may be seen that counterbore


40


(

FIG. 2A

) is formed in lower end


36


of crankshaft


20


to receive stem


56


of impeller


52


. End face


50


of crankshaft


20


includes angled counterbore or chamfer


44


provided in counterbore


40


of crankshaft


20


(FIG.


2


A). A pair of diametrically opposed slots


48


(

FIG. 2A

) radially extend from counterbore


40


of crankshaft


20


toward outer surface


46


of crankshaft


20


to engageably receive tangs


60


of impeller


52


. Tangs


60


axially extend from disk shaped drive portion


54


and are attached to a periphery of impeller stem


56


(FIG.


3


A).




Impeller stem


56


axially extends from drive portion


54


and includes circumferentially disposed groove


58


(FIGS.


4


and


5


), having a U-shaped cross section and O-ring


62


is received therein. O-ring


62


provides a liquid seal between the outer periphery of impeller stem


56


and counterbore


40


of drive shaft


20


(FIGS.


4


and


5


). Drive portion


54


of impeller


52


includes a plurality of radially arranged impeller blades


66


. Each impeller blade


66


is separated from an adjacent impeller blade


66


by circumferential spaced groove


65


(FIG.


6


). As best seen in

FIGS. 2A and 6

, impeller


52


includes annular groove


68


located substantially centered on lower surface of drive portion


54


of impeller


52


. Impeller


52


includes center portion


69


provided with generally planar surface


71


which is coextensive with surface


73


of each respective impeller blade


66


(FIG.


6


). Hole


64


extends axially through impeller


52


. Surfaces


71


and


73


form thrust face


70


(

FIGS. 4-5

) of impeller


52


.




Referring again to

FIGS. 2A and 3A

, shown is thrust member or thrust plate


72


having thrust face


74


which rotatably supports thrust face


70


of impeller


52


(FIGS.


4


-


5


). It may be seen that a clearance “c” exists between main bearing


22


and shoulder portion


75


of crankshaft


20


such that the weight of crankshaft


20


and displacement element


52


urges displacement element


52


into engagement with face


74


of thrust plate


72


(FIG.


1


). Those having ordinary skill will understand that the combined weight of crankshaft


20


, and displacement element


52


, bearing down on face


74


of thrust plate


72


prevents a significant and detrimental loss of lubricant through an interface provided by displacement element


52


and face


74


of thrust plate


72


.




Thrust plate


72


includes outer radial surface


76


and lateral surface


77


(FIG.


7


). Lateral surface


77


is provided with lower faces


78




a


,


78




b


and


78




c


which collectively form a planar support surface which abuts upper face


86


of magnetic member or disk


84


(FIGS.


2


A and


7


). Thrust plate


72


is provided with central hole


80


which is aligned with central hole


64


of impeller


52


(FIGS.


4


and


5


). As best seen in

FIGS. 2A and 4

, thrust plate


72


includes extended annular nose portion


81


, split into two arcuate halves, each of which axially extend from lower face


78




b


. The two halves of nose portion


81


are engaged with recess


94


in magnetic disk


84


to center thrust plate


72


relative to magnetic disk


84


(FIG.


3


A).




Magnetic disk


84


includes upper face


86


, lower face


88


and peripheral surface


90


, and as best seen in

FIGS. 3A and 8

, is provided with semi-circular notch


92


which receives semi-circular protrusion


82


(

FIG. 7

) axially extended from thrust plate


72


. Protrusion


82


, extended into notch


92


, prevents rotation between magnetic disk


84


relative to thrust plate


72


. Lower face


88


of magnetic disk


84


includes three projections


96


intersected at centerline axis


85


and radially extended towards peripheral surface


90


of magnetic disk


84


(FIGS.


2


A and


11


). Referring to

FIG. 11

, radial projections


96


are engaged with three circumferentially spaced slots


116


(

FIG. 9

) located in pump housing


104


to prevent rotation between magnetic disk


84


and pump housing


104


. Housing


104


is fixed to support member


43


by, for example, a press fit engagement between outer surface


106


of housing


104


and counterbore


105


located in support member


43


(FIG.


1


). Alternatively housing


104


may be eliminated and in its place support member


43


may be provided with identically internal characteristics as that of housing


104


.




Magnetic disk


84


may be manufactured from a magnetized metallic material through, for example, a sinterized powder metal process. The magnetic properties of magnetic disk


84


attract ferrous particles


87


(

FIG. 4

) entrained or suspended in the oil as described below. Impeller


52


and thrust plate


72


may be made of an abrasion resistant moldable plastic, such as a phenolic material for example, through an injection molding process. Crankshaft


20


may be preferably made from a carbon steel and formed through a forging process to produce high durability and abrasion resistant properties.




An alternate thrust plate and magnetic disk engagement is shown in

FIGS. 2B and 3B

. As best seen in

FIG. 2B

, magnetic disk


84


′ includes a pair of through holes


98


aligned with a pair of holes


99


in thrust plate


72


′. Holes


99


are engaged by a pair of fasteners


100


, which may include, for example, brads, to secure magnetic disk


84


′ to thrust plate


72


′.




Referring to

FIGS. 2-5

, pump housing


104


is provided with cylindrical outer surface


106


and cylindrical inner surface


108


(FIGS.


3


-


5


). Housing


104


and support member


43


may be made from an aluminum alloy through a die cast molding process or a powder metal process, for example. As best seen in

FIG. 10A

, lower end


109


of housing


104


includes annular platform


110


which provides support for magnetic disk


84


. Platform


110


includes inwardly angled frustoconical surface


112


providing support for outwardly angled frustoconical surface


102


(

FIG. 8

) provided on lower face


88


of magnetic disk


84


(

FIGS. 4

,


5


and


10


). Lower end


109


of housing


104


includes through hole


114


extended axially through housing


104


to provide an inlet for oil to be drawn into pump


42


by the oil displacement element, i.e. impeller


52


. Frustoconical surface


112


, provided on annular platform


110


, forms a frustoconical engagement with frustoconical surface


102


of magnetic disk


84


. The frustoconical engagement provides a degree of self alignment of the abutting faces of impeller


52


and thrust plate


72


, despite angular variations in the housing centerline relative to the shaft centerline. As a result, reliance on close manufacturing and assembling tolerances of impeller


52


, crankshaft


20


and thrust plate


72


, traditionally employed, are not required with oil pump


42


.




Referring to

FIG. 10B

, a third embodiment of a lubricant pump is shown and includes mating hemispherically shaped surfaces


102


′,


112


′ of magnetic member and housing


104


′,


84


′ respectively. As an alternative to frustoconical surfaces


102


,


112


shown, in

FIG. 10A

, hemispherical surfaces


102


′,


112


′ shown in

FIG. 10B

provide increased pivoting mobility between magnetic member


84


′ relative to housing


104


′ to remedy the angular variations in the housing centerline relative to the shaft centerline.




The flow of oil through oil pump assembly


42


will now be described. Referring to

FIG. 4

, oil is drawn through suction port or hole


114


of housing


104


from sump


30


and into a pair of arcuate suction ports


120


formed in magnetic disk


84


(

FIGS. 4

,


8


and


11


). Arcuate suction ports


120


extend completely through the magnetic disk from lower face


88


to upper face


86


(FIG.


8


). Similarly, arcuate suction port


122


extends completely through thrust plate


72


between thrust face


74


and lower face


78




a


thereof (FIG.


7


). Arcuate suction port


122


, provided in thrust plate


72


, is radially aligned with the, pair of arcuate suction ports


120


in magnetic disk


84


. It may be seen that thrust plate


72


includes a pair of U-shaped discharge slots


126


provided in outer periphery


76


of thrust plate


72


(FIG.


3


A). Slots


126


are oppositely located relative to one another and axially extend into a pair of arcuate channels


130


formed in thrust plate


72


(

FIGS. 2A

,


7


). Channels


130


are provided in lateral surface


77


of thrust plate


72


as described below.




As best seen in

FIG. 7

, each channel


130


includes transverse wall


132


, first sidewall


136


, and second sidewall


138


. Transverse wall


132


is substantially planar and is formed within lateral surface


77


of thrust plate


72


. First sidewall


136


is arcuate and extends from its respective discharge slot


126


to hole


80


in thrust plate


72


. Each second side wall


138


of channel


130


includes U-shaped slot


140


. A portion of oil received by slots


126


from impeller


52


flows into channels


130


and into central hole


80


in thrust plate


72


. The other portion of oil flows into magnetic particle trap cavity


142


as described below.




Lateral surface


77


of thrust plate


72


is provided with crescent-shaped magnetic particle trap cavity


142


. First sidewall


144


of magnetic particle trap cavity


142


includes a plurality of circumferentially spaced semi-circular inclusions


146


(FIG.


7


). Second sidewall


148


of magnetic particle trap cavity


142


is generally smooth and continuous. Magnetic particle trap cavity


142


includes transverse wall


150


provided in lateral surface


77


of thrust plate


72


. Magnetic particle trap cavity


142


is enclosed by upper face


86


of magnetic disk


84


(FIGS.


4


and


5


).




In operation, pump


42


is activated by motor driven shaft


20


urging rotation of impeller


52


and oil in sump


30


(

FIG. 1

) is drawn, illustrated by arrows


149


in

FIG. 4

, into suction port


120


of magnetic disk


84


. Thereafter, oil enters suction port


122


provided in thrust plate


72


. It is well understood that over time a compressor assembly generates debris which becomes entrained in the oil and frequently a portion of the debris is in the form of ferrous particles. Ferrous particles, which may be included in the present invention lubricant pump


42


, are attracted to and retained by magnetic disk


84


before the oil enters suction port


122


of thrust plate


72


. Oil then enters annular groove


68


within impeller


52


and is centrifugally flung radially outward through radially positioned grooves


65


between impeller blades


66


. The oil is then urged downwardly into U-shaped discharge slots


126


in thrust plate


72


, and thereafter, a portion of the oil is urged into the pair of arcuate channels


130


which extend toward central hole


80


of the thrust plate


72


. Oil entering central hole


80


of thrust plate


72


via channels


130


is urged upwardly through hole


64


in impeller


52


, into passage


23


of crankshaft


20


, and is ultimately received by the bearing surfaces within the compressor mechanism.




The portion of oil which does not travel through arcuate slots


130


enters magnetic particle trap cavity


142


and is slow moving due to the debris entrained therein. The oil entering magnetic particle trap cavity


142


is flung radially outward into the plurality of inclusions


146


in first sidewall


144


. Oil circulates through magnetic particle trap cavity


142


, entering one of the U-shaped slots


140


and exiting the other U-shaped slot


140


. Since thrust plate


72


is symmetrical, pump


42


may operate in either rotational direction with similar particle trapping results, i.e., pump


42


is reversible.




Referring to

FIGS. 4 and 5

, it may be seen that upper face


86


of magnetic disk


84


overlays arcuate channels


130


and magnetic particle trap cavity


142


of thrust plate


72


. Ferrous particles


87


entering magnetic particle trap cavity


142


are carried with the oil and are attracted to and trapped by upper face


86


of magnetic disk


84


under the influence of magnetic force established by magnetic disk


84


(FIG.


4


). Additionally, oil flowing through channels


130


includes ferrous particles which pass over magnetic disk


84


and become attracted and attached to face


86


of magnetic disk. Additional particles and debris, which may include ferrous or non-ferrous particles, are caught within inclusions


146


of magnetic particle trap cavity


142


as oil flows through cavity


142


. Therefore, magnetic particle trap cavity


142


and face


86


of magnetic disk


84


provide a two-stage debris retaining structure, the first stage provided by inclusions


146


within thrust plate


72


, trapping a portion of the debris therein, and a second stage, provided by face


86


of magnetic disk


84


, trapping additional debris, in the form of ferrous particles


87


.




As best seen in

FIG. 4

, drive shaft


20


is provided with centrifugal particle trap cavity


155


radially located within a wall defining passage


23


. Specifically, centrifugal particle trap cavity


155


is bound by counterbore


40


and frustoconical surface


156


of impeller stem


56


, on one axial end, and frustoconical surface


160


of the other axial end. Thus, it may be seen that annular, frustoconical surfaces


156


,


160


, and a portion of counterbore


40


in crankshaft


20


, form centrifugal particle trap cavity


155


to capture debris


162


, as it is transported by the oil flowing through passage


23


, shown by flow arrow


149


(FIG.


4


). Particles


162


, under the influence of centrifugal force as crankshaft


20


is rotated by motor assembly


14


, are flung into centrifugal particle trap cavity


155


as oil moves through passage


23


. Particles


162


are thereby centrifugally trapped in centrifugal particle trap cavity


155


during compressor operation, and are prevented from thereafter continuing with the oil upwards through passage


23


.




Referring to

FIG. 5

, it may be seen that once shaft


20


ceases rotation, at least a portion of particles


162


travel downwardly and rest upon conical surface


156


formed by impeller stem


56


. The remaining particles continue downwardly from second chamber


155


and accumulate at center portion


164


of magnetic disk


84


and some particles may eventually flush back through oil pump


42


and into oil sump


30


or magnetic particle trap cavity


142


. Those having ordinary skill in the art will understand that an abundance of debris entrained in the oil will not plug inventive pump


42


. Rather, magnetic and centrifugal particle trap cavities


142


,


155


are so positioned within the oil circuit such that oil is allowed to pass through pump


42


regardless of whether the magnetic and centrifugal particle trap cavities are replete with debris. Since hermetically sealed compressor assembly


10


of the present invention is manufactured to be non-maintainable, i.e., not to be disassembled for maintenance purposes, it is particularly important that oil pump


42


continues to perform even if a significant amount of debris is accumulated within magnetic and centrifugal particle trap cavities


142


,


155


.




Referring to

FIGS. 2-5

, gas vent


166


extends from chamfer


44


of crankshaft


20


to outer surface


46


of crankshaft


20


to provide an escape path for refrigerant gases flashed from the oil in pump


42


. Gases or vapor which are not vented may be detrimental to proper lubricant flow, inasmuch as it may cause an insufficient amount of oil being delivered to the bearing surfaces. Vent


166


provides an escape for these gases to avoid bearing damage.




While this invention has been described as having exemplary designs, the present invention may be further modified within the spirit and scope of this disclosure. Therefore, this application is intended to cover any variations, uses, or adaptations of the invention using its general principles. For example, aspects of the present invention may be applied to compressors other than reciprocating piston compressors such as rotary and scroll compressor assemblies, for example. Further, this application is intended to cover such departures from the present disclosure as come within known or customary practice in the art to which this invention pertains.



Claims
  • 1. A hermetic compressor assembly comprising:a compressor housing including a quantity of liquid lubricant therein; a compressor mechanism disposed in said compressor housing; a drive shaft selectively rotatable and operably connected to said compressor mechanism; and a liquid lubricant displacement element engaged to said drive shaft; a support member attached to said compressor housing; a pivoting magnetic member disposed between said liquid lubricant displacement element and said support member; a suction port defined within said magnetic member, said liquid lubricant displacement element is in fluid communication with said quantity of liquid lubricant through said suction port in said magnetic member, wherein at least a portion of any ferrous particles contained in said liquid lubricant are attracted to and retained by said magnetic member as said liquid lubricant is passed through said suction port of said magnetic member.
  • 2. The compressor assembly according to claim 1, further comprising a thrust member, said liquid lubricant displacement element being supported by said thrust member.
  • 3. A hermetic compressor assembly comprising:a compressor housing including a quantity of liquid lubricant therein; a compressor mechanism disposed in said compressor housing; a drive shaft selectively rotatable and operably connected to said compressor mechanism; and a liquid lubricant displacement element engaged to said drive shaft; a support member attached to said compressor housing; a pivotable magnetic member disposed between said liquid lubricant displacement element and said support member; a suction port defined within said magnetic member, said liquid lubricant displacement element is in fluid communication with said quantity of liquid lubricant through said suction port in said magnetic member; and a thrust member, said liquid lubricant displacement element being supported by said thrust member; wherein at least a portion of any ferrous particles contained in said liquid lubricant are attracted to and retained by said magnetic member as said liquid lubricant is passed through said suction port of said magnetic member and said thrust member defines a magnetic particle trap cavity, said magnetic particle trap cavity being superposed by said magnetic member, whereby an additional portion of said any ferrous particles contained in said liquid lubricant is retained within said magnetic particle trap cavity under the influence of magnetic force.
  • 4. The compressor assembly according to claim 3, wherein said magnetic particle trap cavity includes a plurality of circumferentially disposed inclusions, whereby any debris contained by said liquid lubricant is captured within said inclusions as said liquid lubricant is passed through said magnetic particle trap cavity.
  • 5. The compressor assembly according to claim 1, wherein said drive shaft includes a passage, said passage partially defining a centrifugal particle trap cavity, wherein at least a portion of any debris contained in said liquid lubricant is retained within said centrifugal particle trap cavity under the influence of centrifugal force provided by rotation of said drive shaft.
  • 6. The compressor assembly according to claim 5, wherein said liquid lubricant displacement element is in fluid communication with an exterior portion of said drive shaft through a gas vent disposed in said drive shaft and any gas intermixed with said liquid lubricant is transported to an interior of said compressor housing through said gas vent.
  • 7. The compressor assembly according to claim 5, wherein said centrifugal particle trap cavity is located downstream of said magnetic particle trap cavity.
  • 8. The compressor assembly according to claim 3, wherein said thrust member includes a lateral face having a pair of radially extended channels disposed therein, said magnetic particle trap cavity being disposed in said lateral face of said thrust member, wherein said liquid lubricant being urged toward said lateral face of said thrust member is diverted between said channels and said magnetic particle trap cavity.
  • 9. The compressor assembly according to claim 2, wherein said thrust member is supported by a lateral surface of said magnetic member, said magnetic member comprising a magnetized substance to attract and retain any ferrous particles contained in said liquid lubricant.
  • 10. The compressor assembly according to claim 1, wherein said liquid lubricant displacement element is an impeller.
  • 11. A hermetic compressor assembly comprising:compressor housing including a quantity of liquid lubricant therein; a compressor mechanism disposed in said compressor housing; a selectively operable drive shaft driveably connected to said compressor mechanism; a support member; a liquid lubricant displacement element supported by said support member, said liquid lubricant displacement element engaged to said drive shaft, said compressor mechanism and said liquid lubricant displacement element being in fluid communication through a passage disposed in said drive shaft; a centrifugal particle trap cavity defined by a wall of said passage within said drive shaft and a portion of said liquid lubricant displacement element; a magnetic member pivotably supported by said support member; a thrust member superposed with said magnetic member; and a magnetic particle trap cavity disposed within a lateral face of said thrust member and being partially enclosed by a lateral surface of said magnetic member, wherein said liquid lubricant is urged from said sump to said compression mechanism through said passage in said drive shaft and any debris in said liquid lubricant being successively retained by said magnetic particle trap cavity and said centrifugal particle trap cavity.
  • 12. The compressor assembly according to claim 11, wherein said magnetic particle trap cavity is partially defined by a plurality of radially disposed inclusions, wherein any debris contained in said liquid lubricant is retained by said centrifugal particle trap cavity under the influence of centrifugal force and any debris comprising ferrous particles is retained by said magnetic particle trap cavity under the influence of magnetic force.
  • 13. The compressor assembly according to claim 11, wherein said magnetic particle trap cavity is positioned upstream relative to said centrifugal particle trap cavity.
  • 14. The compressor assembly according to claim 11, wherein said magnetic member is pivotally supported within said housing;
  • 15. The compressor assembly according to claim 11, wherein said magnetic member includes a surface moveably engaged with a surface defined by said pump housing.
  • 16. The compressor assembly according to claim 15, wherein said surface of said magnetic member and said surface of said support member are superposed spherical surfaces.
  • 17. The compressor assembly according to claim 15, wherein said surface of said magnetic member and said surface of said support member are superposed frustoconical surfaces.
  • 18. The compressor assembly according to claim 11, wherein said liquid lubricant displacement element is in fluid communication with an interior of said compressor housing through a gas vent disposed in said drive shaft.
  • 19. The compressor assembly according to claim 11, further comprising a pump housing disposed between said support member and said magnetic member.
  • 20. The compressor assembly according to claim 11, wherein said liquid lubricant displacement element constitutes an impeller.
  • 21. The compressor assembly according to claim 20, wherein said compressor housing defines a liquid lubricant sump containing said liquid lubricant, said impeller includes an annular groove disposed therein, said annular groove being in fluid communication with said sump through a suction port extended axially through said thrust member and said magnetic member.
  • 22. The compressor assembly according to claim 21, wherein said suction port extended through said thrust member and said magnetic member is offset relative to a centerline extended axially through said drive shaft.
  • 23. The compressor assembly according to claim 22, wherein said compressor mechanism includes bearing surfaces in fluid communication with said liquid lubricant displacement element though said passage within said drive shaft, said liquid lubricant displacement element and said thrust member include a centrally located discharge port axially extended therethrough, said suction port within said magnetic member and said thrust member in fluid communication with said discharge port within said liquid lubricant displacement element and said thrust member through a pair of slots disposed in said thrust member.
  • 24. The compressor assembly according to claim 11, wherein said magnetic member comprises a disk having a pair of lateral surfaces, one of said pair of lateral surfaces includes a plurality of radially extending projections attached thereto, said projections being received within a plurality of circumferentially spaced and radially extended slots provided in said support member, whereby said magnetic member is substantially rotationally restrained relative to said pump housing.
US Referenced Citations (17)
Number Name Date Kind
2883101 Kosfeld Apr 1959 A
3285504 Smith Nov 1966 A
3478887 Ohrberg Nov 1969 A
4131396 Privon et al. Dec 1978 A
4421453 Hoff et al. Dec 1983 A
4432693 Hackbart Feb 1984 A
4747471 Ballentine et al. May 1988 A
4850819 Bush et al. Jul 1989 A
5176506 Siebel Jan 1993 A
5282963 Hull et al. Feb 1994 A
5413462 Alberni May 1995 A
5580233 Wakana et al. Dec 1996 A
5707220 Krueger et al. Jan 1998 A
5865607 Fukuoka Feb 1999 A
6039550 Friedley et al. Mar 2000 A
6102160 Cornelius Aug 2000 A
6116877 Takeuchi et al. Sep 2000 A