Rolling piston rotary compressors

Abstract

An apparatus includes a compressor housing and a rolling piston rotary compressor assembly contained in the compressor housing. The rolling piston rotary compressor assembly includes a main bearing fixedly coupled to the compressor housing. An electric motor assembly is contained in the compressor housing. The electric motor assembly includes an electric motor stator fixedly coupled to the compressor housing. A crankshaft extends from the compressor assembly, through the main bearing, and into the electric motor assembly.

Description

125992.000548:GWR / pb2_25110305.V3ROLLING PISTON ROTARY COMPRESSORSCROSS REFERENCE TO RELATED APPLICATION(S)

[0001] This application claims the benefit of priority to United States Provisional Patent Application No. 63 / 697,250, filed on September 20, 2024, which is incorporated herein by reference.FIELD OF THE INVENTION

[0002] Various embodiments herein relate to positive-displacement compressors and, more particularly, to electrically powered rolling piston rotary compressors for compressing refrigerants in air conditioning, refrigeration, heat pump, and / or other cooling and / or heating systems for electric vehicles, internal combustion engine vehicles, aircraft, marine vehicles, buildings, manufacturing systems, and / or other suitable applications.BACKGROUND

[0003] Historically, undesirably high concentrations of oil in refrigerant gasses circulated though refrigerant systems have contributed to undesirable refrigerant system inefficiencies and maintenance issues. Meanwhile, undesirably inefficient circulations of oil and undesirably high electric motor operating temperatures within electrically powered refrigerant compressors have contributed to undesirable compressor inefficiencies and reduced compressor durabilities.125110305. v3125992.000548:GWR / pb2_25110305.V3SUMMARY OF THE INVENTION

[0004] In some embodiments, an apparatus includes a compressor housing and a rolling piston rotary compressor assembly contained in the compressor housing. The rolling piston rotary compressor assembly includes a main bearing fixedly coupled to the compressor housing. An electric motor assembly is contained in the compressor housing. The electric motor assembly includes an electric motor stator fixedly coupled to the compressor housing. A crankshaft extends from the compressor assembly, through the main bearing, and into the electric motor assembly. An annular skirt extends from the main bearing to the electric motor stator.

[0005] In some embodiments, an apparatus includes a compressor housing and a generally U-shaped flow diverter arranged and configured to divert a refrigerant flow within the compressor housing. The generally U-shaped flow diverter includes a mid portion, a first side portion extending from the mid portion at about a 90 degree angle relative to the mid portion, and a second side portion extending from the mid portion at about a 90 degree angle relative to the mid portion. The compressor housing includes a discharge tube having an end extending into the housing. The end extending into the housing is positioned between the first and second side portions of the generally U- shaped flow diverter.

[0006] In some embodiments, an apparatus for compressing a refrigerant and urging the refrigerant along a flow path includes a compressor housing. The compressor housing includes a discharge tube having an end extending into the compressor housing. The apparatus also includes a rolling piston rotary compressor assembly contained in the housing. The rolling piston rotary compressor assembly includes a compressor discharge225110305. v3125992.000548:GWR / pb2_25110305.V3 port, a peripheral portion, and an annular oil screen. The annular oil screen is arranged and configured to filter at least some of the oil from the refrigerant. The annular oil screen extends around the peripheral portion of the rolling piston rotary compressor assembly and between the rolling piston rotary compressor assembly and the compressor housing. And the annular screen is axially positioned between the compressor discharge port and the discharge tube.

[0007] In some embodiments, an apparatus includes a compressor housing and a rolling piston rotary compressor assembly contained in the compressor housing. The rolling piston rotary compressor assembly includes a main bearing fixedly coupled to the compressor housing. An electric motor assembly is contained in the compressor housing. The electric motor assembly includes an electric motor stator fixedly coupled to the compressor housing. A crankshaft extends from the compressor assembly, through the main bearing, and into the electric motor assembly. The crankshaft includes a first shaft portion extending through the main bearing. The first shaft portion has an outer surface. The outer surface of the first shaft portion defines a helicoidal oil flow channel.

[0008] In some embodiments, an apparatus includes a compressor housing including a generally bell-shaped section, a separate plate-like section, and a separate generally cylindroid section extending between the generally bell-shaped section and the plate-like section. The apparatus also includes a rolling piston rotary compressor assembly positioned in the generally bell-shaped section of the compressor housing, and an electric motor assembly rotationally coupled to the rolling piston rotary compressor assembly and positioned in the generally cylindroid section of the compressor housing.325110305. v3125992.000548:GWR / pb2_25110305.V3

[0009] In some embodiments, an apparatus includes a rolling piston rotary compressor assembly, and a compressor housing surrounding the rolling piston rotary compressor assembly. The compressor housing includes a cyclonic plenary refrigerant discharge port assembly.

[0010] In some embodiments, a method includes, within a compressor housing, flowing a refrigerant between a longitudinal tube sidewall portion and a longitudinal socket sidewall portion extending around the longitudinal tube sidewall portion, and receiving oil from the flowing refrigerant onto the longitudinal socket sidewall portion. Flowing the refrigerant includes swirling the refrigerant around the longitudinal tube sidewall portion.

[0011] In some embodiments, an apparatus an apparatus for compressing a refrigerant and urging the refrigerant along a flow path includes a rolling piston rotary compressor. The rolling piston rotary compressor includes an oil pump assembly. The apparatus also includes a compressor housing housing the rolling piston rotary compressor. The compressor housing includes a refrigerant discharge port. The compressor housing includes a refrigerant discharge flow deflector positioned between the refrigerant discharge port and the oil pump assembly.BRIEF DESCRIPTION OF THE DRAWINGS

[0012] Some of the figures shown herein may include dimensions. Further, the figures shown herein may have been created from scaled drawings, scaled models, or from photographs that are scalable. It is understood that such dimensions, or the relative scaling within a figure, are by way of example, and not to be construed as limiting unless so stated in a claim. Persons of ordinary skill will also recognize that computer-aided425110305. v3125992.000548:GWR / pb2_25110305.V3 design (“CAD”) renderings may include lines that pertain to changes in surface geometry, and not necessarily to component features.

[0013] FIG. 1 illustrates a top front right perspective view of an electrically powered, single-cylinder rolling-piston rotary compressor apparatus in accordance with aspects of the present disclosure.

[0014] FIG. 2 illustrates a top front right perspective partially exploded view of an electrically powered, single-cylinder rolling-piston rotary compressor apparatus in accordance with aspects of the present disclosure.

[0015] FIG. 3 illustrates a top front right perspective view of a single-cylinder rollingpiston rotary compressor in accordance with aspects of the present disclosure.

[0016] FIG. 4 illustrates a top front right perspective view of an electric motor in accordance with aspects of the present disclosure.

[0017] FIG. 5 illustrates a top back left perspective view of an electric motor in accordance with aspects of the present disclosure.

[0018] FIG. 6 illustrates a top back left perspective view of a single-cylinder rollingpiston rotary compressor in accordance with aspects of the present disclosure.

[0019] FIG. 7 illustrates a top front right perspective exploded view of a single-cylinder rolling-piston rotary compressor in accordance with aspects of the present disclosure.

[0020] FIG. 8 illustrates a top back right perspective exploded view of a single-cylinder rolling-piston rotary compressor in accordance with aspects of the present disclosure.

[0021] FIG. 9 illustrates a first plan view of a single-cylinder rolling-piston rotary compressor crankshaft in accordance with aspects of the present disclosure.525110305. v3125992.000548:GWR / pb2_25110305.V3

[0022] FIG. 10 illustrates a second plan view of a single-cylinder rolling-piston rotary compressor crankshaft in accordance with aspects of the present disclosure.

[0023] FIG. 11 illustrates a top plan section schematic depiction of a hollow singlecylinder rolling-piston rotary compressor crankshaft in accordance with aspects of the present disclosure.

[0024] FIG. 12 illustrates a perspective view of a single-cylinder rolling-piston rotary compressor crankshaft and a compressor main rotation bearing in accordance with aspects of the present disclosure.

[0025] FIG. 13 illustrates a perspective view of a single-cylinder rolling-piston rotary compressor crankshaft and an electric motor rotor in accordance with aspects of the present disclosure.

[0026] FIG. 14 illustrates a top back left perspective view of an electric motor in accordance with aspects of the present disclosure.

[0027] FIG. 15 illustrates a top back left perspective view of a single-cylinder rollingpiston rotary compressor in accordance with aspects of the present disclosure.

[0028] FIG. 16 illustrates a top front right perspective view of a compressor main rotation bearing in accordance with aspects of the present disclosure.

[0029] FIG. 17 illustrates a plan sectional view of a single-cylinder rolling-piston rotary compressor in accordance with aspects of the present disclosure.

[0030] FIG. 18 illustrates a top back right perspective view of an electrically powered, dual-cylinder rolling-piston rotary compressor apparatus in accordance with aspects of the present disclosure.625110305. v3125992.000548:GWR / pb2_25110305.V3

[0031] FIG. 19 illustrates a top back left perspective exploded view of parts of a compressor housing in accordance with aspects of the present disclosure.

[0032] FIG. 20 illustrates a plan sectional view of an electrically powered, dual-cylinder rolling-piston rotary compressor apparatus in accordance with aspects of the present disclosure.

[0033] FIG. 21 illustrates an exploded rear plan view of a compressor holding section of a compressor housing in accordance with aspects of the present disclosure.

[0034] FIG. 22 illustrates a plan sectional view of an electrically powered, dual-cylinder rolling-piston rotary compressor apparatus in accordance with aspects of the present disclosure.

[0035] FIG. 23 illustrates a plan sectional view of a cyclonic plenary refrigerant discharge port assembly in accordance with aspects of the present disclosure.

[0036] FIG. 24 illustrates a top plan section schematic depiction of some preferable flow of a compressed refrigerant within a cyclonic plenary refrigerant discharge port assembly in accordance with aspects of the present disclosure.DETAILED DESCRIPTION OF ONE OR MORE EMBODIMENTS

[0037] For the purposes of promoting an understanding of the principles of the invention, references may be made to one or more embodiments illustrated in the drawings and specific language may be used to describe the same. It should nevertheless be understood that no limitation of the scope of the invention is thereby intended, such alterations and further modifications in the illustrated device, and such further applications of the principles of the invention as illustrated therein being725110305. v3125992.000548:GWR / pb2_25110305.V3 contemplated as would normally occur to one skilled in the art to which the invention relates. Further, it should be appreciated that reasonable and logical inference of still other embodiments as would be understood by persons of ordinary skill in the art are contemplated. Unless expressly claimed herein as particularly limited to one or more specific materials, any component of the invention may be made from any one or more suitable metals, plastics, woods, fabrics, fibers, and / or combination(s) thereof (and / or any other suitable material(s) or combination(s) thereof) as would be understood by one of ordinary skill in the art.

[0038] Any reference to “the invention” is a reference to an embodiment of a family of inventions, with no single embodiment including an apparatus, process, or composition that should be included in all embodiments, unless otherwise stated. Further, although there may be discussion with regards to “advantages” provided by some embodiments of the present invention, it is understood that yet other embodiments may not include those same advantages, or may include yet different advantages. Any advantages described herein are not to be construed as limiting to any of the claims. The usage of words indicating preference, such as “various embodiments” or “preferably,” refers to features and aspects that are present in at least one embodiment, but which are optional for some embodiments, it therefore being understood that usage of words indicating preference implies the term “optional” and inflections thereof.

[0039] Like reference numerals refer to like parts throughout the description and the drawings. Additionally, the use of an N-series prefix for an element number (NXX.XX) refers to an element that is the same as the non-prefixed element (XX.XX), except as shown and described. As an example, an element 1020.1 would be the same as element825110305. v3125992.000548:GWR / pb2_25110305.V320.1 , except for those different features of element 1020.1 shown and described. Further, common elements and common features of related elements may be drawn in the same manner in different figures, and / or use the same symbology in different figures. As such, it is not necessary to describe the features of 1020.1 and 20.1 that are the same, since these common features are apparent to a person of ordinary skill in the related field of technology. Further, it is understood that some features 1020.1 and 20.1 may be backward compatible, such that a feature of a later discussed embodiment (NXX.XX) may include features compatible with other various embodiments that were discussed earlier (MXX.XX), as would be understood by those of ordinary skill in the art. This description convention also applies to the use of prime ('), double prime (“), triple prime ('”) and star or asterisk (*) suffixed element numbers. Therefore, it is not necessary to describe the features of 20.1 , 20.1 ’, 20.1”, 20.1 ”’ and 20* that are the same, since these common features are apparent to persons of ordinary skill in the related field of technology.

[0040] Some element numbers may be prefixed with an “X” indicating that the words pertain to any of the similar features shown in the drawings or described in the text. However, those of ordinary skill in the art will recognize various other non-X prefixed element numbers that discuss features applicable to other embodiments.

[0041] This document may use different words to describe the same element number, or to refer to an element number in a specific family of features (NXX.XX). It is understood that such multiple, different words are not intended to provide a redefinition of any language herein. It is understood that such words demonstrate that the particular feature can be considered in various linguistical ways, such ways not necessarily being additive or exclusive.925110305. v3125992.000548:GWR / pb2_25110305.V3

[0042] As used herein, the terms “flow,” “gas,” “gas flow,” “refrigerant,” “refrigerant flow,” and the like are intended to mean, generally, one or more gaseous or vaporous heat exchange mediums which may at times include various degrees of suspended oil or other substances as known in the art. Further, it should be appreciated that the compressor apparatuses described herein are, generally, designed to function as parts of air conditioning, refrigeration, heat pump, and / or other cooling and / or heating systems in which they may receive respective refrigerants from upstream parts of the systems through one or more inlet (suction) ports of their housings, compress the refrigerants within the housings, and provide the refrigerants back to downstream parts of the systems through one or more outlet (discharge) ports of their housings. However, it should also be appreciated that no invention described herein is intended to be particularly limited to any specific type or category of compressor (e.g., hermetic, semi-hermetic, etc.; single piston, dual piston, triple piston, etc.; rotary, reciprocating, etc.) except as expressly specified in a claim.

[0043] Additionally, it should be appreciated that any directional and / or orientational terms such as “top,” “upper,” “above,” “bottom,” “lower,” “below,” “left,” “right,” “front,” “forward,” “rear,” “rearward,” “aft,” and the like are merely used herein as generally indicative of relative orientations and / or positions of any corresponding parts, and are not intended to limit any invention described herein to any particular orientation or use except as expressly specified in a claim.

[0044] FIG. 1 illustrates a top front right perspective view of an electrically powered, single-cylinder rolling-piston rotary compressor apparatus 100 in accordance with aspects of the present disclosure. The compressor apparatus 100 includes a compressor1025110305. v3125992.000548:GWR / pb2_25110305.V3 housing 110, and includes an electrically powered single-cylinder rolling-piston rotary compressor electro-mechanical sub-assembly 180 (the electro-mechanical sub-assembly 180 is not visible in FIG. 1 , but see, e.g., FIG. 2, FIG. 17). The compressor housing 110 houses the electro-mechanical sub-assembly 180. In hermetic embodiments of the compressor apparatus 100, the compressor housing 110 may be hermetic and, accordingly, may be made primarily of welded or otherwise suitably hermetically sealed aluminum castings and / or other suitable and suitably hermetically sealed components and materials. In semi-hermetic embodiments of the compressor apparatus 100, the compressor housing 110 may be semi-hermetic and, accordingly, may be made primarily of bolted and gasketed or otherwise suitably semi-hermetically sealed aluminum castings and / or other suitable and suitably semi-hermetically sealed components and materials. The compressor housing 110 includes a housing front end cap 120, a generally cylindrical sidewall portion 140 having a sidewall inner diameter 150, and a housing back end cap 160. The front end cap 120 includes a plenary refrigerant discharge tube 200 extending therethrough. The discharge tube 200 includes a distal end 204. The distal end 204 couples to a hose, tube, or the like (not shown) for conveying compressed refrigerant gas thereto. The discharge tube includes an open plenary refrigerant discharge tube receiving end 210 positioned in the compressor housing 110 (the end 210 is not visible in FIG. 1 , but see, e.g., FIG. 17). The compressor apparatus 100 also includes mounting brackets 220. The brackets 220 are welded, bolted, or otherwise suitably attached to the sidewall portion 140.

[0045] FIG. 2 illustrates a top front right perspective partially exploded view of the compressor apparatus 100. The electro-mechanical sub-assembly 180 includes a single-1125110305. v3125992.000548:GWR / pb2_25110305.V3 cylinder rolling-piston rotary compressor 240 and an electric motor 260. The compressor 240 includes an inlet port 280 (not visible in FIG. 2, but see, e.g., FIG. 3, FIG. 6, FIG. 15). The electric motor 260 converts electrical power from an external power source (not shown) into mechanical rotation about an axis 300, and is mechanically coupled to the compressor 240 to convey the mechanical rotation thereto. The sidewall portion 140 defines an aperture (or “through hole”) 320 therethrough. The through hole 320 holds the inlet port 280 therein (the inlet port is not visible in FIG. 2, but see, e.g., FIG. 3, FIG. 6, FIG. 15). The compressor apparatus 100 also includes a J-tube suction accumulator 340. The suction accumulator 340 includes an inlet tube 360. The inlet tube 360 suitably couples to a hose, tube, or the like (not shown) for receiving upstream refrigerant gas therefrom. The suction accumulator 340 also includes a J-tube 380 having an outlet end portion 400. The end portion 400 suitably couples to the inlet port 280 of the compressor 240 to convey refrigerant gas thereto.

[0046] FIG. 3 illustrates a top front right perspective view of the single-cylinder rollingpiston rotary compressor 240. The compressor 240 includes a compressor front end cap 420. The end cap 420 includes a sidewall portion 440. The compressor 240 also includes a compressor main rotation bearing 452 fixedly coupled to the sidewall portion 140 of the compressor housing 110 (the compressor housing 110 and the sidewall portion 140 are not shown in FIG. 3, but see, e.g., FIG. 1 , FIG. 2). The main rotation bearing 452 includes a plate-like front side 456 (partially visible in FIG. 3; see also, e.g., FIG. 7, FIG. 16), and includes a back side 460 (the back side 460 is not visible in FIG. 3, but see, e.g., FIG. 12). The main rotation bearing 452 also includes refrigerant flow ducts 1520 arcuately spaced therearound and axially extending (with reference to the axis 300) therethrough1225110305. v3125992.000548:GWR / pb2_25110305.V3 from the front side 456 of the main rotation bearing 452 to the back side 460. The main rotation bearing 452 also includes a main rotation bearing inner race 464 extending axially therethrough about the axis 300 (the inner race 464 is not visible in FIG. 3, but see, e.g., FIG. 6, FIG. 7, FIG. 8, FIG. 12). The compressor 240 also includes check valves 446 (preferably implemented as leaf or reed valves attached to the front side 456 of the main rotation bearing 452), attached to the main rotation bearing 452, to control refrigerant flow through the ducts 1520.

[0047] The compressor 240 also includes a helical oil pump assembly 470. The helical oil pump assembly 470 is an Archimedes-screw type device that draws oil from an oil sump area 480 (not marked in FIG. 1 , but see, e.g., FIG. 17) within the compressor 240 and urges the oil to move in a generally rearward direction with reference to the axis 300. The helical oil pump assembly 470 extends from the compressor front end cap 420, generally forwardly along the axis 300, and bends downward to further extend into the oil sump area 480.

[0048] The compressor 240 also includes an annular oil screen 500 fitted around the sidewall portion 440 of compressor front end cap 420 and extending radially outwardly therefrom relative to the axis 300. The annular oil screen 500 filters at least some oil from refrigerant flowing within the compressor 240. It should be appreciated that the annular oil screen 500 may thereby reduce oil discharged from the compressor apparatus 100 through the discharge tube 200. The annular oil screen 500 may be made from a suitable widely available wire mesh, stainless steel, or any other suitable material(s). With reference to the axis 300, the annular oil screen 500 is axially positioned between the check valves 446 and the plenary refrigerant discharge tube receiving end 210 (the end1325110305. v3125992.000548:GWR / pb2_25110305.V3210 is not shown in FIG. 1 , but see, e.g., FIG. 17). Or, it may be said that (with reference to the axis 300) the annular oil screen 500 is located in front of the check valves 446 and behind the plenary refrigerant discharge tube receiving end 210. The annular oil screen 500 has an oil screen outer diameter 520. Preferably, the oil screen outer diameter 520 is equal to or about equal to the sidewall inner diameter 150 of the generally cylindrical sidewall portion 140 of the compressor apparatus 100.

[0049] The compressor 240 also includes a generally U-shaped flow deflector 540. The flow deflector 540 protects or shields the discharge tube from receiving otherwise more direct refrigerant flow. It should be appreciated, then, that the flow deflector 540 may reduce oil discharged from the compressor apparatus 100 through the discharge tube 200. The flow deflector 540 may be made from metal, plastic, or any other suitable material(s). The flow deflector 540 includes a plate-like mid portion 560 having an arcuate inner diametrical edge 580, an arcuate outer diametrical edge 600, a first radially extending side edge 620, and a second radially extending side edge 640. Preferably, the inner diametrical edge 580 is contoured to fit against and abuts the sidewall portion 440 of the compressor front end cap 420. Preferably, the outer diametrical edge 600 is contoured to fit against and abuts the sidewall inner diameter 150 of the generally cylindrical sidewall portion 140 of the compressor housing 110 (the sidewall portion 140 of the compressor housing 110 is not shown in FIG. 3, but see, e.g., FIG. 1 , FIG. 2). The flow deflector 540 also includes a first side tab portion 660 extending away from the platelike mid portion 560 (at the first radially extending side edge 620) generally toward the plenary refrigerant discharge tube receiving end 210 (the discharge tube receiving end 210 is not shown in FIG. 3, but see, e.g., FIG. 17). Preferably, the first side tab portion1425110305. v3125992.000548:GWR / pb2_25110305.V3660 extends perpendicularly or about perpendicularly away from the mid portion 560. The flow deflector 540 also includes a second side tab portion 680 extending away from the mid portion 560 (at the second radially extending side edge 640) generally toward the plenary refrigerant discharge tube receiving end 210 (again, the discharge tube receiving end 210 is not shown in FIG. 3, but see, e.g., FIG. 17). Preferably, the second side tab portion 680 extends perpendicularly or about perpendicularly away from the mid portion 560. With respect to the axis 300, the first radially extending side edge 620 and the second radially extending side edge 640 subtend an angle 700 enclosing the angular position of the plenary refrigerant discharge tube receiving end 210. Further, with reference to the axis 300, the mid portion 560 of the flow deflector 540 is axially positioned between the annular oil screen 500 and the plenary refrigerant discharge tube receiving end 210 (the discharge tube receiving end 210 is not shown in FIG. 1 , but see, e.g., FIG. 17). Or, it may be said that (with reference to the axis 300) the mid portion 560 is located in front of the annular oil screen 500 and behind the plenary refrigerant discharge tube receiving end 210. In some embodiments, the mid portion 560 may abut the annular oil screen 500. In some embodiments, the mid portion 560 may be spaced apart from the annular oil screen 500.

[0050] The compressor 240 also includes and an annular refrigerant flow guide (or “annular skirt”) 706 (the annular skirt 706 is not visible in FIG. 3, but see, e.g., FIG. 6, FIG. 7, FIG. 8). The compressor 240 also includes a hollow single-cylinder rolling-piston rotary compressor crankshaft 712 (the compressor crankshaft 712 is not visible in FIG. 3, but see, e.g., FIG. 6, FIG. 7, FIG. 8, FIG. 9, FIG. 10, FIG. 12, FIG. 13).1525110305. v3125992.000548:GWR / pb2_25110305.V3

[0051] FIG. 4 illustrates a top front right perspective view of the electric motor 260. The electric motor 260 includes an electric motor stator 720 fixedly coupled to the sidewall portion 140 of the compressor housing 110 (the compressor housing 110 and the sidewall portion 140 are not shown in FIG. 4, but see, e.g., FIG. 1 , FIG. 2), and the electric motor 260 includes and electric motor rotor 740. The electric motor 260 converts electrical power from an external power source (not shown) into mechanical rotation of the electric motor rotor 740 about the axis 300, and the electric motor rotor 740 is mechanically coupled to the compressor 240 to convey the mechanical rotation thereto (the compressor 240 is not shown in FIG. 4, but see, e.g., FIG. 2, FIG. 3, FIG. 5, FIG. 6, FIG. 7, FIG. 8, FIG. 15). The electric motor stator 720 has radially outer peripheral channels 760 spaced radially therearound. The channels 760 allow refrigerant to flow though them (between the electric motor stator 720 and the generally cylindrical sidewall portion 140 of the compressor housing 110) during operations of the compressor apparatus 100 (the sidewall portion 140 is not shown in FIG. 4, but see, e.g., FIG. 1 , FIG. 2). Additionally, portions (not marked in FIG. 4, but see, e.g., FIG. 14) of the electric motor stator 720 are radially spaced apart from each other by an annular gap 780, so as to allow refrigerant to flow therethrough during operations of the compressor apparatus 100. Preferably, the electric motor 260 converts the electrical power from the external power source (not shown) into clockwise mechanical rotation 790 of the electric motor rotor 740 (as from a front facing perspective reference to the compressor apparatus 100) about the axis 300.

[0052] FIG. 5 illustrates a top back left perspective view of the electric motor 260, and FIG. 6 illustrates a top back left perspective view of the single-cylinder rolling-piston rotary compressor 240. The compressor crankshaft 712 includes an aft shaft portion 796 (visible1625110305. v3125992.000548:GWR / pb2_25110305.V3 in FIG. 6) extending rearwardly about the axis 300. The aft shaft portion 796 has a closed rear end 804 attached to the electric motor rotor 740 to receive mechanical rotational power therefrom (the electric motor rotor 740 is not shown in FIG. 6, but see, e.g., FIG. 5, FIG. 13).

[0053] FIG. 7 and FIG. 8 illustrate a top front right perspective exploded view and a top rear right perspective exploded view, respectively, of the single-cylinder rolling-piston rotary compressor 240. The compressor 240 compresses a refrigerant (not shown in FIG. 7 or FIG. 8) and discharges the compressed refrigerant (not shown in FIG. 7 or FIG. 8) into the compressor housing 110 (the compressor housing 110 is not shown in FIG. 7 or FIG. 8, but see, e.g., FIG. 1 ). The compressor 240 includes fastening bolts 812, the helical oil pump assembly 470, the generally U-shaped flow deflector 540, the annular oil screen 500, the compressor front end cap 420, a compressor cylinder front cover plate 820, a leaf or reed valve 840, a compression roller 860, the inlet port 280, a compressor vane 880, a compressor cylinder 900, the check valves 446, the compressor main rotation bearing 452, a compressor rear end cap 940, the annular skirt 706, and the hollow singlecylinder rolling-piston rotary compressor crankshaft 712.

[0054] The crankshaft 712 extends through the compressor 240 (about the axis 300), and transmits mechanical power and distributes oil in the compressor 240. It should be appreciated that in FIG. 5 and FIG. 6 the compressor crankshaft 712 is shown as spaced apart from other components aligned along the axis 300 merely for clarity of exposition. The crankshaft 712 includes a forward shaft portion 1020. The forward shaft portion 1020 has an hollow front end 1040 and a rear end 1060. The hollow front end 1040 is rotatably coupled to the helical oil pump assembly 470 to rotate about the axis 300 and receive1725110305. v3125992.000548:GWR / pb2_25110305.V3 lubrication oil from the helical oil pump assembly 470 during operations of the compressor 240. The aft shaft portion 796 of the crankshaft 712 is aligned with the forward shaft portion 1020 about the axis 300, is about 4.5 times longer than the forward shaft portion 1020, has a front end 1100, and includes the closed rear end 804. Additionally, the aft shaft portion 796 has an external helicoidal groove (or external “helicoidal channel”) 1140 therein. The helicoidal groove 1140 spirals about 1 / 4 turn around the aft shaft portion 796 (about the axis 300) and extends from the front end 1100 of the aft shaft portion 796 toward the closed rear end 804 of the aft shaft portion 796 to a groove end 1160. With reference along the axis 300, the groove end 1160 is positioned about 35% of the way between the front end 1100 of the aft shaft portion 796 and the closed rear end 804 of the aft shaft portion 796. Preferably, the helicoidal groove 1140 spirals counterclockwise as it extends from the front end 1100 of the aft shaft portion 796 toward the closed rear end 804 of the aft shaft portion 796 (as from a front facing perspective reference to the compressor apparatus 100) about the axis 300. It should be appreciated, then, that from the front end 1100 of the aft shaft portion 796 toward the closed rear end 804 of the aft shaft portion 796 the helicoidal groove 1140 spirals oppositely to the clockwise mechanical rotation 790 of the electric motor rotor 740. The crankshaft 712 also includes a cam lobe 1180 interposed between the forward shaft portion 1020 and the aft shaft portion 796. The crankshaft 712 also includes an elongated hollow 1220 extending into the crankshaft 712 about the axis 300. The front end 1100 of the aft shaft portion 796 of the crankshaft 712 includes a first crankshaft sidewall bore 1240 defining a through hole extending radially outwardly between the elongated hollow 1220 and the helicoidal groove 1140 (the crankshaft sidewall bore 1240 is not visible in FIG. 7 or FIG. 8, but see, e.g.,1825110305. v3125992.000548:GWR / pb2_25110305.V3FIG. 9). The front end 1100 of the aft shaft portion 796 of the crankshaft 712 also includes a second crankshaft sidewall bore 1260 diametrically opposed to the first crankshaft sidewall bore 1240 and defining a through hole extending radially outwardly from the elongated hollow 1220 (the second crankshaft sidewall bore 1260 is not visible in FIG. 7 or FIG. 8, but see, e.g., FIG. 10). The hollow front end 1040 is rotatably coupled to rotate about the axis 300 and receive lubrication oil from the helical oil pump assembly 470. During operations of the compressor 240, the helical oil pump assembly 470 pumps oil into the elongated hollow 1220, some of the oil flows (from the elongated hollow 1220) through the crankshaft sidewall bore 1240 into the helicoidal groove 1140, and the helicoidal groove 1140 distributes and expels oil as it rotates about the axis 300. Preferably, the helicoidal groove 1140 axially extends through the main rotation bearing inner race 464 of the compressor main rotation bearing 452 about the axis 300.

[0055] FIG. 9 and FIG. 10 illustrate a first plan view and a second plan view, respectively, of the crankshaft 712. It should be appreciated that relative to FIG. 9, FIG. 10 shows the crankshaft 712 as rotated 180 degrees about the axis 300. The cam lobe 1180 extends farthest away from the axis 300 along a cam lobe peak extension line 1280.

[0056] FIG. 11 illustrates a top plan section schematic depiction of the crankshaft 712. The first crankshaft sidewall bore 1240 is angularly displaced from the cam lobe peak extension line 1280 about the axis 300 by a displacement angle 1290. It should be appreciated that in some embodiments the size of the displacement angle 1290 may be designed to keep the crankshaft sidewall bore 1240 in areas of minimum or relatively low bearing loads between the aft shaft portion 796 (where the sidewall bore 1240 is located) and the compressor main rotation bearing 452 as the aft shaft portion 796 rotates within1925110305. v3125992.000548:GWR / pb2_25110305.V3 the compressor main rotation bearing 452, which may facilitate oil flow from the sidewall bore 1240 and / or the helicoidal groove 1140 (the compressor main rotation bearing 452 is not shown in FIG. 11 , but see, e.g., FIG. 3, FIG. 5, FIG. 7, FIG. 8, FIG. 15, and FIG. 16) (the helicoidal groove 1140 is not shown in FIG. 11 , but see, e.g., FIG. 7, FIG. 8, FIG. 9, FIG. 10). Preferably, in single-cylinder rolling-piston rotary compressor embodiments and in dual-cylinder rolling-piston rotary compressor embodiments the displacement angle 1290 is 90 degrees or about 90 degrees.

[0057] FIG. 12 illustrates a perspective view of the crankshaft 712 and the compressor main rotation bearing 452. It should be appreciated that the main bearing is depicted as transparent merely for clarity of exposition. Meanwhile, FIG. 13 illustrates a perspective view of the crankshaft 712 and the electric motor rotor 740.

[0058] FIG. 14 illustrates a top back left perspective view of the electric motor 260. The electric motor stator 720 includes a radially outer electric motor stator ring 1300 encircling and axially centered about the axis 300. The outer electric motor stator 1300 has a maximum outer diameter 1320 and a minimum inner diameter 1340. The electric motor stator 720 also includes a radially inner electric motor stator ring 1360 encircling and axially centered about the axis 300, encircling the electric motor rotor 740, and encircled by the outer electric motor stator ring 1300. The inner electric motor stator ring 1360 has a maximum outer diameter 1380. The minimum inner diameter 1340 of the outer electric motor stator ring 1300 is greater than the maximum outer diameter 1380 of the inner electric motor stator ring 1360. The maximum outer diameter 1320 of the outer electric motor stator ring 1300 is greater than the minimum inner diameter 1340 of the outer electric motor stator ring 1300. The annular gap 780 radially extends between the2025110305. v3125992.000548:GWR / pb2_25110305.V3 maximum outer diameter 1380 of the inner electric motor stator ring 1360 and the minimum inner diameter 1340 of the outer electric motor stator ring 1300.

[0059] FIG. 15 illustrates a top back left perspective view of the single-cylinder rollingpiston rotary compressor 240. The annular skirt 706 has an annular front end 1400 abutting the compressor main rotation bearing 452. The front end 1400 has an outer diameter 1420. The annular skirt 706 also has a flanged annular rear end 1440 abutting the electric motor stator 720. The rear end 1440 has an outer diameter 1460 and an inner diameter 1480. The annular skirt 706 also includes a generally cylindrical sidewall 1500 axially extending (with reference to the axis 300) from the front end 1400 to the rear end 1440. The inner diameter 1480 of the flanged annular rear end 1440 is greater than the maximum outer diameter 1380 of the inner electric motor stator ring 1360. Meanwhile, the outer diameter 1460 of the flanged annular rear end 1440 is less than the maximum outer diameter 1320 of the outer electric motor stator ring 1300.

[0060] FIG. 16 illustrates a top front right perspective view of the compressor main rotation bearing 452. With reference to the axis 300, the ducts 1520 have a maximum radius 1540 and a minimum radius 1560. The outer diameter 1420 of the front end 1400 of the annular skirt 706 is equal to or less than twice the minimum radius 1560 of the ducts 1520 (the annular skirt 706, the front end 1400, and the outer diameter 1420 are not shown in FIG. 16, but see, e.g., FIG. 15).

[0061] FIG. 17 illustrates a plan sectional view of the compressor apparatus 100, in the direction of plane 17-17 of FIG. 1 . The compressor 240 includes a compressor discharge port 1580 that provides compressed refrigerant therefrom, and the compressor 240 includes a compressor discharge port 1600 that provides compressed refrigerant2125110305. v3125992.000548:GWR / pb2_25110305.V3 therefrom. It should be appreciated that (with reference to the axis 300) the annular oil screen 500 is axially positioned between the compressor discharge port 1580 (and the compressor discharge port 1600) and the plenary refrigerant discharge tube receiving end 210. Or, it may be said that (with reference to the axis 300) the annular oil screen 500 is located in front of the compressor discharge port 1580 (and in front of the compressor discharge port 1600) and behind the plenary refrigerant discharge tube receiving end 210. During operations of the compressor apparatus 100, refrigerant may flow generally rearward through the annular gap 780 (the gap 780 is not marked in FIG. 17, but see, e.g., FIG. 4, FIG. 14), may flow generally radially outward, and may flow generally forward through the radially outer peripheral channels 760 (the channels 760 are not marked in FIG. 17, but see, e.g., FIG. 4, FIG. 14). It should be appreciated that in some embodiments such refrigerant flow may tend to cool the electric motor 260. Further, refrigerant may flow through the ducts 1520 under control of the check valves 446 (the check valves 446 are not shown in FIG. 17, but see, e.g., FIG. 3, FIG. 7, FIG. 8). It should also be appreciated that in some embodiments such operations may contribute to pressure differences within the compressor housing 110 that may tend to urge lubricating oil that seeps into the compressor housing 110 from aft of the oil sump area 480 back toward the oil sump area 480 for suction and recirculation by the helical oil pump assembly 470.

[0062] FIG. 18 illustrates a top back right perspective view of an electrically powered, dual-cylinder rolling-piston rotary compressor apparatus 2000 in accordance with aspects of the present disclosure. The compressor apparatus 2000 includes a compressor housing 2010, an electric motor 2020 (the electric motor 2020 is not shown in FIG. 18,2225110305. v3125992.000548:GWR / pb2_25110305.V3 but see, e.g., FIG. 20), a dual-cylinder rolling-piston rotary compressor 2040 (the compressor 2040 is not shown in FIG. 18, but see, e.g., FIG. 20), and motor control electronics (not shown). The compressor housing 2010 houses the electric motor 2020, the compressor 2040, and the motor control electronics. The compressor housing 2010 includes a plate-like back cover portion 2060, a generally cylindroid motor holding portion 2080, an electronics enclosure portion 2090 extending from the motor holding portion 2080, and a generally bell-shaped compressor holding portion 2100 extending from the motor holding portion 2080. The motor holding portion 2080 extends between the back cover portion 2060 and the compressor holding portion 2100 about an axis of rotation 2110 of the compressor 2040 (the compressor 2040 is not shown in FIG. 18, but see, e.g., FIG. 20). In hermetic embodiments of the compressor apparatus 2000, the compressor housing 2010 may be hermetic and, accordingly, the back cover portion 2060, the motor holding portion 2080, the electronics enclosure portion 2090, and the generally bell-shaped compressor holding portion 2100 may be welded or otherwise suitably hermetically sealed aluminum castings and / or other suitable and suitably hermetically sealed components and materials. In semi-hermetic embodiments of the compressor apparatus 2000, the compressor housing 2010 may be semi-hermetic and, accordingly, the back cover portion 2060, the motor holding portion 2080, the electronics enclosure portion 2090, and the generally bell-shaped compressor holding portion 2100 may be bolted and gasketed or otherwise suitably semi-hermetically sealed aluminum castings and / or other suitable and suitably semi-hermetically sealed components and materials. The motor holding portion 2080 holds the electric motor 2020 (the electric motor 2020 is not shown in FIG. 18, but see, e.g., FIG. 20). The electronics enclosure2325110305. v3125992.000548:GWR / pb2_25110305.V3 portion 2090 holds the motor control electronics (not shown), which receive electrical power and electric motor control signals from one or more external sources (not shown) and provide electrical power and electric motor control signals to the electric motor 2020 (the electric motor 2020 is not shown in FIG. 18, but see, e.g., FIG. 20). The compressor holding portion 2100 holds the compressor 2040 (the compressor 2040 is not shown in FIG. 18, but see, e.g., FIG. 20), and includes a cyclonic plenary refrigerant discharge port assembly 2120. The discharge port assembly 2120 couples to a hose, tube, or the like (not shown) for conveying compressed refrigerant gas thereto. The discharge port assembly 2120 defines an elongated cyclonic action socket 2140 extending longitudinally about an axis 2160 (the socket 2140 is not marked in FIG. 18, but see, e.g., FIG. 20, FIG.21 , FIG. 22, FIG.22, FIG. 24), and includes a generally cylindroid cyclonic action tube 2180 recessed within the socket 2140 and axially aligned with the with the socket 2140 along the axis 2160 (the tube 2180 is not visible in FIG. 18, but see, e.g., FIG. 21 , FIG.22, FIG. 23).

[0063] FIG. 19 illustrates a top back left perspective exploded view of the back cover portion 2060, the motor holding portion 2080, and the compressor holding portion 2100 of the compressor housing 2010 (the electronics enclosure portion 2090 is not shown in FIG. 19, but see, e.g., FIG. 18).

[0064] FIG. 20 illustrates a plan sectional view of the compressor apparatus 2000, in the direction of plane 20-20 of FIG. 18. The motor holding portion 2080 substantially houses the electric motor 2020. The compressor holding portion 2100 substantially houses the compressor 2040. It should be appreciated that some semi-hermetic embodiments of the compressor apparatus 2000 may provide enhanced flexibilities for2425110305. v3125992.000548:GWR / pb2_25110305.V3 separately accommodating various geometries of the electric motor 2020 and the compressor 2040, and / or may facilitate separate servicing of the electric motor 2020 and the compressor 2040. The compressor 2040 includes a rolling-piston rotary compressor front end cap 2190, a helical oil pump assembly 2200 extending forwardly from the front end cap 2190, and a crankshaft 2210 extending rearwardly from the helical oil pump assembly 2200 about the axis of rotation 2110. The helical oil pump assembly 2200 is an Archimedes-screw type device that draws oil (not shown) from an oil sump area 2220 within the compressor holding portion 2100 of the compressor housing 2010 and urges the oil to move in a generally rearward direction through the crankshaft 2210. The helical oil pump assembly 2200 extends from the compressor front end cap 2190, forwardly about the axis of rotation 2110, and bends downward to further extend into the oil sump area 2220. The elongated cyclonic action socket 2140 includes an elongated socket sidewall 2226 and a sidewall bore 2232, which defines a hole through the sidewall 2226 (the sidewall 2226 is not marked in FIG. 20, but see. e.g., FIG. 21 , FIG. 22, FIG. 23, FIG. 24).

[0065] The compressor holding portion 2100 includes a front interior surface 2240 having a transverse wall portion 2260 protruding rearwardly therefrom. The transverse wall portion 2260 is positioned below the sidewall bore 2232, is spaced above the oil pump assembly 2200 by a suitable operating clearance 2300, and extends rearwardly to a suitable operating clearance 2320 from the front end cap 2190 of the compressor 2040. It should be appreciated that in some embodiments the transverse wall portion 2260 may somewhat isolate oil pooled in the oil sump area 2220 from refrigerant flow discharge2525110305. v3125992.000548:GWR / pb2_25110305.V3 turbulence, which may in turn protect operating efficiencies of the helical oil pump assembly 2200.

[0066] FIG. 21 illustrates an exploded rear plan view of the compressor holding portion 2100. Preferably, the transverse wall portion 2260 is generally gullwing-shaped and, accordingly, has an arcuate mid portion 2340, a right portion 2350 extending rightwardly outwardly and from the mid portion 2340, and a left portion 2360 extending outwardly leftwardly from the mid portion 2340. The discharge port assembly 2120 includes the cyclonic action tube 2180 and the cyclonic action socket 2140. The socket 2140 includes a bottom wall 2380 (the bottom wall 2380 is not visible in FIG. 21 , but see, e.g., FIG. 22, FIG. 23). The socket 2140 also includes the elongated socket sidewall 2226 and the sidewall bore 2232, which defines a hole through the sidewall 2226. The discharge port assembly 2120 also includes a generally cylindrical oil drip channel 2400 opening in the bottom wall 2380 and extending (downwardly) therefrom (about the axis 2160) through the right portion 2350 of the transverse wall portion 2260. Meanwhile, the cyclonic action tube 2180 includes an elongated tube sidewall 2420 extending about the axis 2160. The elongated tube sidewall 2420 has a tube outer diameter 2440. Further, the tube 2180 has an open bottom end 2480 and an open top end 2500. The elongated tube sidewall 2420 has tube length 2520 extending between the open bottom end 2480 and the open top end 2500. The tube 2180 also includes an annular flange 2540 extending around and radially outwardly from the open top end 2500 of the tube 2180. The annular flange 2540 has a flange outer diameter 2560. The flange outer diameter 2560 is greater than the tube outer diameter 2440. Further, the socket inner diameter 2420 is larger than the tube outer diameter 2440. It should be appreciated, then, that the sidewall bore 2232 is2625110305. v3125992.000548:GWR / pb2_25110305.V3 positioned radially outward (with reference to the axis 2160) from the elongated tube sidewall 2420.

[0067] FIG. 22 illustrates a plan sectional view of the compressor apparatus 2000, in the direction of plane 22-22 of FIG. 18. The elongated cyclonic action socket 2140 includes (in addition to the elongated socket sidewall 2226 and the sidewall bore 2232) a substantially cylindrical, flared plenary refrigerant discharge port 2580. The discharge port 2580 couples to a hose, tube, or the like (not shown) for conveying compressed refrigerant gas thereto, and has a discharge port inner diameter 2600 suitably slightly larger than the flange outer diameter 2560 of the cyclonic action tube 2180, such that the cyclonic action tube 2180 is recessed into the discharge port 2580 and is hermetically or semi-hermetically sealed therein via the annular flange 2540 of the cyclonic action tube 2180. The elongated socket sidewall 2226 has a socket sidewall length 2620. The open bottom end 2480 of the cyclonic action tube 2180 is spaced apart from the bottom wall 2380 of the cyclonic action socket 2140 along the axis 2160. Preferably, the socket sidewall length 2620 is about 1.6 times (about 60% larger) than the tube length 2520 of the cyclonic action tube 2180, so as to provide an axial spacing 2640 between the open bottom end 2480 and the bottom wall 2380 along the axis 2160. The elongated socket sidewall 2226 has a socket sidewall inner diameter 2660. Meanwhile, the generally cylindrical oil drip channel 2400 has a channel outer diameter 2680 suitably large enough to suitably drain oil from cyclonic action socket 2140 at a rate greater than the rate at which such oil is extracted from the refrigerant within the socket 2140 and, yet, suitably small enough to maintain a suitable refrigerant discharge flow thought the plenary refrigerant discharge port 2580. Preferably, the channel outer diameter 2680 is about 1 / 72725110305. v3125992.000548:GWR / pb2_25110305.V3(about 15%) as large as the socket sidewall inner diameter 2660 (the channel outer diameter 2680 is not marked in FIG. 22, but see, e.g., FIG. 23). During operations of the compressor apparatus 2000, the compressor 2040 discharges a compressed refrigerant 2570.

[0068] FIG. 23 illustrates a plan sectional view of the cyclonic plenary refrigerant discharge port assembly 2120, in the direction of plane 23-23 of FIG. 18. It should be appreciated that the sidewall bore 2232 of the elongated cyclonic action socket 2140 (visible in FIG. 21 and marked in FIG. 22) is not visible in FIG. 23 because it is located in a portion of the elongated socket sidewall 2226 that is not in the cross-section plane of FIG. 23. The socket sidewall inner diameter 2660 is suitably larger than the tube outer diameter 2440 of the generally cylindroid cyclonic action tube 2180 to provide a suitable annular space 2700 between the elongated tube sidewall 2420 and the elongated socket sidewall 2226.

[0069] FIG. 24 illustrates a top plan section schematic depiction of some preferable flow of the compressed refrigerant 2570 within the cyclonic plenary refrigerant discharge port assembly 2120 during operations of the compressor apparatus 2000 (the compressor apparatus 2000 is not comprehensively shown or marked in FIG. 24, but see, e.g., FIG. 18, FIG. 20, FIG. 22). During operations of the compressor apparatus 2000, the compressor 2040 (the compressor 2040 is not comprehensively shown or marked in FIG. 24, but see, e.g., FIG. 20, FIG. 22) discharges the compressed refrigerant 2570 into the compressor housing 2010 and thereby sufficiently raises the pressure of the refrigerant 2570 within the compressor housing 2010 to cause the compressed refrigerant 2570 to flow thorough the sidewall bore 2232 of the cyclonic action socket 2140 (and, more2825110305. v3125992.000548:GWR / pb2_25110305.V3 particularly, into the annular space 2700 between the elongated tube sidewall 2420 and the elongated socket sidewall 2226) (the cyclonic action socket 2140 is not comprehensively shown or marked in FIG. 24, but see, e.g., FIG. 21 , FIG. 22, FIG. 23). The elongated tube sidewall 2420 of the cyclonic action tube 2180 has a tube sidewall outer circumference 2720, and the elongated socket sidewall 2226 of the cyclonic action socket 2140 has a socket sidewall inner circumference 2730. Preferably, the sidewall bore 2232 is arranged and configured to act as a nozzle that jets the refrigerant 2570 into the annular space 2700 generally tangentially to the tube sidewall outer circumference 2720, is preferably tubular, preferably includes a first sidewall portion 2740 longitudinally extending along a first sidewall line 2760, and preferably includes a second sidewall portion 2780 longitudinally extending along a second sidewall line 2800, with the first sidewall line 2760 preferably being tangential to or about tangential to the tube sidewall outer circumference 2720, and with second sidewall line 2800 preferably being tangential to or about tangential to the socket inner wall circumference. The arrangement and configuration of the cyclonic plenary refrigerant discharge port assembly 2120 preferably causes at least some of the refrigerant to swirl around the elongated tube sidewall 2420 of the cyclonic action tube 2180 within the annular space 2700 in a generally spiral or helical manner. Preferably, this swirling effectively centrifuges at least some undesired oil from the compressed refrigerant 2570 onto the socket sidewall 2226, and / or otherwise causes undesired oil to coalesce from the refrigerant 2570 onto the socket sidewall 2226 and / or onto the outside of the action tube 2180. Further, such oil preferably moves down the socket sidewall 2226 (under the force of gravity or otherwise), and the generally cylindrical oil drip channel 2400 suitably drains that oil from the socket 2140 and channels2925110305. v3125992.000548:GWR / pb2_25110305.V3 that oil to the oil sump area 480 for recirculation / reuse within the compressor apparatus 2000 (e.g., under impetus of the helical oil pump assembly 2200). Further, a resulting, preferably relatively less oil-laden refrigerant 2820 (as compared to the refrigerant 2570) in due course flows (within the socket 21 0) to between the open bottom end 2480 of the cyclonic action tube 2180 and the bottom of the socket 2140, flows up through the elongated tube sidewall 2420 of the tube 2180 about the axis 2160, and then discharges from the compressor apparatus 2000 through the plenary refrigerant discharge port 2580 (the socket 2140, the tube 2180, and the discharge port 2580 are not comprehensively shown or marked in FIG. 24, but see, e.g., FIG. 22, FIG. 23).

[0070] It should be appreciated that aspects of the present disclosure may be incorporated into air and / or liquid heat exchanging air conditioning, refrigeration, heat pump, and / or other cooling and / or heating systems for electric vehicles, internal combustion engine vehicles, aircraft, marine vehicles, buildings, manufacturing systems, and / or any other suitable application(s).

[0071] Still further descriptions of various aspects of various embodiments of the present invention are included in the following paragraphs X1 through Xn (including the paragraphs that modify the paragraphs X1 through Xn).

[0072] X1. An apparatus, comprising: a compressor housing; a rolling piston rotary compressor assembly contained in the compressor housing, the rolling piston rotary compressor assembly including a main bearing fixedly coupled to the compressor housing; an electric motor assembly contained in the compressor housing, the electric motor assembly including an electric motor stator fixedly coupled to the compressor housing; a crankshaft extending from the compressor assembly, through the main3025110305. v3125992.000548:GWR / pb2_25110305.V3 bearing, and into the electric motor assembly; and an annular skirt extending from the main bearing to the electric motor stator.

[0073] X2. The apparatus of paragraph 1 , wherein the main bearing includes an arcuate refrigerant flow duct having a minimum inner radius, wherein the main bearing includes a check valve arranged and configured to control a refrigerant flow through the refrigerant flow duct, and wherein the annular skirt includes a first end, a second end having a maximum diameter less than twice the minimum inner radius of the arcuate refrigerant flow duct, and a sidewall extending between the fist end and the second end.

[0074] X3. The apparatus of paragraph 2, wherein the compressor housing is hermetic.

[0075] X4. The apparatus of paragraph 2, wherein the compressor housing is semi- hermetic.

[0076] X5. An apparatus, comprising: a compressor housing; a generally U-shaped flow diverter arranged and configured to divert a refrigerant flow within the compressor housing, the generally U-shaped flow diverter including a mid portion, a first side portion extending from the mid portion at about a 90 degree angle relative to the mid portion, and a second side portion extending from the mid portion at about a 90 degree angle relative to the mid portion, wherein the compressor housing includes a discharge tube having an end extending into the housing, wherein the end extending into the housing is positioned between the first and second side portions of the generally U-shaped flow diverter.

[0077] X6. The apparatus of paragraph 5, wherein the mid portion of the generally U- shaped flow diverter is arcuate.

[0078] X7. The apparatus of paragraph 6, wherein the compressor housing is hermetic.3125110305. v3125992.000548:GWR / pb2_25110305.V3

[0079] X8. The apparatus of paragraph 6, wherein the compressor housing is semi- hermetic.

[0080] X9. An apparatus for compressing a refrigerant and urging the refrigerant along a flow path, the apparatus comprising: a compressor housing including a discharge tube having an end extending into the compressor housing; and a rolling piston rotary compressor assembly contained in the housing, the rolling piston rotary compressor assembly including a compressor discharge port, a peripheral portion, and an annular oil screen, wherein the annular oil screen is arranged and configured to filter at least some of the oil from the refrigerant, wherein the annular oil screen extends around the peripheral portion of the rolling piston rotary compressor assembly and between the rolling piston rotary compressor assembly and the compressor housing, and wherein the annular screen is axially positioned between the compressor discharge port and the discharge tube.

[0081] X10. The apparatus of paragraph 9, wherein the compressor housing is hermetic.

[0082] X11 . The apparatus of paragraph 9, wherein the compressor housing is semi- hermetic.

[0083] X12. An apparatus, comprising: a compressor housing; a rolling piston rotary compressor assembly contained in the compressor housing, the rolling piston rotary compressor assembly including a main bearing fixedly coupled to the compressor housing; an electric motor assembly contained in the housing, the electric motor assembly including an electric motor stator fixedly coupled to the compressor housing; and a crankshaft extending from the compressor assembly, through the main bearing, and into3225110305. v3125992.000548:GWR / pb2_25110305.V3 the electric motor assembly, wherein the crankshaft includes a first shaft portion extending through the main bearing, wherein the first shaft portion has an outer surface, and wherein the outer surface of the first shaft portion defines a helicoidal oil flow channel.

[0084] X13. The apparatus of paragraph 12, wherein the compressor housing is hermetic.

[0085] X14. The apparatus of paragraph 12, wherein the compressor housing is semi- hermetic.

[0086] X15. An apparatus, comprising: a compressor housing including a generally bell-shaped section, a separate plate-like section, and a separate generally cylindroid section extending between the generally bell-shaped section and the plate-like section; a rolling piston rotary compressor assembly positioned in the generally bell-shaped section of the compressor housing; and an electric motor assembly rotationally coupled to the rolling piston rotary compressor assembly and positioned in the generally cylindroid section of the compressor housing.

[0087] X16. The apparatus of paragraph 15, wherein the compressor housing is hermetic.

[0088] X17. The apparatus of paragraph 15, wherein the compressor housing is semi- hermetic.

[0089] X18. An apparatus, comprising: a rolling piston rotary compressor assembly; and a compressor housing surrounding the rolling piston rotary compressor assembly, wherein the compressor housing includes a cyclonic plenary refrigerant discharge port assembly.3325110305. v3125992.000548:GWR / pb2_25110305.V3

[0090] X19. The apparatus of paragraph 18, wherein the cyclonic plenary refrigerant discharge port assembly includes an elongated tube portion.

[0091] X20. The apparatus of paragraph 19, wherein the compressor housing has an oil sump area therein, wherein the cyclonic plenary refrigerant discharge port assembly includes a socket portion, wherein the elongated tube portion has an open end positioned within the socket, and wherein the cyclonic plenary refrigerant discharge port assembly includes a channel extending from the socket portion to the oil sump area.

[0092] X21. The apparatus of paragraph 20, wherein the compressor housing is hermetic.

[0093] X22. The apparatus of paragraph 20, wherein the compressor housing is semi- hermetic.

[0094] X23. A method, comprising: within a compressor housing, flowing a refrigerant between a longitudinal tube sidewall portion and a longitudinal socket sidewall portion extending around the longitudinal tube sidewall portion; and receiving oil from the flowing refrigerant onto the longitudinal socket sidewall portion, wherein flowing the refrigerant includes swirling the refrigerant around the longitudinal tube sidewall portion.

[0095] X24. The method of paragraph 23, further comprising: flowing the refrigerant through the longitudinal tube sidewall portion.

[0096] X25. The method of paragraph 24, further comprising: discharging the refrigerant from the compressor housing after the refrigerant has flowed through the longitudinal tube sidewall portion.

[0097] X26. The method of paragraph 25, Further comprising channeling the oil to a sump area within the compressor housing.3425110305. v3125992.000548:GWR / pb2_25110305.V3

[0098] X27. The method of paragraph 26, wherein swirling the refrigerant includes swirling the refrigerant around the longitudinal tube sidewall portion within a hermetic compressor housing.

[0099] X28. The method of paragraph 26, wherein swirling the refrigerant includes swirling the refrigerant around the longitudinal tube sidewall portion within a semi- hermetic compressor housing.

[0100] X29. An apparatus for compressing a refrigerant and urging the refrigerant along a flow path, the apparatus comprising: a rolling piston rotary compressor including an oil pump assembly; and a compressor housing housing the rolling piston rotary compressor, wherein the compressor housing includes a refrigerant discharge port, and wherein the compressor housing includes a refrigerant discharge flow deflector positioned between the refrigerant discharge port and the oil pump assembly.

[0101] X30. The apparatus of paragraph 29, wherein the compressor housing includes a cyclonic plenary refrigerant discharge port assembly, and wherein the refrigerant discharge flow deflector is positioned between the cyclonic plenary refrigerant discharge port assembly and the oil pump assembly.

[0102] X31. The apparatus of paragraph 30, wherein the compressor housing is hermetic.

[0103] X32. The apparatus of paragraph 30, wherein the compressor housing is semi- hermetic.

[0104] While the invention(s) have been illustrated and described in the drawings and the text, the same is to be considered as illustrative and not restrictive in character, it being understood that only certain embodiments have been shown and described and3525110305. v3125992.000548:GWR / pb2_25110305.V3 that all changes and modifications that come within the spirit of the invention(s) are desired to be protected.3625110305. v3

Claims

125992.000548:GWR / pb2_25110305.V3CLAIMSWhat is claimed is:1 . An apparatus, comprising: a compressor housing; a rolling piston rotary compressor assembly contained in the compressor housing, the rolling piston rotary compressor assembly including a main bearing fixedly coupled to the compressor housing; an electric motor assembly contained in the compressor housing, the electric motor assembly including an electric motor stator fixedly coupled to the compressor housing; a crankshaft extending from the compressor assembly, through the main bearing, and into the electric motor assembly; and an annular skirt extending from the main bearing to the electric motor stator.

2. The apparatus of claim 1 , wherein the main bearing includes an arcuate refrigerant flow duct having a minimum inner radius, wherein the main bearing includes a checkvalve arranged and configured to control a refrigerant flow through the refrigerant flow duct, and wherein the annular skirt includes a first end, a second end having a maximum diameter less than twice the minimum inner radius of the arcuate refrigerant flow duct, and a sidewall extending between the fist end and the second end.

3. The apparatus of claim 2, wherein the compressor housing is hermetic.3725110305. v3125992.000548:GWR / pb2_25110305.V34. The apparatus of claim 2, wherein the compressor housing is semi-hermetic.

5. An apparatus, comprising: a compressor housing; and a generally U-shaped flow diverter arranged and configured to divert a refrigerant flow within the compressor housing, the generally U-shaped flow diverter including a mid portion, a first side portion extending from the mid portion at about a 90 degree angle relative to the mid portion, and a second side portion extending from the mid portion at about a 90 degree angle relative to the mid portion, wherein the compressor housing includes a discharge tube having an end extending into the housing, wherein the end extending into the housing is positioned between the first and second side portions of the generally U-shaped flow diverter.

6. The apparatus of claim 5, wherein the mid portion of the generally U-shaped flow diverter is arcuate.

7. The apparatus of claim 6, wherein the compressor housing is hermetic.

8. The apparatus of claim 6, wherein the compressor housing is semi-hermetic.

9. An apparatus for compressing a refrigerant and urging the refrigerant along a flow path, the apparatus comprising:3825110305. v3125992.000548:GWR / pb2_25110305.V3 a compressor housing including a discharge tube having an end extending into the compressor housing; and a rolling piston rotary compressor assembly contained in the housing, the rolling piston rotary compressor assembly including a compressor discharge port, a peripheral portion, and an annular oil screen, wherein the annular oil screen is arranged and configured to filter at least some of the oil from the refrigerant, wherein the annular oil screen extends around the peripheral portion of the rolling piston rotary compressor assembly and between the rolling piston rotary compressor assembly and the compressor housing, and wherein the annular screen is axially positioned between the compressor discharge port and the discharge tube.

10. The apparatus of claim 9, wherein the compressor housing is hermetic.

11. The apparatus of claim 9, wherein the compressor housing is semi-hermetic.

12. An apparatus, comprising: a compressor housing; a rolling piston rotary compressor assembly contained in the compressor housing, the rolling piston rotary compressor assembly including a main bearing fixedly coupled to the compressor housing; an electric motor assembly contained in the housing, the electric motor assembly including an electric motor stator fixedly coupled to the compressor housing; and3925110305. v3125992.000548:GWR / pb2_25110305.V3 a crankshaft extending from the compressor assembly, through the main bearing, and into the electric motor assembly, wherein the crankshaft includes a first shaft portion extending through the main bearing, wherein the first shaft portion has an outer surface, and wherein the outer surface of the first shaft portion defines a helicoidal oil flow channel.

13. The apparatus of claim 12, wherein the compressor housing is hermetic.

14. The apparatus of claim 12, wherein the compressor housing is semi-hermetic.

15. An apparatus, comprising: a compressor housing including a generally bell-shaped section, a separate platelike section, and a separate generally cylindroid section extending between the generally bell-shaped section and the plate-like section; a rolling piston rotary compressor assembly positioned in the generally bell-shaped section of the compressor housing; and an electric motor assembly rotationally coupled to the rolling piston rotary compressor assembly and positioned in the generally cylindroid section of the compressor housing.

16. The apparatus of claim 15, wherein the compressor housing is hermetic.

17. The apparatus of claim 15, wherein the compressor housing is semi-hermetic.4025110305. v3125992.000548:GWR / pb2_25110305.V318. An apparatus, comprising: a rolling piston rotary compressor assembly; and a compressor housing surrounding the rolling piston rotary compressor assembly, wherein the compressor housing includes a cyclonic plenary refrigerant discharge port assembly.

19. The apparatus of claim 18, wherein the cyclonic plenary refrigerant discharge port assembly includes an elongated tube portion.

20. The apparatus of claim 19, wherein the compressor housing has an oil sump area therein, wherein the cyclonic plenary refrigerant discharge port assembly includes a socket portion, wherein the elongated tube portion has an open end positioned within the socket, and wherein the cyclonic plenary refrigerant discharge port assembly includes a channel extending from the socket portion to the oil sump area.21 . The apparatus of claim 20, wherein the compressor housing is hermetic.

22. The apparatus of claim 20, wherein the compressor housing is semi-hermetic.

23. A method, comprising:4125110305. v3125992.000548:GWR / pb2_25110305.V3 within a compressor housing, flowing a refrigerant between a longitudinal tube sidewall portion and a longitudinal socket sidewall portion extending around the longitudinal tube sidewall portion; and receiving oil from the flowing refrigerant onto the longitudinal socket sidewall portion, wherein flowing the refrigerant includes swirling the refrigerant around the longitudinal tube sidewall portion.

24. The method of claim 23, further comprising: flowing the refrigerant through the longitudinal tube sidewall portion.

25. The method of claim 24, further comprising: discharging the refrigerant from the compressor housing after the refrigerant has flowed through the longitudinal tube sidewall portion.

26. The method of claim 25, Further comprising channeling the oil to a sump area within the compressor housing.

27. The method of claim 26, wherein swirling the refrigerant includes swirling the refrigerant around the longitudinal tube sidewall portion within a hermetic compressor housing.4225110305. v3125992.000548:GWR / pb2_25110305.V328. The method of claim 26, wherein swirling the refrigerant includes swirling the refrigerant around the longitudinal tube sidewall portion within a semi-hermetic compressor housing.

29. An apparatus for compressing a refrigerant and urging the refrigerant along a flow path, the apparatus comprising: a rolling piston rotary compressor including an oil pump assembly; and a compressor housing housing the rolling piston rotary compressor, wherein the compressor housing includes a refrigerant discharge port, and wherein the compressor housing includes a refrigerant discharge flow deflector positioned between the refrigerant discharge port and the oil pump assembly.

30. The apparatus of claim 29, wherein the compressor housing includes a cyclonic plenary refrigerant discharge port assembly, and wherein the refrigerant discharge flow deflector is positioned between the cyclonic plenary refrigerant discharge port assembly and the oil pump assembly.31 . The apparatus of claim 30, wherein the compressor housing is hermetic.

32. The apparatus of claim 30, wherein the compressor housing is semi-hermetic.4325110305. v3

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