US3451615A - Compressor lubricating system - Google Patents

Compressor lubricating system Download PDF

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Publication number
US3451615A
US3451615A US652789A US3451615DA US3451615A US 3451615 A US3451615 A US 3451615A US 652789 A US652789 A US 652789A US 3451615D A US3451615D A US 3451615DA US 3451615 A US3451615 A US 3451615A
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Prior art keywords
crankshaft
oil
passageway
port
shell
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Expired - Lifetime
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US652789A
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English (en)
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Paul B Hover
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Tecumseh Products Co
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Tecumseh Products Co
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B31/00—Compressor arrangements
    • F25B31/002—Lubrication
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/02—Lubrication
    • F04B39/0223—Lubrication characterised by the compressor type
    • F04B39/023—Hermetic compressors
    • F04B39/0238—Hermetic compressors with oil distribution channels
    • F04B39/0246—Hermetic compressors with oil distribution channels in the rotating shaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C3/00—Shafts; Axles; Cranks; Eccentrics
    • F16C3/04—Crankshafts, eccentric-shafts; Cranks, eccentrics
    • F16C3/06—Crankshafts
    • F16C3/14—Features relating to lubrication
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16N—LUBRICATING
    • F16N7/00—Arrangements for supplying oil or unspecified lubricant from a stationary reservoir or the equivalent in or on the machine or member to be lubricated
    • F16N7/36—Arrangements for supplying oil or unspecified lubricant from a stationary reservoir or the equivalent in or on the machine or member to be lubricated with feed by pumping action of the member to be lubricated or of a shaft of the machine; Centrifugal lubrication
    • F16N7/366—Arrangements for supplying oil or unspecified lubricant from a stationary reservoir or the equivalent in or on the machine or member to be lubricated with feed by pumping action of the member to be lubricated or of a shaft of the machine; Centrifugal lubrication with feed by pumping action of a vertical shaft of the machine
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S417/00—Pumps
    • Y10S417/902—Hermetically sealed motor pump unit

Definitions

  • crankshaft At the upper end of the crankshaft there is an axially directed port and a generally radially directed port for discharging oil from the bore. These two ports are arranged so that centrifugal force discharges oil from the bore through the radial port at low crankshaft speeds and through both ports at higher crankshaft speeds. Oil discharged at both speeds is directed toward the compressor shell at substantially the same vertical angle.
  • compressor parts are lubricated by pumping oil through a passageway in the crankshaft of the compressor.
  • the crankshaft passageway is eccentric to the rotational axis of the crankshaft to provide a pumping action.
  • As the oil moves upwardly through the passageway some of the oil is directed outwardly through suitaable ports in the crankshaft to lubricate compressor parts. Oil that is not used for lubricating is expelled at or near the top of the crankshaft and returns by gravity to a sump in the lower portion of the compressor shell for recirculation.
  • crankshaft speed also varies somewhat depending on the load.
  • a given type of compressor operating on 60 cycle alternating current for domestic use may run at one speed, say 3l503550 rpm, and the same type of compressor operating on 50 cycles alternating current for foreign use will run at a lower speed, say 2600-2950 r.p.m.
  • substantially all of the excess oil should be sprayed against the compressor shell in a substantially uniform pattern at all crankshaft speeds.
  • the objects of the present invention are to provide a lubricating system for a compressor-motor unit that overcomes the aforementioned disadvantages; that provides improved and more uniform cooling of the lubricating oil and the compressor-motor unit; that provides more uniform temperature variation at the compressor shell in response to temperature variation at other compressormotor parts within the shell; and that provides more effective, more uniform and more predictable operation of the unit as compared to units having prior art lubricating systems.
  • FIG. 1 is a vertical sectional view of a hermetically sealed compressor-motor unit incorporating a lubricating system of the present invention
  • FIG. 2 is a view of the crankshaft in the compressormotor unit of FIG. 1;
  • FIG. 3 is a side view of the crankshaft shown in FIG. 2;
  • FIG. 4 is a horizontal section taken on line 44 of FIG. 3 through a generally radial discharge port on the upper end of the crankshaft.
  • FIG. 5 is a horizontal section taken on line 55 of FIG. 3;
  • FIG. 6 is an enlarged fragmentary horizontal section from FIG. 4;
  • FIG. 7 is a vertical section taken on line 77 of FIG. 6 and also illustrates an oil stream leaving the crankshaft at low crankshaft speeds.
  • FIG. 8 is a fragmentary side view taken on line 8-8 of FIG. 6;
  • FIG. 9 is an enlarged fragmentary top view of the crankshaft.
  • FIG. 10 is an enlarged vertical section corresponding to FIG. 7 and illustrating an oil stream leaving the crankshaft at high crankshaft speeds.
  • FIG. 1 illustrates a hermetically sealed compressormotor 14 comprising the usual hermetically sealed shell 16 with a motor 18 and a compressor 20 mounted together on shell 16 with the compressor disposed above the motor.
  • the compressor-motor may be generally conventional and thus will be described in detail only to the extent necessary to an understanding of the present invention.
  • the compressor 20 includes a crankshaft 22 journalled in bearings 23, 24 and having a crankshaft extension 25 that serves as the rotor shaft for motor 18.
  • Mounted on the lower end of the crankshaft 22 is a sump pump 26 projecting into a pool of lubricating oil 27 collected in the lower portion of shell 16.
  • an axial bore 28 In the lower portion of crankshaft 22 is an axial bore 28 (FIG.
  • pump 26 comprises the stepped pick-up tube shown in FIG. land disclosed and claimed in a copending United States application, Ser. No. 636,476, filed May 5, 1967, other conical-centrifugal pumps, such as described in United States Patent No. 2,287,203 may be used to lift oil from the bottom of shell 16 upwardly through bore 28 and into bore 32.
  • crankshaft 22 has the usual porting arrangements for lubricating various compressor parts.
  • Bearing 23 is lubricated by means including a port 38 and a spiral groove 40.
  • a piston 42 and a cylinder 44 are lubricated by means including a port 46 (FIG. 5) in a crankpin 48 and bearing 24 is lubricated by means including a radial port 50 (FIG. 3).
  • crankshaft 22 Opens upwardly at a top face 52 on crankshaft 22 to form an axial discharge port (FIGS. 2 and 9).
  • Crankshaft 22 also has a generally radial passageway 61 communicating at its inner end with bore 32. The outer end of passageway 61 opens at the side of crankshaft 22,
  • ports 60, 62 are such that excess oil leaves crankshaft 22 in a stream designated generally at 63 (FIG. 1).
  • the oil stream 63 is directed upwardly and outwardly toward an inner top surface 64 of shell 16 at a vertical angle Within a predetermined angular range to assure that all or substantially all of the oil contacts the shell for effective cooling of the oil and uniform temperature variation of the shell in response to temperature variations at motor 18 and compressor 20. As the rotational speed of crankshaft 22 increases, the oil stream 63 would tend to become more upwardly inclined.
  • crankshaft 22 With increased crankshaft speeds, oil also leaves crankshaft 22 via port 60
  • the oil leaving port 60 combines with the oil leaving port 62 in such a way that the combined stream remains at approximately the same vertical angle as the stream issuing from port 62 alone at low crankshaft speeds.
  • bore 32 has a circular transverse cross section and a vertically disposed longitudinal axis 66.
  • the diameter of bore 32 and the location of axis 66 are such that bore 32 is located radially of axis 30 and oil is forced radially outwardly in bore 32 by centrifugal force. Oil moves upwardl in bore 32 toward ports 60, 62 as a narrow film 65 located along a radially outermost zone of bore 32.
  • Axis 66 lies in a vertical plane 68 which also contains axi 30.
  • Rotation of crankshaft 22 is clockwise as viewed in FIGS. 6 and 9.
  • the top face 52 of crankshaft 22 is dome-shaped, inclining slightly downwardly and radially outwardly from axis 30.
  • Port 60 is slightly elliptical due to the downward curvature of face 52.
  • crankshaft 22 i recessed inwardly at 69 just below face 52 and radially outwardly of port 60.
  • the bottom of recess 69 forms a flat generally chordal face 72 containing port 62, Face 72 begins slightly trailing plane 68 and extends into crankshaft 22 beyond port 62. Face 72 is also inclined downwardly and inwardly of crankshaft 22 below port 62 at a slight vertical angle 73 which is about in the preferred embodiment.
  • Recess 69 is a fragmentary counterbore in the preferred embodiment, although the particular configuration is not essential to the present invention.
  • the generally radial passageway 61 extends inwardly from port 62 through the side wall of crankshaft 22 and opens at its inner end into bore 32.
  • Passagewa 61 has a longitudinal axis 78 that intersects plane 68 at a horizontal angle 79 from plane 68.
  • Axis 78 is perpendicular to face 72 and thus axis 78 and passageway 61 are inclined downwardly from axis 66 at 10 in the preferred embodiment.
  • angle 79 is 45.
  • the diameter of passageway 61 and the angle of axis 78 are such that a leading wall portion 80 of the passageway intersects bore 32 closely adjacent plane 68 to intercept the oil 65 at low crankshaft speeds. As viewed in FIG. 6, the leading wall portion 80 is clockwise from the bottom of passageway 61. This arrangement assures that oil entering passageway 61 moves upwardly and generally radially outwardly on the leading wall 80.
  • passageway 61 on the leading wall 80, that is, slightl leading the bottom of the pasageway.
  • surface tension and cohesion of the oil film causes all of the oil to move into pasageway 61.
  • Centrifugal force causes the oil in passageway 61 to move upwardly and radially outwardly along wall as illustrated at 84 (FIGS. 6 and 7).
  • the oil 84 passing outwardly through passageway 61 tends to exit from the port 62 at the most forward or leading location on the port designated at 86 (FIG. 8).
  • the oil 84 continues upwardly along the intersection edge between passage 61 and face 72 and leaves crankshaft 22 at a point designated by numeral 88.
  • oil from port 62 leaves in a stream 90 inclined upwardly and radially outwardly from the crankshaft toward surface 64 of shell 16.
  • the vertical angle 92 at which stream 90 leaves crankshaft 22 is chosen so that all or at least most of the oil strikes the top of the shell 16. In the preferred embodiment, the vertical angle 92 is on the order of from 1030 for the particular arrangement of shell 16 and the top of the crankshaft 22 shown in FIG, 1.
  • each particle of oil in stream 90 follows a linear path once it leaves crankshaft 22, as the crankshaft 22 rotates the oil stream 90 will appear to spiral outwardly and rearwardly as illustrated in FIG. 6.
  • Oil in stream 90 flows down the inner surface of the shell due to adhesion and gravity and returns to the bottom of the shell. The oil transfers heat from motor 18 and compressor 20 to shell 16 which in turn transfers heat to the surrounding environment.
  • the direction of the oil stream leaving crankshaft 22 is selected to assure that the oil remains in contact with shell 16 for the longest possible time as it flows downwardly on the inner surface of the shell to the sump.
  • the angle of the oil stream is directed toward the top of shell 16 rather than toward the side of the shell so that it must travel further along the shell to reach the bottom. This increases the amount of heat transferred from the oil to the shell.
  • additional and more uniform cooling of the oil and of the compressor and the motor is achieved as compared to prior art lubricating systems. Cooling of the oil is efficient at different compressor speeds for a given compressor and relatively uniform for different compressors of the same general type. Uniform and efficient distribution of the oil also tends to provide relatively uniform temperature variation at the shell in response to temperature variations at other compressor parts.
  • FIG. 1 there is an overload protection apparatus 106 mounted on the exterior of shell 16.
  • the overload protection circuit is generally conventional and operates in response to the temperature at the shell.
  • the overload protection circuit can be designed with greater sensitivity and less tolerance than would have to be allowed for nouniform temperature response with prior art units.
  • passageway 61 (axis 78) is not on a true radius of crankshaft 22 (axis 30) although it is radial to bore 32 (axis 66).
  • radial is used broadly herein to describe port 62 and passageway 61 and is intended to include arrangements where there is a radial displacement between the port and the oil film so that centrifugal force can propel the oil radially outwardly through the passageway.
  • a compressor having a crankshaft provided with a bore through which lubricating fluid is pumped and wherein said crankshaft has discharge means on an upper end portion thereof which is spaced from a shell of said compressor and ada ted to fling lubricating fluid from said bore outwardly of said crankshaft against said shell and wherein said bore opens at a top face of said crankshaft to form a first port of said discharge means
  • said discharge means further comprises a generally radial passageway in said upper portion of said chankshaft, said passageway having a radially inner end opening into said bore below said first port and a radially outer end opening at a side of said end portion below said first port to form a second discharge port, said second discharge port being in substantially constant communication with said space between said shell and said upper end portion of said crankshaft throughout substantially a full 360 rotation of said crankshaft so that fluid in said bore is discharged from said second port and flung against said shell throughout substantially a full 360 rotation of said crankshaft
  • a compressor having a crankshaft provided with a bore through which lubricating fluid is pumped and wherein said crankshaft has discharge means on an upper end portion thereof spaced from a shell of said compressor 6 to fling lubricating fluid from said bore outwardly of said crankshaft against said shell
  • said discharge means further comprises a generally radial passageway in said upper portion of said crankshaft, said passageway having a radially inner end opening into said bore and a radially outer end opening at a side of said end portion to form a discharge port, said discharge port being in substantially constant communication with said space between said shell and said upper end portion of said crankshaft throughout substantially a full 360 rotation of said crankshaft so that fluid in said bore is discharged from said port and flung against said shell throughout substantially a full 360 rotation of said crankshaft substantially free of obstruction from other compressor parts.
  • said discharge means further comprises a generally chordal face on the side of said crankshaft, said face is inclined downwardly and radially inwardly on said crankshaft, and said port opens at said face so as to form an intersecting edge between said face and said second passageway inclined upwardly and radially outwardly to impart additional lift to lubricant discharged from said port.
  • a lubricating system for an apparatus having a rotatable body therein, said body having a passageway therethrough to conduct lubricating oil through said body, means for moving oil through said passageway while said body rotates, said passageway being disposed in said body to extend in substantially the same direction as the rotational axis of said body and being offset radially from said axis so that when said body is rotating centrifugal force tends to propel said oil radially outwardly from said axis but radially outward movement of the oil is limited by the inner wall of the body bounding said passageway, first discharge means on said body operatively communieating with said passageway and opening exteriorly of said body so that when said body rotates at one speed centrifugal force propels oil through said first discharge means and outward from said body directed within a predetermined angular range relative to a radial plane through said body, and second discharge means on said body operatively communicating with said passageway and opening exteriorly of said body so that when said body rotates at a second speed
  • a lubricating system for a compressor of the type having a rotatable crankshaft, a passageway in said crankshaft for conducting lubricating oil through the shaft, lubricating outlets on said shaft to conduct oil from said passageway to other compressor parts, means for moving oil through said passageway while said shaft rotates, and discharge means on said shaft downstream of said lubricating outlets and communicating from said passageway through the wall of said shaft to conduct oil from said passageway and discharge the oil exteriorly of the shaft when said shaft is rotating, said discharge means comprising first discharge port means constructed so that at one rotational speed of said shaft oil from said passage- Way leaves said shaft through said first discharge port means in a stream having a predetermined direction relative to said shaft, and second discharge port means constructed so that at a second rotational speed of said shaft oil from said passageway leaves said shaft through said second discharge port means in a direction to combine with oil leaving said shaft from said first discharge port means and maintain the direction of said combined stream of oil from said first and said second discharge port means at substantially said predetermined direction relative to said shaft
  • a compressor-motor unit comprising a housing, a compressor mounted in the housing and having a crankshaft rotatable about a vertically disposed axis, liquid lubricant in said housing, a sump in the lower portion of the housing for collecting said lubricant, a passageway in said crankshaft extending in a direction generally axially of said crankshaft, said passageway including an upper portion in the upper portion of the crankshaft eccentric to the rotational axis of said crankshaft, pump means for moving lubricant from said sump upwardly into said passageway, first discharge means on said upper crankshaft portion operatively communicating with said upper passageway portion and constructed so that at low crankshaft speeds lubricant leaves said crankshaft in a stream directed generally radially outwardly of said shaft toward said housing within a predetermined range of vertical angles relative to a radial plane through said shaft, and second discharge means on the upper crankshaft portion operatively communicating with said upper passageway portion and constructed so that at higher crankshaft speeds lubric
  • said first discharge means includes a port opening at a side of said crankshaft in a direction generally radially outwardly of said crankshaft to direct said stream upwardly and outwardly from said crankshaft toward said housing at low crankshaft speeds and said second discharge means includes a second port disposed above said first port and opening generally axially of the crankshaft eccentric to said rotational axis.
  • said second port opens at a top end face of said crankshaft above said first discharge port and said end face slopes downwardly and radially outwardly from said second port toward said first port so that at said higher crankshaft speeds lubricant leaving said second port is directed downwardly and radially outwardly by said face toward said first discharge port to combine with lubricant leaving said crankshaft through said first port.
  • said upper passageway portion opens at a top face of said crankshaft to form said second port, said upper passageway portion has a longitudinal axis disposed in a vertical plane which contains said rotational axis, and said first port has an axis extending therethrough and intersecting said longitudinal axis at a vertical angle with respect to said radial plane.
  • said first discharge means comprises a second passageway having a radially outer end opening at the side of said crankshaft to form said first port and a radially inner end opening at said first mentioned passageway closely adjacent said vertical plane.
  • said first discharge means further includes a generally chordal face on the side of said crankshaft, said face is inclined downwardly and radially inwardly of said crankshaft, and said first port opens at said face so as to form an intersecting edge between said face and said second passageway inclined upwardly and radially outwardly to impart additional lift to lubricant discharged from said first port.
  • said first discharge means comprises a second passageway communicating at its radially inner end with said first passageway and opening at its radially outer end at a side of said crankshaft to form said first port, said second passageway having a wall that directs lubricant upwardly and radially outwardly when lubricant is moved through said second passageway by centrifugal force.
  • said first passageway opens upwardly at a generally horizontal upper face on said crankshaft to form said second port and said upper face slopes downwardly and radially outwardly from said second port to direct lubricant leaving said second port in a downwardly and radially outwardly direction due to centrifugal force.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Ocean & Marine Engineering (AREA)
  • Compressor (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
US652789A 1967-07-12 1967-07-12 Compressor lubricating system Expired - Lifetime US3451615A (en)

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US65278967A 1967-07-12 1967-07-12

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US (1) US3451615A (en:Method)
BE (1) BE716868A (en:Method)
DE (1) DE1775061B1 (en:Method)
DK (1) DK125107B (en:Method)
ES (1) ES356063A1 (en:Method)
FR (1) FR1571680A (en:Method)
GB (1) GB1199370A (en:Method)
LU (1) LU56337A1 (en:Method)
NL (1) NL6809869A (en:Method)

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4097185A (en) * 1976-09-13 1978-06-27 Tecumseh Products Company Lubricating device
JPS5776201A (en) * 1980-10-31 1982-05-13 Hitachi Ltd Oil feed device for scroll hydraulic machine
DE3128385A1 (de) * 1980-07-18 1982-05-27 Aspera S.p.A., Castelnuovo Don Bosco, Asti Kompressor fuer kuehlfluide
US4569639A (en) * 1982-05-03 1986-02-11 Tecumseh Products Company Oil distribution system for a compressor
DE3632963A1 (de) * 1985-12-26 1987-07-02 Unidad Hermetica Sa Schmierungssystem
US4834627A (en) * 1988-01-25 1989-05-30 Tecumseh Products Co. Compressor lubrication system including shaft seals
WO1999043952A1 (de) * 1998-02-28 1999-09-02 Robert Bosch Gmbh Bauteil mit einer bohrung
DE10106234A1 (de) * 2001-02-10 2002-08-29 Danfoss Compressors Gmbh Kolbenverdichter
US6702067B2 (en) 2000-10-28 2004-03-09 Danfoss Compressors Gmbh Piston compressor, particularly hermetically enclosed refrigerant compressor
US20040247474A1 (en) * 2002-06-05 2004-12-09 Hiroshi Kitaura Rotary compressor
US20050265863A1 (en) * 2002-06-26 2005-12-01 Matsushita Refrigeration Company Hermetic compressor
WO2011023810A1 (en) * 2009-08-31 2011-03-03 Arcelik Anonim Sirketi Variable capacity hermetic compressor
WO2014155923A1 (ja) * 2013-03-29 2014-10-02 ダイキン工業株式会社 圧縮機

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1983003878A1 (en) * 1982-05-03 1983-11-10 Tecumseh Products Company Oil distribution system for a compressor
US4576555A (en) * 1984-11-13 1986-03-18 Tecumseh Products Company Oil dispersing device
RU2173403C1 (ru) * 2000-01-05 2001-09-10 Федеральное государственное унитарное предприятие "Вятское машиностроительное предприятие "АВИТЕК" Герметичный компрессор

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US2125645A (en) * 1936-06-11 1938-08-02 Crosley Radio Corp Lubricating enclosed engines
US2809872A (en) * 1953-07-16 1957-10-15 Whirlpool Seeger Corp Lubricating bearings of refrigerator compressor

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US2287203A (en) * 1939-09-29 1942-06-23 Gen Motors Corp Refrigerating apparatus
DE1891226U (de) * 1961-11-25 1964-04-16 Danfoss As Kurbelwelle mit oelzufuhrkanal.

Patent Citations (2)

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US2125645A (en) * 1936-06-11 1938-08-02 Crosley Radio Corp Lubricating enclosed engines
US2809872A (en) * 1953-07-16 1957-10-15 Whirlpool Seeger Corp Lubricating bearings of refrigerator compressor

Cited By (21)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4097185A (en) * 1976-09-13 1978-06-27 Tecumseh Products Company Lubricating device
DE3128385A1 (de) * 1980-07-18 1982-05-27 Aspera S.p.A., Castelnuovo Don Bosco, Asti Kompressor fuer kuehlfluide
US4478559A (en) * 1980-07-18 1984-10-23 Aspera S.P.A. Compressor with ducted crankshaft having a grooved end for oil distribution
JPS5776201A (en) * 1980-10-31 1982-05-13 Hitachi Ltd Oil feed device for scroll hydraulic machine
US4569639A (en) * 1982-05-03 1986-02-11 Tecumseh Products Company Oil distribution system for a compressor
DE3632963A1 (de) * 1985-12-26 1987-07-02 Unidad Hermetica Sa Schmierungssystem
US4834627A (en) * 1988-01-25 1989-05-30 Tecumseh Products Co. Compressor lubrication system including shaft seals
WO1999043952A1 (de) * 1998-02-28 1999-09-02 Robert Bosch Gmbh Bauteil mit einer bohrung
DE10053574B4 (de) * 2000-10-28 2005-07-28 Danfoss Compressors Gmbh Kolbenverdichter, insbesondere hermetisch gekapselter Kältemittelverdichter
US6702067B2 (en) 2000-10-28 2004-03-09 Danfoss Compressors Gmbh Piston compressor, particularly hermetically enclosed refrigerant compressor
US6688432B2 (en) 2001-02-10 2004-02-10 Danfoss Compressors Gmbh Piston compressor
DE10106234C2 (de) * 2001-02-10 2002-12-12 Danfoss Compressors Gmbh Kolbenverdichter
DE10106234A1 (de) * 2001-02-10 2002-08-29 Danfoss Compressors Gmbh Kolbenverdichter
US20040247474A1 (en) * 2002-06-05 2004-12-09 Hiroshi Kitaura Rotary compressor
US7322809B2 (en) 2002-06-05 2008-01-29 Daikin Industries, Ltd. Rotary compressor with sealing portions and oil-supply groove
US20050265863A1 (en) * 2002-06-26 2005-12-01 Matsushita Refrigeration Company Hermetic compressor
WO2011023810A1 (en) * 2009-08-31 2011-03-03 Arcelik Anonim Sirketi Variable capacity hermetic compressor
WO2014155923A1 (ja) * 2013-03-29 2014-10-02 ダイキン工業株式会社 圧縮機
JP5652497B2 (ja) * 2013-03-29 2015-01-14 ダイキン工業株式会社 圧縮機
US9447786B2 (en) 2013-03-29 2016-09-20 Daikin Industries, Ltd. Compressor with trailing and leading edges of oil discharge passage displaced behind trailing and leading edges of oil supply hole
EP2980406A4 (en) * 2013-03-29 2016-11-09 Daikin Ind Ltd COMPRESSOR

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BE716868A (en:Method) 1968-12-20
GB1199370A (en) 1970-07-22
DK125107B (da) 1972-12-27
DE1775061B1 (de) 1971-10-14
FR1571680A (en:Method) 1969-06-20
ES356063A1 (es) 1970-04-01
LU56337A1 (en:Method) 1969-04-25
NL6809869A (en:Method) 1969-01-14

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