EP0182993B1 - Rotary compressor lubrication arrangement - Google Patents

Rotary compressor lubrication arrangement Download PDF

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Publication number
EP0182993B1
EP0182993B1 EP19850111798 EP85111798A EP0182993B1 EP 0182993 B1 EP0182993 B1 EP 0182993B1 EP 19850111798 EP19850111798 EP 19850111798 EP 85111798 A EP85111798 A EP 85111798A EP 0182993 B1 EP0182993 B1 EP 0182993B1
Authority
EP
European Patent Office
Prior art keywords
oil
crankshaft
vane
cylinder
compressor
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired
Application number
EP19850111798
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0182993A1 (en
Inventor
Edwin L. Gannaway
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Tecumseh Products Co
Original Assignee
Tecumseh Products Co
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Tecumseh Products Co filed Critical Tecumseh Products Co
Publication of EP0182993A1 publication Critical patent/EP0182993A1/en
Application granted granted Critical
Publication of EP0182993B1 publication Critical patent/EP0182993B1/en
Expired legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/008—Hermetic pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/02—Lubrication; Lubricant separation
    • F04C29/023—Lubricant distribution through a hollow driving shaft

Definitions

  • This invention pertains to hermetic rotary compressors for compressing refrigerant in refrigeration systems such as refrigerators, freezers, air conditioners and the like.
  • this invention relates to the manner of lubricating the sliding vanes in a rotary compressor.
  • prior art rotary hermetic compressors comprise a housing in which are positioned a motor and a compressor cylinder.
  • the motor drives a crankshaft having an eccentric portion thereon for revolving inside a bore which is located centrally in the compressor cylinder.
  • the eccentric has a roller rotatably mounted thereon which revolves within the bore as the crankshaft rotates.
  • One or more sliding vanes which are slidably received in slots located in the cylinder wall cooperate with the roller to provide the pumping action for compressing refrigerant within the cylinder bore.
  • the operating parts of rotary hermetic compressors are machined to extremely close tolerances and the surfaces of the parts are finished to a high degree in order to prevent leakage in the compressor and to provide a very efficient compressor. It is important to properly lubricate the operating parts to preserve the surface finish. Additionally, it is important that proper lubrication be provided for the moving parts of the compressor so that dynamic friction is kept low and frictional losses are minimized. Lastly, by providing adequate lubrication a minimum amount of heat due to friction losses is generated, heat transfer is reduced and the compressor efficiency is improved.
  • U.S. Patent 3,499,600 shows a compressor wherein the rotor has a vane slot 24 in which the sliding vane 25 reciprocates.
  • the object of the invention is to lubricate the rotor and to that end, oil is pumped upwardly through axial passage 19 in the crankshaft and then outwardly through holes 30, then upwardly through passage 33 into an annular passage 34 to lubricate the lower face of rotor 16. Some of the oil will also flow upwardly through passages 35 to both lubricate vane 25 and also provide lubricant for the upper surface 37 of rotor 16.
  • U.S. Patent 3,513,476 discloses a gravity fed lubrication system whereby oil overflows raised ridges 28 to flow through perforations 16 into grooves 38a and 38b. The oil then returns to the sump. Thus this patent does not disclose supplying lubricant for the vane slot grooves under positive pressure from a pump.
  • U.S. Patent 2,883,101 also discloses a gravity fed lubrication system whereby oil is pumped upwardly from sump 24 through passes 25 and 27 to cavity 29 from which the oil exits through port 40 into reservoir 32 and from there travels downwardly, by gravity, through passage 43 and slot 42 in the side of vane 14.
  • this reference also does not disclose a pressure fed lubrication system for lubracting the vane.
  • Japanese Abstract Vol. 7, Number 189 of August 18 1983 discloses a rotary compressor wherein oil is caused to flow into oil grooves 12a and 12b because of the pressure different in the compressor casing, suction chamber 14, and compression chamber 15.
  • U.S. Patent 3,565,552 discloses a compressor with lubricant ducts 28 and 29 wherein the pressure difference between the compressor casing and the compressor chamber causes lubricant in reservoir 11 to be sucked out of the lubricant feeder 31 to flow into compression chamber 12.
  • U.S. Patent No. 2,107,630 discloses an oil pump 61 in recess 60 for lubricating the bearings and other surfaces of the compressor.
  • U.S. Patent No. 2,072,307 discloses a compressor having a helical groove 139 in the crankshaft of the compressor to draw oil upwardly.
  • the present invention overcomes the disadvantages of the above-described prior art rotary hermetic compressors by providing an improved lubrication arrangement for a rotary compressor, such as is defined by the characterizing part of the claim.
  • a lubricating arrangement for a rotary hermetic compressor wherein an oil pump provides oil under positive pressure to both sides of the sliding vane and wherein the excess oil returns to the sump by means of gravity.
  • the present invention comprises a lubrication arrangement in a rotary hermetic compressor wherein an oil pump which is located in the lower portion of the crankshaft extends into the oil sump of the compressor.
  • the oil pump comprises an axial aperture in the lower portion of the crankshaft which angles diagonally radially outwardly in an upward direction. Oil is pumped through this aperture into an annular chamber surrounding the crankshaft.
  • a passageway in the outboard bearing of the compressor communicates with this annular chamber and conducts the oil radially outwardly from the annulus and then upwardly against gravity under positive pressure into a pair of vertical oil channels which are located adjacent the vane and are open to both sides of the vane.
  • the positive pressure provided by the oil pump ensures that the oil channels are filled with oil at all times. Excess oil exits at the upper end of the vane through a relief in the main bearing and flows down around the cylinder by gravity and into the oil sump.
  • One advantage of the lubrication system of the present invention is that adequate quantities of lubricating oil are supplied at all times to the vane of the compressor.
  • Another advantage according to the present invention is that the lubricating oil is supplied to the sliding vane of the compressor under positive pressure so that the vane is properly lubricated regardless of the oil level in the sump.
  • Yet another advantage according to the present invention is the provision of a lubricating arrangement for the sliding vane of a rotary hermetic compressor wherein the oil forms a hydraulic seal around the vane of the compressor.
  • Still another advantage according to the present invention is the provision of lubricating passages which are filled adjacent the sliding vane of a compressor so that a sufficient quantity of oil is available for lubricating the vane at the point of heaviest load at all times.
  • a further advantage of the structure according to the present invention is that frictional losses in the compressor are kept to a minimum by means of proper lubrication and the efficiency is improved.
  • a yet further advantage according to the structure of the present invention is that a minimum amount of heat due to frictional losses is generated, heat transfer is minimized and the compressor efficiency is improved.
  • the invention comprises, in accordance with one form thereof, a rotary compressor including a crankshaft rotatably journalled in a bearing and a sliding vane, the vane having at least two sliding surfaces.
  • a lubricating means is provided for lubricating the vane and comprises an oil sump located in a lower portion of the housing, and an oil pumping means communicating with the sump for pumping oil upwardly from the sump.
  • the invention comprises a rotary compressor having a rotor including a shaft rotatably journalled in a bearing and a compressor cylinder coaxial with the bearing.
  • the cylinder has a vane slot in the cylindrical wall thereof and a vane having at least two sliding surfaces is slidably received in the slot.
  • Lubrication means for supplying lubricating oil to the vane comprises an oil sump in the bottom of the housing, oil pump means in the crankshaft for pumping oil upwardly and an oil passageway in the bearing.
  • the passageway conducts oil radially outwardly from the crankshaft pump means under positive pressure to vane lubrication means located in the cylinder for lubricating both sliding surfaces of the vane.
  • the invention further provides, in accordance with one form thereof, a hermetic rotary compressor for compressing refrigerant including a housing, an electric motor for driving the compressor and a crankshaft driven by a motor.
  • the crankshaft is journalled in first and second bearings and a cylinder is located intermediate to bearings and is coaxial therewith.
  • a vane slot is located in the wall of the cylinder and the vane is slidably received in the slot.
  • An oil lubrication means for lubricating the vane comprises an oil sump located in the housing and an oil pump means in the crankshaft for pumping oil upwardly from the sump.
  • the pump means comprises an axial aperture in the crankshaft the aperture extending axially upwardly and diagonally outwardly from the crankshaft axis.
  • the upper portion of the axial aperture communicates with the radial passage in the crankshaft for conducting oil to an annular chamber surrounding the crankshaft.
  • a passageway in the first bearing conducts oil from the annular chamber to the vane under positive pressure.
  • At least one oil channel extends through the cylinder, the axis of the channel being parallel to the crankshaft axis and the channel communicating with both the slot and the first bearing passageway.
  • Still another object of the present invention is to provide an oil lubricating system for a hermetic rotary compressor wherein the vane lubricant forms a hydraulic seal for the vane whereby leakage of refrigerant is reduced.
  • a compressor having a housing generally designated at 10.
  • the housing has a top portion 12, a lower portion 16 and a central portion 14.
  • the three housing portions are hermetically secured together as by welding or brazing.
  • a flange 18 is welded to the bottom of housing 10 for mounting the compressor.
  • a motor Located inside the hermetically sealed housing is a motor generally designated at 20 having a stator 22 and a rotor 24.
  • the stator is provided with windings 23.
  • the stator is secured to the housing 10 by an interference fit such as by shrink fitting.
  • the rotor 24 has a central aperture 25 provided therein into which is secured a crankshaft 26 by an interference fit.
  • a terminal cluster 28 is provided on the top portion 12 of the compressor for connecting the compressor to a source of electric power.
  • a refrigerant discharge tube 30 extends through top portion 12 of the housing and has an end 32 thereof extending into the interior of the compressor as shown.
  • the tube is sealingly connected to housing 10 at 31 as by soldering.
  • a suction tube 34 extends into the interior of compressor housing 10 and is sealed thereto as further described hereinbelow.
  • the outer end 36 of suction tube 34 is connected to accumulator 38 which has support plates 40 disposed therein for supporting a filtering mesh 42.
  • crankshaft 26 is provided with an eccentric portion 44 which revolves around the crankshaft axis as crankshaft 26 is rotatably driven by rotor 24.
  • a counterweight is provided to balance eccentric 44 and is secured to the end ring 47 of rotor 24 by rivetting.
  • Crankshaft 26 is journalled in a main bearing 46 having a cylindrical journal portion 48 and a generally flat planar mounting portion 50. Planar portion 50 is secured to housing 10 at three points 52 such as by welding of flanges 54 to the housing as best illustrated in Figure 2.
  • a second bearing or journal 56 is also shown disposed in the lower part of housing 10. As best illustrated in Figure 3 and 4, lower bearing 56 is provided with a journalling portion 58 having aperture 59 therein and a generally planar portion 60. Crankshaft 26 has a lower portion 62 journalled in journalling portion 58 of outboard bearing 56 as illustrated in Figure 1.
  • a compressor cylinder 66 Located intermediate main bearing 46 and outboard bearing 56 is a compressor cylinder 66.
  • Compressor cylinder 66, outboard bearing 56 and main bearing 46 are secured together by means of six bolts 68, one of which is indicated in Figure 1.
  • Bolts 68 extend through holes 70 in main bearing 46, holes 72 in cylinder 66 and into threaded holes 74 in lower bearing 56. if the cylinder axial dimension is sufficiently large the six bolts 68 could be replaced with twelve bolts, six of which would secure outboard bearing 56 to cylinder 66 and be threaded into cylinder 66.
  • a discharge muffler 76 is also secured to main bearing 46 by bolts 68 as indicated in Fig. 1.
  • Compressed refrigerant gas is discharged through relief 64 into discharge space 78 defined by discharge muffler 76 and the top surface of planar bearing portion 50. From space 78 the refrigerant will exit into housing 10 through three openings 80 in muffler 76, one of which is indicated in Figure 1.
  • cylinder 66 has a vane slot 82 provided in the cylindrical wall thereof into which is received a sliding vane 84.
  • Roller 86 is provided which surrounds eccentric portion 44 of crankshaft 26 and revolves around the axis of crankshaft 26 and is driven by eccentric 44.
  • Tip 88 of sliding vane 84 is in continuous engagement with roller 86 as vane 84 is urged against the roller by spring 89 received in spring pocket 90.
  • Figure 2 it can be seen that, in operation, as the roller 86 revolves around bore 92, the compression volume enclosed by roller 86, bore 92.and sliding vane 84 will decrease in size as roller 86 revolves clockwise around bore 92.
  • Refrigerant contained in that volume will therefore be compressed and after compression will exit through relief 64 in the cylinder as explained hereinabove.
  • a discharge valve (not shown) located in main bearing 46 discharges refrigerant into discharge volume 78 defined by discharge muffler 76 and planar portion 50 of main bearing 46.
  • the compressed refrigerant will exit from discharge muffler 76 through three discharge openings 80 in muffler 76 into sealed housing 10 of the compressor.
  • the refrigerant is discharged directly into motor windings 23 whereby the windings will be cooled.
  • Suction tube 34 extends into housing 10 and is sealed thereto as best illustrated in Figure 1.
  • Suction tube 34 has a portion 100 extending into an aperture 102 in the wall of cylinder 66.
  • Aperture 102 extends completely through the cylinder wall and communicates with bore 92 as best shown in Fig. 2.
  • Tube 34 is sealed to aperture 102 by means of an O-ring 104 housed in an annular recess 106 of the cylinder wall of cylinder 66.
  • a cylindrical soldering flange 108 secures tube 34 to housing 10 and conducts heat away from the tube 34 as it is being soldered to the housing.
  • Portion 110 extends away from tube 34 and is spaced from tube 34 by a space 112 extending between portion 110 and tube 34. Portion 110 conducts heat away from tube 34 and into housing 10.
  • crankshaft 26 is provided with an axial aperture 114 which extends completely through the upper portion of the crankshaft as shown.
  • An aperture 116 extends the entire length of the lower portion 117 of the crankshaft 26 as shown and communicates with aperture 114.
  • the extreme lower end 62 of crankshaft 26, which is journalled in outboard bearing 56 extends into oil sump 120 located in housing lower shell portion 16. It should be noted that aperture 116 diverges radially outwardly of the crankshaft axis in the upward direction so that it angles diagonally upwardly and its upper portion is spaced radially further outwardly from the crankshaft axis than its lower portion.
  • a radial passageway 122 includes an outer opening 124 which extends into an annular space 126 surrounding crankshaft 26. Annulus 126 surrounding crankshaft 26 provides a chamber together with relief 127 in outboard bearing 56 for the oil to flow into under positive pressure from the pumping aperture 116. The oil will flow outwardly under positive pressure from annular chamber 126 through passageway 128 as best illustrated in Figure 4. Passageway 128 extends radially outwardly in outboard bearing 56 and conducts oil to an upwardly extending passageway 130. Passageway 130 has a relief 132 formed therein which abuts cylinder 66.
  • passageway 130 conducts oil under positive pressure upwardly into a pair of grooves or channels 134 formed on either side of vane slot 82 in the wall of cylinder 66.
  • Channels 134 are located closer to bore 92 than to the outside wall 135 of cylinder 66. Oil will be supplied at positive pressure to oil channels 134 and will fill those channels completely at all times thereby allowing vane 84 to be well lubricated.
  • Channels 134 are adjacent to and have one side completely open to slot 82.
  • the column of oil in channels 134 surrounding the vane will prevent refrigerant gas under discharge pressure to escape from the sealed housing enclosure through vane slot 82 since the oil in channels 134 forms a hydraulic seal in combination with the vane 84.
  • FIG. 7 an enlarged broken-. away sectional view of one of the oil channels as viewed from line 7-7 in Figure 2 can be seen.
  • oil channels 134 in the cylinder wall of cylinder 36 are semicircular as best shown in Figures 2 and 7.
  • the channels or grooves 134 are located adjacent slots 82 and are open to the slot on one side along their entire axis. Oil can therefore freely contact both sides of vane 84.
  • Figure 7 also shows spring pocket 90 and planar portion 60 of lower bearing 56 which has a passageway 128 therein from which oil flows into upwardly extending passageway 130.
  • Oil channels 134 are substantially perpendicular to the direction of movement of vane 82. From relief 138 the oil will flow outwardly and drip downwardly around the cylinder and the lower bearing 56 back into the sump 120.
  • a rotary hermetic compressor wherein oil is pumped from an oil sump and conducted by positive pressure through a radial passageway in the outboard bearing and upwardly axially into a pair of oil channels formed adjacent the vane slot.
  • the oil channels will be continuously filled with oil under the positive pressure from the pumping mechanism, thereby providing proper lubrication of the vane as well as hydraulic sealing to prevent refrigerant gas from leaking past the vane.
  • By properly lubricating the vane its surface temperature will be minized.
  • the combination of proper lubrication under positive pressure and hydraulic sealing increases the efficiency of the compressor because of a reduction in leakage and the reduction in the heat exchange which takes place in the compressor.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Compressor (AREA)
EP19850111798 1984-11-13 1985-09-18 Rotary compressor lubrication arrangement Expired EP0182993B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US67030784A 1984-11-13 1984-11-13
US670307 1984-11-13

Publications (2)

Publication Number Publication Date
EP0182993A1 EP0182993A1 (en) 1986-06-04
EP0182993B1 true EP0182993B1 (en) 1989-05-24

Family

ID=24689885

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19850111798 Expired EP0182993B1 (en) 1984-11-13 1985-09-18 Rotary compressor lubrication arrangement

Country Status (10)

Country Link
EP (1) EP0182993B1 (zh)
JP (1) JPS61123792A (zh)
CN (1) CN1003319B (zh)
AU (1) AU582395B2 (zh)
BR (1) BR8505077A (zh)
CA (1) CA1274494A (zh)
DE (1) DE3570488D1 (zh)
DK (1) DK519685A (zh)
MX (1) MX162615A (zh)
PH (1) PH22163A (zh)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AU2014316483B2 (en) * 2013-09-06 2017-02-16 Fujitsu General Limited Rotary compressor

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7223082B2 (en) * 2003-03-25 2007-05-29 Sanyo Electric Co., Ltd. Rotary compressor
JP2009215929A (ja) * 2008-03-10 2009-09-24 Panasonic Corp 密閉型圧縮機
CN101839241B (zh) * 2009-03-20 2013-12-25 上海日立电器有限公司 一种两级滚动转子式压缩机
CN101737330B (zh) * 2010-02-10 2013-01-02 河北省电力公司电力科学研究院 滚动活塞压缩机或发动机密封结构
CN104373354B (zh) * 2014-11-05 2017-12-08 合肥凌达压缩机有限公司 滑片压缩机及其下法兰
CN104696227B (zh) * 2015-03-02 2017-11-10 广东美芝制冷设备有限公司 旋转式压缩机
CN105952643B (zh) * 2016-06-15 2018-02-27 珠海格力节能环保制冷技术研究中心有限公司 压缩机及具有其的空调器
WO2021079401A1 (ja) * 2019-10-21 2021-04-29 日立ジョンソンコントロールズ空調株式会社 ロータリ圧縮機
WO2022085443A1 (ja) * 2020-10-22 2022-04-28 東芝キヤリア株式会社 圧縮機、および冷凍サイクル装置
CN114776560A (zh) * 2022-05-06 2022-07-22 广东美芝制冷设备有限公司 应用于压缩机的泵体以及压缩机

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US2107630A (en) * 1932-09-21 1938-02-08 Nash Kelvinator Corp Refrigerating apparatus
US2072307A (en) * 1934-05-14 1937-03-02 Reconstruction Finance Corp Compressor
GB447318A (en) * 1934-06-14 1936-05-15 British Thomson Houston Co Ltd Improvements in and relating to refrigerating machines
US2212717A (en) * 1936-03-31 1940-08-27 Gen Motors Corp Rotary compressor for refrigerating apparatus
US2246276A (en) * 1938-01-20 1941-06-17 Davidson William Ward Pump
US2883101A (en) * 1956-04-16 1959-04-21 Gen Electric Rotary compressor
US3513476A (en) * 1967-06-21 1970-05-19 Tokyo Shibaura Electric Co Rotary compressors
US3565552A (en) * 1968-03-19 1971-02-23 Tokyo Shibaura Electric Co Rotary compressor
US3499600A (en) * 1968-03-21 1970-03-10 Whirlpool Co Rotary compressor
JPS5613575B2 (zh) * 1972-09-11 1981-03-30
US4091638A (en) * 1976-12-13 1978-05-30 Borg-Warner Corporation Cooling system for hermetic compressor
JPS5613575U (zh) * 1979-07-09 1981-02-05

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AU2014316483B2 (en) * 2013-09-06 2017-02-16 Fujitsu General Limited Rotary compressor

Also Published As

Publication number Publication date
PH22163A (en) 1988-06-01
EP0182993A1 (en) 1986-06-04
AU4914385A (en) 1986-05-22
AU582395B2 (en) 1989-03-23
MX162615A (es) 1991-06-03
JPS61123792A (ja) 1986-06-11
JPH0219316B2 (zh) 1990-05-01
DK519685D0 (da) 1985-11-12
CN85106952A (zh) 1986-07-23
CN1003319B (zh) 1989-02-15
DE3570488D1 (en) 1989-06-29
BR8505077A (pt) 1986-07-29
CA1274494A (en) 1990-09-25
DK519685A (da) 1986-05-14

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