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WO2010010998A2 - Compresseur - Google Patents

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Publication number
WO2010010998A2
WO2010010998A2 PCT/KR2008/007015 KR2008007015W WO2010010998A2 WO 2010010998 A2 WO2010010998 A2 WO 2010010998A2 KR 2008007015 W KR2008007015 W KR 2008007015W WO 2010010998 A2 WO2010010998 A2 WO 2010010998A2
Authority
WO
WIPO (PCT)
Prior art keywords
oil
rotation
axis
roller
refrigerant
Prior art date
Application number
PCT/KR2008/007015
Other languages
English (en)
Other versions
WO2010010998A3 (fr
Inventor
Kangwook Lee
Jin-Ung Shin
Yongchol Kwon
Geun-Hyoung Lee
Original Assignee
Lg Electronics, Inc.
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
Priority claimed from KR1020080112746A external-priority patent/KR101467577B1/ko
Application filed by Lg Electronics, Inc. filed Critical Lg Electronics, Inc.
Priority to CN200880130055.7A priority Critical patent/CN102076966B/zh
Priority to US13/054,981 priority patent/US9097254B2/en
Publication of WO2010010998A2 publication Critical patent/WO2010010998A2/fr
Publication of WO2010010998A3 publication Critical patent/WO2010010998A3/fr

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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
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
    • F04C18/3562—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation
    • F04C18/3564—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the working space, being surfaces of revolution
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/02—Arrangements of bearings
    • 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
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/344—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • F04C18/3441—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation
    • F04C18/3443—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation with a separation element located between the inlet and outlet opening
    • 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
    • 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
    • F04C29/025—Lubrication; Lubricant separation using a lubricant pump
    • 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
    • F04C29/028—Means for improving or restricting lubricant flow
    • 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
    • F04C2240/00—Components
    • F04C2240/60—Shafts
    • F04C2240/603—Shafts with internal channels for fluid distribution, e.g. hollow shaft

Definitions

  • the present invention relates in general to a compressor, and more particularly, to a compressor which eliminates sliding contacts between a cylinder and a roller to minimize the mixing of lubricating oil into refrigerant, and is structured to be able to evenly distributing lubricating oil over sliding contact portions of a compressor actuator by pumping the oil from the inside on an axis of rotation.
  • the present invention relates to a compressor having a structure to accommodate a refrigerant passage separately from an oil feed passage such that the mixing of oil into refrigerant is minimized and the operational reliability is enhanced.
  • a compressor is a mechanical apparatus that receives power from a power generation apparatus such as an electric motor, a turbine or the like and compresses air, refrigerant or various operation gases to raise a pressure.
  • the compressor has been widely used in electric home appliances such as a refrigerator and an air conditioner, or in the whole industry.
  • the compressors are roughly classified into a reciprocating compressor wherein a compression chamber to/from which an operation gas is sucked and discharged is defined between a piston and a cylinder and refrigerant is compressed as the piston linearly reciprocates inside the cylinder, a rotary compressor which compresses an operation gas in a compression chamber defined between an eccentrically-rotated roller and a cylinder, and a scroll compressor wherein a compression chamber to/from which an operation gas is sucked and discharged is defined between an orbiting scroll and a fixed scroll and refrigerant is compressed as the orbiting scroll rotates along the fixed scroll.
  • the reciprocating compressor is excellent in mechanical efficiency, its reciprocating motion causes serious vibrations and noise problems. Because of this problem, the rotary compressor has been developed as it has a compact size and demonstrates excellent vibration properties.
  • the rotary compressor is configured in a manner that a motor and a compression mechanism part are mounted on a drive shaft in a hermetic container, a roller fitted around an eccentric portion of the drive shaft is positioned inside a cylinder that has a cylinder shape compression chamber therein, and at least one vane is extended between the roller and the compression chamber to divide the compression chamber into a suction region and a compression region, with the roller being eccentrically positioned in the compression chamber.
  • vanes are supported by springs in a recess of the cylinder to pressurize surface of the roller, and the vane(s) as noted above divide(s) the compression chamber into a suction region and a compression region.
  • vanes are supported by springs in a recess of the cylinder to pressurize surface of the roller, and the vane(s), as noted above, divide(s) the compression chamber into a suction region and a compression region.
  • the suction region expands gradually with the rotation of the drive shaft to suck refrigerant or a working fluid into it, while the compression region shrinks gradually at the same time to compress refrigerant or a working fluid in it.
  • No. 7,344,367 discloses a rotary compressor having a compression chamber positioned between a rotor and a roller rotatably mounted on a stationary shaft.
  • the stationary shaft extends longitudinally inwardly within a housing and a motor includes a stator and a rotor, with the rotor being rotatably mounted on the stationary shaft within the housing the roller being rotatably mounted on an eccentric portion that is integrally formed with the stationary shaft.
  • a vane is interposed between the rotor and the roller to let the roller rotate along with the rotation of the roller, such that a working fluid can be compressed within the compression chamber.
  • the stationary shaft still makes a sliding contact with an interior surface of the roller so a high relative velocity is created between them and the patent still shares the problems found in the conventional rotary compressor.
  • WO2008/004983 discloses another type of rotary compressors, comprising: a cylinder, a rotor mounted in the cylinder to rotate eccentrically with respect to the cylinder, and a vane positioned within a slot which is arranged at the rotor, the vane sliding against the rotor, wherein the vane is connected to the cylinder to transfer a force to the cylinder rotating along with the rotation of the rotor, and wherein a working fluid is compressed within a compression chamber defined between the cylinder and the rotor.
  • these rotary compressors require a separate electric motor for driving the rotor because the rotor rotates by a drive force transferred through the drive shaft.
  • rotary compressors require lubrication to reduce frictional force and frictional heat between members that make a sliding contact while rotating.
  • the roller and the cylinder are typical members making a sliding contact so an interior of the compression chamber had to be lubricated, and this made it unavoidable the mixing of refrigerant and lubricating oil.
  • an accumulator had to be installed additionally to separate the refrigerant from the lubricating oil, which required extra large compressors and became the leading cause of manufacturing cost.
  • the present invention is conceived to solve the aforementioned problems in the prior art.
  • An object of the present invention is to provide a compressor
  • Another object of the present invention is to provide a compressor having a structure of high oil recovery and enhanced operational reliability by minimizing the mixing of oil into refrigerant.
  • An aspect of the present invention provides a compressor, comprising: a hermetic container storing oil at a lower portion; a stator mounted within the hermetic container; a cylinder type rotor rotating within the stator by a rotating electromagnetic field from the stator, with the rotor defining a compression chamber inside; a roller rotating within the compression chamber of the cylinder type rotor by a rotational force transferred from the rotor, with the roller compressing refrigerant during rotation; an axis of rotation integrally formed with the roller and extending in an axial direction; a vane dividing the compression chamber into a suction region where refrigerant is sucked in and a compression region where the refrigerant is compressed/discharged from, with the vane transferring the rotational force from the cylinder type rotor to the roller; and oil feed passages provided to the axis of rotation and the roller, with the oil feed passage feeding oil that is pumped along the motion of the axis of rotation to an area where two or more
  • the compressor of in accordance with the first embodiment of the present invention further comprises: first and second covers joined to the cylinder type rotor in the axial direction, with the covers defining the compression chamber therebetween and receiving the axis of rotation therethrough; and first and second bearings joined to the first and second covers for rotatably supporting the axis of rotation, the roller, and the first and second covers onto the hermetic container.
  • the oil feed passage comprises an oil feeder formed within the axis of rotation that is protruded from one side of the roller in the axis direction, and a first oil feed hole radially passing through one portion of the axis of rotation that is contiguous with the roller to be in communication with the oil feeder.
  • the oil feed passage further comprises first oil storage cavities formed in the axis of rotation having the first oil feed hole and in one axial side of the roller, with the roller being connected to the axis of rotation, so as to temporarily collect oil supplied through the first oil feed hole.
  • the first oil storage cavities are formed to lubricate a bearing in contact with an outer circumferential surface of the axis of rotation and with one axial side of the second rotating member.
  • the oil feed passage further comprises a second oil feed hole axially passing through the second rotating member to be in communication with the first oil storage cavities, and second oil storage cavities formed in the other axial side of the second rotating member having the second oil feed hole and in the axis of rotation connected thereto so as to temporarily collect oil supplied through the second feed hole.
  • the second oil storage cavities are formed to lubricate a bearing in contact with the axis of rotation and the other axial side of the roller.
  • the oil feed passage further comprises oil feed cavities provided to the roller and the vane so as to communicate with at least one of the first and second oil storage cavities.
  • the oil feed passage is mounted with an oil feed member for pumping oil up to an oil feeder, with the oil feed member being twisted in a spiral shape.
  • the oil feeder feeds oil through the oil feed passage by a capillary phenomenon.
  • the oil feeder has a groove in an inner circumferential thereof, and an oil feed member is press fitted therein except for the groove.
  • the oil feed member having a groove in an outer circumferential surface is press fitted into the oil feeder.
  • a compressor in accordance with the second embodiment of the present invention further comprises a shaft cover and a main cover joined to the cylinder type roller and the roller in the axial direction for defining a compression chamber therebetween, with the shaft cover covering the axis of rotation, with the main cover receiving the axis of rotation; a mechanical seal axially joined to the shaft cover and rotatably supporting the shaft cover onto the hermetic container; and a bearing axially joined to the main cover and rotatably supporting the main cover, the axis of rotation and the roller onto the hermetic container.
  • the oil feed passage comprises an oil feeder formed within the axis of rotation in the axis direction, and a first oil feed hole radially passing through one portion of the axis of rotation that is contiguous with the roller to be in communication with the oil feeder.
  • the oil feed passage further comprises first oil storage cavities formed in the axis of rotation having the first oil feed hole and in one axial side of the roller, with the roller being connected to the axis of rotation, so as to temporarily collect oil supplied through the first oil feed hole.
  • the first oil storage cavities are formed to lubricate a bearing in contact with an outer circumferential surface of the axis of rotation and with one axial side of the second rotating member.
  • the oil feed passage further comprises a second oil feed hole axially passing through the second rotating member to be in communication with the first oil storage cavities, and second oil storage cavities formed in the other axial side of the roller having the second oil feed hole so as to temporarily collect oil supplied through the second feed hole.
  • the second oil storage cavities are formed to lubricate a bearing in contact with the axis of rotation and with the other axial side of the roller.
  • the shaft cover has cavities for storing oil which are formed on an opposite side of the second oil storage cavities.
  • the oil feed passage further comprises oil feed cavities provided to the roller and the vane so as to communicate with at least one of the first and second oil storage cavities.
  • the oil feed passage is mounted with an oil feed member for pumping oil up to an oil feeder, with the oil feed member being twisted in a spiral shape.
  • the oil feeder feeds oil through the oil feed passage by a capillary phenomenon.
  • the oil feeder has a groove in an inner circumferential thereof, and an oil feed member is press fitted therein except for the groove.
  • the oil feed member having a groove in an outer circumferential surface is press fitted into the oil feeder.
  • the compressor of the present invention comprises a refrigerant suction passage for sucking refrigerant into the compression chamber through the axis of rotation and the roller, with the refrigerant suction passage formed separately from an oil feed passage.
  • the compressor having the above configuration in accordance with the present invention arranges the refrigerant passage separately from the oil passage, so it can prevent the mixing of refrigerant and oil and further reduce a much refrigerant and oil leak, thereby guaranteeing an enhanced operational reliability. Moreover, since the roller and the cylinder rotate together with the cover, a sliding contact is noticeably reduced so there is no need to extend the oil feed passage into the interior of the cylinder. In result, nearly none of the oil is mixed with the refrigerant, and the operational reliability as well as the endurance of drive members can be maximized.
  • the operational reliability of the compressor is also enhanced by providing a compressor with an efficient lubrication structure to evenly distribute lubricating oil over contact portions.
  • FIG. 1 is a transverse cross-sectional view showing a compressor in accordance with a first embodiment of the present invention
  • FIG. 2 is an exploded perspective view showing one example of an electromotive part of the compressor in accordance with the first embodiment of the present invention
  • FIGS. 3 and 4 each illustrate an exploded perspective view showing one example of the compression mechanism part of the compressor in accordance with the first embodiment of the present invention
  • FIG. 5 is a plan view showing a vane mount structure adopted to a compressor in accordance with the present invention, and a running cycle of the compressor;
  • FIG. 6 is an exploded perspective view showing one example of a support member of the compressor in accordance with the first embodiment of the present invention
  • FIGS. 7 through 9 each illustrate a transverse cross-sectional view showing a rotation centerline of the compressor in accordance with the first embodiment of the present invention
  • FIG. 10 is an exploded perspective view showing the compressor in accordance with the first embodiment of the present invention
  • FIG. 11 is a transverse cross-sectional view showing how refrigerant and oil flow in the compressor in accordance with the first embodiment of the present invention
  • FIGS. 7 through 9 each illustrate a transverse cross-sectional view showing a rotation centerline of the compressor in accordance with the first embodiment of the present invention
  • FIG. 10 is an exploded perspective view showing the compressor in accordance with the first embodiment of the present invention
  • FIG. 11 is a transverse cross-sectional view showing how refrigerant and oil flow in the compressor in accordance with the first embodiment of the present invention
  • FIG. 12 and 13 each illustrate a perspective view showing an example of the assembled structure of a roller and an oil feeder of the compressor in accordance with the first embodiment of the present invention
  • FIG. 14 is a perspective view of the roller with an oil feed structure for a vane and bushes of the compressor in accordance with the first embodiment of the present invention
  • FIG. 15 is a transverse cross-sectional view showing a first bearing of the compressor in accordance with the first embodiment of the present invention
  • FIG. 16 is a transverse cross-sectional view showing a compressor in accordance with a second embodiment of the present invention
  • FIG. 17 is an exploded perspective view showing the compressor in accordance with the second embodiment of the present invention
  • FIG. 18 through 20 each illustrate a transverse cross-sectional view showing a rotation centerline of the compressor in accordance with the second embodiment of the present invention
  • FIG. 21 is a transverse cross-sectional view showing how refrigerant and oil flow in the compressor in accordance with the second embodiment of the present invention
  • FIGS. 22 and 23 each illustrate a perspective view showing an example of the assembled structure of a roller and an oil feeder of the compressor in accordance with the second embodiment of the present invention
  • FIG. 24 is a perspective view of the roller with an oil feed structure for a vane and bushes of the compressor in accordance with the second embodiment of the present invention.
  • FIG. 1 is a transverse cross-sectional view showing a compressor in accordance with the present invention
  • FIG. 2 is an exploded perspective view showing one example of an electric motor of the compressor in accordance with the present invention
  • FIGS. 3 and 4 each illustrate an exploded perspective view showing one example of a compression mechanism part of the compressor in accordance with the present invention.
  • a compressor in accordance with a first embodiments of the present invention includes a hermetic container 110, a stator 120 installed within the hermetic container 110, a first rotating member 130 installed within the stator 120 and rotating by a rotating electromagnetic field from the stator 120, a second rotating member 140 rotating within the first rotating member 130 by a rotational force transferred from the first rotating member 130 for compressing refrigerant therebetween, and first and second bearings 150 and 160 supporting the first and second rotating members 130 and 140 to be able to rotate within the hermetic container 110.
  • An electromotive mechanism part which provides power through an electrical reaction employs, for example, a BLDC motor including the stator 120 and the first rotating member 130, and a compression mechanism part which compresses refrigerant through a mechanical reaction includes the first and second rotating members 130 and 140, and the first and second bearings 150 and 160. Therefore, by installing the electromotive mechanism part and the compression mechanism part in a radial direction, the total height of the compressor can be reduced.
  • the hermetic container 110 is composed of a cylinder-shaped body 111, and upper/lower shells 112 and 113 coupled to the top/bottom of the body 111 and stores oil at a suitable height to lubricate or smooth the first and second rotating members 130 and 140 (see FIG. 1).
  • the upper shell 113 includes a suction tube 114 at a predetermined position for sucking refrigerant and a discharge tube 115 at another predetermined position for discharging refrigerant.
  • a compressor is a high-pressure type compressor or a low-pressure type compressor is determined depending on whether the interior of the hermetic container 110 is filled with compressed refrigerants or pre-compressed refrigerants, and the position of the suction tube 114 and discharge tube 115 should be determined based on that.
  • this embodiment of the present invention introduces a low pressure compressor.
  • the suction tube 114 is connected to the hermetic container 110 and the discharge tube 115 is connected to the compression mechanism part.
  • the stator 120 is composed of a core 121, and a coil 122 primarily wound around the core 121. While a core used for a conventional BLDC motor has 9 slots along the circumference, the core 121 of a BLDC motor has 12 slots along the circumference because the stator in a preferred embodiment of the present invention has a relatively a large diameter. Considering that a coil winding number increases with an increasing number of core slots, in order to generate an electromagnetic force of the conventional stator 120, the core 121 may have a smaller height.
  • the first rotating member 130 is composed of a rotor 131, a cylinder 132, a first cover 133 and a second cover 134.
  • the rotor 131 has a cylindrical shape, with the rotor 131 rotating within the stator 120 (see FIG. 1) by a rotating electromagnetic field generated from the stator 120 (see FIG. 1), and inserted therethrough are plural permanent magnets 131a in an axial direction to generate a rotating magnetic field.
  • the cylinder 132 Similar to the rotor 131, the cylinder 132 also takes the form of a cylinder to create a compression chamber P (see FIG. 1) inside.
  • the rotor 131 and the cylinder 132 can be manufactured separately and joined together later.
  • a pair of mount protrusions 132a is arranged at the outer circumferential surface of the cylinder 132, and grooves 13 Ih having a corresponding shape to the mount protrusions 132a of the cylinder 132 are formed in the inner circumferential surface of the rotor 131 such that the outer circumferential surface of the cylinder 132 is engaged with the inner circumferential surface of the rotor 131.
  • the rotor 131 is integrally formed with the cylinder 132, with the permanent magnets 131a mounted in holes that are additionally formed in the axial direction.
  • the first cover 133 and the second cover 134 are coupled to the rotor 131 and/or the cylinder 132 in the axial direction, and the compression chamber P (see FIG. 1) is defined between the cylinder 132 and the first and second covers 133 and 134.
  • the first cover 133 has a planar shape and is provided with a discharge port 133a through which a compressed refrigerant from the compression chamber P (see FIG. 1) exits and a discharge valve (not shown) mounted thereon.
  • the second cover 134 is composed of a planar shape cover 134a, and a downwardly projecting hollow shaft 134b at the center.
  • the shaft 134b is not absolutely required, but its role in receiving a load acting thereon increases a contact area with the second bearing 160 (see FIG.
  • the second rotating member 140 is composed of an axis of rotation 141, a roller 142, and a vane 143.
  • the axis of rotation 141 is extended in the roller axis direction from both surfaces of the roller 142, with the axis being projected further from the bottom surface of the roller 142 than from the top surface of the roller 142 to provide stable support under any load.
  • the axis of rotation 141 is in tegrally formed with the roller 142, but even if they have been manufactured separately, they must join together to be able to rotate as one unit.
  • the axis of rotation 141 takes the form of a hollow shaft with a blocked center portion, it is better to arrange a suction passage 141a through which refrigerant is sucked in and a passage of an oil feeder 141b (see FIG. 1) separately from each other so as to minimize the mixing of oil and refrigerant.
  • the oil feeder 141b (see FIG. 1) of the axis of rotation 141 is provided with a helical member to assist oil ascending by a rotational force, or a groove to assist oil ascending by a capillary action.
  • the axis of rotation 141 and the roller 142 each have all kinds of oil feed holes (not shown) and oil storage cavities (not shown) for supplying oil from the oil feeder 141b (see FIG. 1) into between two or more members subject to sliding interactions.
  • the roller 142 has suction passages 142a radially penetrating it for the communication of the suction passage 141a of the axis of rotation 141 with the compression chamber P (see FIG. 1), such that refrigerant is sucked into the compression chamber P (see FIG. 1) through the suction passage 141a of the axis of rotation 141 and the suction passage 142a of the roller 142.
  • the vane 143 is formed on the outer circumference surface of the roller 142, with the vane 143 being disposed to extend radially and rotate at a preset angle while making a linear reciprocating motion, along bushes 144, within a vane mount slot 132h (see FIG. 5) of the first rotating member 130 (see FIG. 1). As shown in FIG. 5, a couple of bushes 144 limits the circumferential rotation of the vane 143 to below a preset angle and guides the vane 143 to make the linear reciprocating motion throigh a space defined between the couple of bushes 144 that are mounted within the vane mount slot 132h (see FIG. 5).
  • the bushes 144 can be manufactured in use of a suitable material sold under the trademark of Vespel SP-21.
  • Vespel SP-21 is a polymer material which combines excellent wear resistance, heat resistance, natural lubricity, flame resistance, and electrical insulation.
  • FIG. 5 is a plan view showing a vane mount structure and a running cycle of the compression mechanism part in a compressor according to the present invention.
  • a vane mount slot 132h is formed axially and longitudinally in the inner peripheral surface of the cylinder 132, and a couple of bushes 144 fit into the vane mount slot 132h, and the vane 143 integrally formed with the axis of rotation 141 and the roller 142 is inserted between the bushes 144.
  • the cylinder 132 and the roller 142 define the compression chamber P (see FIG. 1) between them, with the compression chamber P (see FIG. 1) being divided by the vane 143 into a suction region S and a discharge region D.
  • the suction passages 142a see FIG.
  • the vane 143 which is integrally manufactured with the roller 142 in the present invention compressor and assembled to slidably movable between the bushes 144 can reduce frictional loss caused by the sliding contact and lower a refrigerant leak between the suction region S and the discharge region D more than a spring-supported vane which is manufactured separately from the roller or the cylinder in a conventional rotary compressor.
  • FIG. 5a shows a step of sucking refrigerant or a working fluid into the suction region S. For instance, a working fluid is being sucked in and immediately compressed in the discharge D.
  • the first and second rotating members 120 and 140 are arranged as shown in FIG. 5b, the working fluid is continuously sucked into the suction region S and compression proceeds accordingly.
  • the first and second rotating members 120 and 140 are arranged as shown in FIG. 5c, the working fluid is continuously sucked in, and the refrigerant or the working fluid of a preset pressure or higher in the discharge region D is discharged through the discharge incline portion (or discharge port) 136.
  • the first and second rotating members 120 and 140 are arranged as shown in FIG. 5d, the compression and discharge of the working fluid are finished. In this way, one cycle of the compression mechanism part is completed.
  • FIG. 6 is an exploded perspective view showing an example of a support member of the compressor in accordance with the present invention.
  • the first and second rotating members 130 and 140 described earlier are rotatably supported on the inside of the hermetic container 110 by the first and second bearings 150 and 160 that are coupled in the axial direction.
  • the first bearing 150 can be secured with a fixing rib or a fixing protrusion projected from the upper shell 112, and the second bearing 160 can be bolt-fastened to the lower shell 113.
  • the first bearing 150 is constructed to adopt a journal bearing for rotatably supporting the outer peripheral surface of the axis of rotation 141 and the inner peripheral surface of the first cover 133, and a trust bearing for rotatably supporting the upper surface of the first cover 133.
  • the first bearing 150 includes a suction guide passage 151 communicated with a suction passage 141a of the axis of rotation 141.
  • the suction guide passage 151 is opened in communication with the interior of the hermetic container 110 to let the refrigerant having been sucked in through the suction tube 114 enter the hermetic container 110.
  • the first bearing 150 includes a discharge guide passage 152 which is opened in communication with the discharge port 133a of the first cover 133, with the discharge port 133a taking the form of a ring or an annular ring to accommodate a revolving orbit of the discharge port 133a of the first cover 133 so as to discharge the refrigerant coming out throigh the discharge port 133a of the first cover 133 via the discharge tube 115 even if the discharge port 133a of the first cover 133 is revolving.
  • the discharge guide passage 152 includes a discharge tube mount hole 153 throigh which it can be connected directly to the discharge tube 115 for a direct discharge of the refrigerant outside.
  • the second bearing 160 is constructed to adopt a journal bearing for rotatably supporting the outer peripheral surface of the axis of rotation 141 and the inner peripheral surface of the second cover 134, and a trust bearing for rotatably supporting the lower surface of the roller 142 and the lower surface of the second cover 134.
  • the second bearing 160 is composed of a planar shape support 161 that is bolt-fastened to the lower shell 113, and a shaft 162 disposed at the center of the support 161, with the shaft having an upwardly protruded hollow 162a.
  • the center of the hollow 162a of the second bearing 160 is formed at a position eccentric from the center of the shaft 162 of the second bearing 160, with the center of the shaft 162 of the second bearing 160 being coUinear with the rotation centerline of the first rotating member 130, the center of the hollow 162a of the second bearing 160 being collinear with the axis of rotation 141 of the second rotating member 140. That is to say, althoigh the center line of the axis of rotation 141 of the second rotating member 140 can be formed eccentric with respect to the rotation center line of the first rotating member 130, it can also be formed concentrically along the longitudinal center line of the roller 142. More details are now provided below.
  • FIGS. 7 throigh 9 each illustrate a transverse cross-sectional view showing a rotation centerline of the compressor in accordance with the first embodiment of the present invention.
  • FIGS. 7 throigh 9 One example of relative positioning of the first and second rotating members 130 and 140 is illustrated in FIGS. 7 throigh 9.
  • 'a' indicates a centerline of the first axis of rotation of the first rotating member 130, or a longitudinal centerline of the shaft 134b of the second cover 134, or a longitudinal centerline of the shaft 162 of the bearing 160.
  • the first rotating member 130 includes the rotor 131, the cylinder 132, the first cover 133 and the second cover 134 as shown in FIG.
  • 'a' may be regarded as the rotation centerline of them
  • 'b' indicates a centerline of the second axis of rotation of the second rotating member 140 or a longitudinal centerline of the axis of the rotation 142
  • 'c' indicates a longitudinal centerline of the second rotating member 140 or a longitudinal centerline of the roller 142.
  • FIG. 7 shows that the centerline 'b' of the second axis of rotation is spaced apart a predetermined distance from the centerline 'a' of the first axis of rotation, and the longitudinal centerline 'c' of the second rotating member 140 is collinear with the centerline 'b' of the second axis of rotation.
  • the second rotating member 140 is disposed eccentric with respect to the first rotating member 130, and when the first and second rotating members 130 and 140 rotate together by the medium of the vane 143, they repeatedly contact, separate, and retouch per rotation as explained before, thereby varying the volume of the suction region S/the discharge region D so as to compress refrigerant within the compression chamber P.
  • FIG. 8 shows that the centerline 'b' of the second axis of rotation is spaced apart a predetermined distance from the centerline 'a' of the first axis of rotation, and the longitudinal centerline 'c' of the second rotating member 140 is spaced apart a predetermined distance from the centerline 'b' of the second axis of rotation, but the centerline 'a' of the first axis of rotation and the longitudinal centerline 'c' of the second rotating member 140 are not collinear.
  • the second rotating member 140 is disposed eccentric with respect to the first rotating member 130, and when the first and second rotating members 130 and 140 rotate together by the medium of the vane 143, they repeatedly contact, separate, and retouch per rotation as explained before, thereby varying the volume of the suction region S/the discharge region D so as to compress refrigerant within the compression chamber P. As such, a larger eccentric amount than that in FIG. 7 can be given.
  • FIG. 9 shows that the centerline 'b' of the second axis of rotation is collinear with the centerline 'a' of the first axis of rotation, and the longitudinal centerline 'c' of the second rotating member 140 is spaced apart a predetermined distance from the centerline 'a' of the first axis of rotation and from the centerline 'b' of the second axis of rotation.
  • the second rotating member 140 is disposed eccentric with respect to the first rotating member 130, and when the first and second rotating members 130 and 140 rotate together by the medium of the vane 143, they repeatedly contact, separate, and retouch per rotation as explained before, thereby varying the volume of the suction region S/the discharge region D so as to compress refrigerant within the compression chamber P.
  • FIG. 10 is an exploded perspective view showing a compressor in accordance with one embodiment of the present invention.
  • the rotor 131 and the cylinder 132 are either manufactured separately and then coupled, or manufactured in one unit from the beginning.
  • the axis of rotation 141, the roller 142 and the vane 143 can also be manufactured separately or integrally, but either way, they should be able to rotate as one unit.
  • the vane 143 is inserted between the bushes 144 within the cylinder 131.
  • the axis of rotation 141, the roller 142 and the vane 143 are mounted within the rotor 131 and the cylinder 132.
  • the first and second covers 133 and 134 are bolt-fastened in the axial direction of the rotor 131 and the cylinder 132, with the covers covering the roller 142 even if the axis of rotation 141 may pass therethrough.
  • the second bearing 160 is bolt-fastened to the lower shell 113, and the rotation assembly is then assembled to the second bearing 160, with the inner circumferential surface of the shaft 134a of the second cover 134 circumscribing the outer circumferential surface of the shaft 162, with the outer circumferential surface of the axis of rotation 141 being inscribed in the hollow 162a of the second bearing 160.
  • the stator 120 is press fitted into the body 111, and the body 111 is joined to the upper shell 112, with the stator 120 being positioned to maintain an air-gap with the outer circumferential surface of the rotation assembly.
  • the first bearing 150 is joined or assembled to the upper shell 112 in a way that the discharge tube 115 of the upper shell 112 is press fitted into the discharge mount hole 153 (see FIG. 6) of the first bearing.
  • the upper shell 122 assembled with the first bearing 150 is joined to the body 111, and the first bearing 150 which is fitted between the axis of rotation 141 and the first cover 133 is covered above by the shell 112 at the same time.
  • the suction guide passage 151 of the first bearing 150 is in communication with the suction passage 141a of the axis of rotation 141, and the discharge guide passage 152 of the first bearing 150 is in com- munication with the discharge port 133a of the first cover 133.
  • FIG. 11 is a transverse cross-sectional view showing how refrigerant and oil flow in a compressor in accordance with one embodiment of the present invention.
  • a rotational force of the first rotating member 130 is transferred to the second rotating member 140 so the second rotating member 140, i.e., the axis of rotation 141, the roller 142 and the vane 143, rotate together as one unit.
  • the first and second rotating members 130 and 140 are disposed eccentric with respect to each other, they repeatedly contact, separate, and retouch per rotation, thereby varying the volume of the suction region S/the discharge region D so as to compress refrigerant within the compression chamber P and to pump oil at the same time to lubricate between two slidingly contacting members.
  • FIGS. 12 and 13 each illustrate a perspective view showing an example of the assembled structure of the roller 142 and oil feed members 145a and 145b of the compressor in accordance with the first embodiment of the present invention.
  • the bottom of the hermetic container 110 is filled up with oil, and with one end of the axis of rotation 141 being dipped into the oil, the oil is pumped up along the interior of the axis of rotation 141.
  • the bottom of the axis of rotation 141 is a start point of the oil feed passage, adequateing a role of an oil pump.
  • an oil feed member 145a may be provided to the oil feeder 141b within the axis of rotation 141.
  • the oil fee member 145a may take the form of a helical shape to function as a centrifugal pump for example.
  • the helical oil feed member can be prepared by twisting a roughly rectangular board in a spiral form. In such case, the board may be twisted to the left or right to help the oil climb up along the face of the board according to the rotational direction of the axis of rotation 141.
  • the oil feed member may also take the form of a pillar shape with a helical groove formed in its outer circumferential surface, or a propeller shape. The helical oil feed member 145a rotates together with the axis of rotation 141 within the oil feeder 141b to pump up oil by the rotational force.
  • FIG. 13 shows yet another preferred embodiment of the oil feed member 145b, with the oil feeder 141b pumping up oil using a capillary phenomenon.
  • a pillar shape oil feed member 145b is press fitted into the oil feeder 141b within the axis of rotation 141, and plural grooves 145c with a diameter small enoigh for the capillary process to take place between the inner circumferential surface of the axis of rotation 141 and the oil feed member are formed.
  • the grooves 145c may be formed in the inner circumferential surface of the oil fee der 141b, or one side of the oil feed member 145b, or both sides.
  • an oil feed passage communicating with peripheral area and the roller 142 to evenly distribute the oil having been pumped up along the axis of rotation 141.
  • the oil feeder 141b has one end blocked to prevent the mixing of oil into the refrigerant in an area close to the roller 142 in the axial direction, and an oil feed hole 141c is drilled, passing through the axis of rotation 141 located contiguous with the roller 142.
  • the oil flowing out throigh the oil feed hole 141c is fed between the outer circumferential surface of the axis of rotation 141 and the second bearing 160, and between the roller 142 and the second cover 134, thereby forming a film of a uniform thickness for lubrication.
  • the second cover 134 has a collection cavity to collect the oil having been used for lubricating between the roller 142 and the contact surface to the bottom of the hermetic container 110.
  • an oil storage cavity 14 Id is formed between the axis of rotation 141 and the second bearing 160 to serve as a temporal reservoir of the oil flowing out from the oil feed hole 141c.
  • the roller 142 has an oil feed hole 142b that is drilled in the axial direction to be in communication with the oil storage cavity 141d.
  • the rotational friction of the axis of rotation 141 is lubricated through oil in the oil storage cavity 141e that is formed between the outer circumferential surface of the axis of rotation 141 and the first bearing 150 at the upper portion of the roller, and the oil is temporarily collected in the oil storage cavity 142c between the roller 142 and the first bearing 150 and used later for lubricating the friction between the roller 142 and the first bearing 150 or the first cover 133.
  • FIG. 14 shows one embodiment of the construction to feed oil to the vane 143 and the bushes 144 in accordance with the present invention, with the oil being fed between the vane 143 and the bushes 144 through an oil groove 143a or an oil hole.
  • the passage going through the vane 143 and the bushes 144 is formed extendedly from the oil storage cavity 142c placed contiguous with the upper portion of the roller of the axis of rotation 141. In so doing oil flows down, by the gravity, along the vane 143 and the bushes 144 from the upper side of the roller 141 evenly to achieve lubrication.
  • the bushes 144 may be made of natural-lubricating materials.
  • FIG. 15 shows a cross section of the first bearing 150.
  • FIG. 16 is a transverse cross-sectional view showing a compressor in accordance with the second embodiment of the present invention.
  • the compressor in accordance with the second embodiment of the present invention includes a hermetic container 210, a stator 220 installed within the hermetic container 210, a first rotating member 230 installed within the stator 220 and rotating with an interaction with the stator 220, a second rotating member 240 rotating within the first rotating member 230 by a rotational force transferred from the first rotating member 230 for compressing refrigerant therebetween, a muffler 250 for guiding refrigerant suction/discharge to a compression chamber P between the first and second rotating members 230 and 240, a bearing 260 supporting the first and second rotating members 230 and 240 to be able to rotate within the hermetic container 210, and a mechanical seal 270.
  • An electromotive mechanism part employs, for example, a BLDC motor including the stator 220 and the first rotating member 230, and a compression mechanism part includes the first and second rotating members 230 and 240, the muffler 250, the bearing 260 and the mechanical seal 270. Therefore, by increasing inner diameter of the electromotive mechanism part instead of reducing its height, the compression mechanism part can be arranged within the electromotive mechanism part, thereby lowering the total height of the compressor.
  • the hermetic container 210 is composed of a cylinder-shaped body 211, and upper/lower shells 212 and 213 coupled to the top/bottom of the body 211 and stores oil at a suitable height to lubricate or smooth the first and second rotating members 230 and 240.
  • the upper shell 213 includes a suction tube 214 on one side for sucking refrigerant, and a discharge tube 215 at the center for discharging refrigerant.
  • a compressor is a high-pressure type compressor or a low-pressure type compressor is determined depending on the connection structure of the suction tube 214 and the discharge tube 215.
  • This particular embodiment of the invention introduces a low pressure compressor, wherein the suction tube 214 is connected to the hermetic container 210 and the discharge tube 215 is connected directly to the compression mechanism part.
  • a low-pressure refrigerant is sucked in through the suction tube 214, it fills the interior of the hermetic container 210 and flows into the compression mechanism part throigh the suction tube 215.
  • the stator 220 is composed of a core 221, and a coil 222 primarily wound around the core 221. Since the stator 220 has the same construction with the compressor stator in accordance with the first embodiment of the present invention, it will not be explained here.
  • FIG. 17 is an exploded perspective view showing the compressor in accordance with the second embodiment of the present invention.
  • the first rotating member 230 is composed of a rotor 231, a cylinder 232, a shaft cover 233. and a cover 234.
  • the rotor 231 has a cylindrical shape, with the rotor 231 rotating within the stator 220 by a rotating electromagnetic field generated from the stator 220, and inserted therethrough are plural permanent magnets (not shown) in an axial direction to generate a rotating magnetic field.
  • the cylinder 232 also takes the form of a cylinder to create a compression chamber P inside.
  • the rotor 231 and the cylinder 232 can be manufactured separately and joined together later, or can be integrally formed from the beginning.
  • the shaft cover 233 and the main cover 234 are coupled to the rotor 231 or the cylinder 232 in the axial direction, and the compression chamber P is defined between the cylinder 232 and the shaft cover 233 and the main cover 234.
  • the shaft cover 233 is composed of a planar shape cover portion 233A for covering the upper surface of the roller 242, and a downwardly projecting hollow shaft 233B at the center.
  • the cover portion 233A of the shaft cover 233 includes a suction port 233a for sucking in refrigerant therethrough, a discharge port 233b for discharging a compressed refrigerant therethrough from the compression chamber P, and a discharge valve (not shown) mounted thereon.
  • the shaft 233B of the shaft cover 233 includes discharge guide passages 233c and 233d for guiding refrigerant to the outside of the hermetic container 210, with the refrigerant having been discharged through the discharge port 233b of the shaft cover 233. Also, the shaft 233B is designed to be inserted into the mechanical seal 270 by forming part of its outer circumferential surface at the tip. Similar to the shaft cover 233, the main cover 234 is composed of a planar shape cover portion 234a for covering the lower surface of the roller 242, and a downwardly projecting hollow shaft portion 234b at the center.
  • the shaft portion 234b may be optionally omitted, its role in receiving a load acting thereon increases a contact area with the bearing 260 and give more stable support to the main cover 234. Since the shaft cover 233 and the main cover 234 are bolt-fastened to the rotor 231 or the cylinder 232 in the axial direction, the rotor 231, the cylinder 232, and the shaft cover and the main cover 233 and 234 rotate together as one unit.
  • the muffler 250 which includes a suction chamber 251 communicated with the suction port 233a of the shaft cover and a discharge chamber 252 communicated with the discharge port 233b and the discharge guide passages 233c and 233d of the shaft cover 233, with the suction chamber 251 being defined separately from the discharge chamber 252, is also joined in the axial direction of the shaft cover 233.
  • the suction chamber 251 of the muffler 250 may be omitted, but it is better for the muffler 250 to have the suction chamber with the suction port 251a to be able to suck the refrigerant within the hermetic container 210 into the suction port 233a of the shaft cover 233.
  • the second rotating member 240 is composed of an axis of rotation 241, a roller 242, and a vane 243.
  • the axis of rotation 241 is protrusively formed towards one side, i.e., lower surface, in the roller 242 axis direction. Because the axis of rotation 241 is protruded only from the lower surface, its protruded length is longer than that in the case where the axis of rotation is protruded from both the upper and lower surfaces so it can support the motion of the second rotating member more stably. Also, even if the axis of rotation 241 and the roller 242 may have been manufactured separately, they must join together to be able to rotate as one unit.
  • the axis of rotation 241 takes the form of a hollow shaft passing through the inside of the roller 242, with the hollow being composed of an oil feeder 241a for pumping oil.
  • the oil feeder 241a of the axis of rotation 241 is provided with a helical member to assist oil ascending by a rotational force, or a groove to assist oil ascending by a capillary phenomenon.
  • the axis of rotation 241 and the roller 242 each have all kinds of oil feed holes 241b and oil storage grooves 242b and oil storage cavities 242a and 242c for supplying oil from the oil feeder 241a into between two or more members subject to sliding interactions.
  • the first and second rotating members 230 and 240 described earlier are rotatably supported on the inside of the hermetic container 210 by the bearing 260 and the mechanical seal 270 that are coupled in the axial direction.
  • the bearing 260 is bolt- fastened to the lower shell 213, and the mechanical seal 270 is secured to the inside of the hermetic container 210 by welding or the like in communication with the discharge tube 215 of the hermetic container 210.
  • the mechanical seal 270 is a device for preventing a fluid leak because of the contact between a rapidly spinning shaft and a fixed element/rotatory element in general, and is disposed between the discharge tube 215 of the stationary hermetic container 210 and the rotating shaft 233B of the shaft cover 233.
  • the mechanical seal 270 rotatably supports the shaft cover within the hermetic container 210 and communicates the shaft 233B of the shaft cover 233 with the discharge tube 215 of the hermetic container 210, while preventing a refrigerant leak between them.
  • the bearing 260 is constructed to adopt a journal bearing for rotatably supporting the outer peripheral surface of the axis of rotation 241 and the inner peripheral surface of the main cover 234, and a trust bearing for rotatably supporting the lower surface of the roller 242 and the lower surface of the main cover 234.
  • the bearing 260 is composed of a planar shape support 261 that is bolt-fastened to the lower shell 213, and a shaft 262 disposed at the center of the support 261, with the shaft having an upwardly protruded hollow 262a (see FIG. 17).
  • the center of the hollow 262a of the bearing 260 is formed at a position eccentric from the center of the shaft 262 of the bearing 260, or may be collinear with the center of the shaft 262 of the bearing 260 depending on whether the roller 242 is formed eccentric. More details are now provided below.
  • FIGS. 18 through 20 each illustrate a transverse cross-sectional view showing a rotation centerline of the compressor in accordance with the second embodiment of the present invention.
  • FIGS. 18 throigh 20 One example of relative positioning of the first and second rotating members 230 and 240 is illustrated in FIGS. 18 throigh 20.
  • 'a' indicates a centerline of the first axis of rotation of the first rotating member 230, or it may be regarded as a longitudinal centerline of the shaft 234b of the main cover 234, or a longitudinal centerline of the shaft 262 of the bearing 260.
  • the first rotating member 230 includes the rotor 231, the cylinder 232, the shaft cover 233 and the main cover 234 as shown in this embodiment, with all the elements rotating together en bloc, 'a' may be regarded as the rotation centerline of them, 'b' indicates a centerline of the second axis of rotation of the second rotating member 240 or a longitudinal centerline of the axis of the rotation 241, and 'c' indicates a longitudinal centerline of the second rotating member 240 or a longitudinal centerline of the roller 242.
  • FIG. 18 shows that the centerline 'b' of the second axis of rotation is spaced apart a predetermined distance from the centerline 'a' of the first axis of rotation, and the longitudinal centerline 'c' of the second rotating member 240 is collinear with the centerline 'b' of the second axis of rotation.
  • the second rotating member 240 is disposed eccentric with respect to the first rotating member 230, and when the first and second rotating members 230 and 240 rotate together by the medium of the vane 243, they repeatedly contact, separate, and retouch per rotation as explained before, thereby compressing refrigerant within the compression chamber, as in this embodiment.
  • FIG. 19 shows that the centerline 'b' of the second axis of rotation is spaced apart a predetermined distance from the centerline 'a' of the first axis of rotation, and the longitudinal centerline 'c' of the second rotating member 240 is spaced apart a predetermined distance from the centerline 'b' of the second axis of rotation, but the centerline 'a' of the first axis of rotation and the longitudinal centerline 'c' of the second rotating member 240 are not collinear.
  • the second rotating member 240 is disposed eccentric with respect to the first rotating member 230, and when the first and second rotating members 230 and 240 rotate together by the medium of the vane 243, they repeatedly contact, separate, and retouch per rotation as explained before in the first embodiment, thereby compressing refrigerant within the compression chamber, as in this embodiment.
  • FIG. 20 shows that the centerline 'b' of the second axis of rotation is collinear with the centerline 'a' of the first axis of rotation, and the longitudinal centerline 'c' of the second rotating member 240 is spaced apart a predetermined distance from the centerline 'a' of the first axis of rotation and from the centerline 'b 1 of the second axis of rotation.
  • the second rotating member 240 is disposed eccentric with respect to the first rotating member 230, and when the first and second rotating members 230 and 240 rotate together by the medium of the vane 243, they repeatedly contact, separate, and retouch per rotation as explained before in the first embodiment, thereby compressing refrigerant within the compression chamber, as in this embodiment.
  • the rotor 231 and the cylinder 232 are either manufactured separately and then coupled, or manufactured in one unit from the beginning.
  • the axis of rotation 241, the roller 242 and the vane 243 can also be manufactured separately or integrally, but either way, they should be able to rotate as one unit.
  • the vane 243 is inserted between the bushes 244 within the cylinder 231. Overall, the axis of rotation 241, the roller 242 and the vane 243 are mounted within the rotor 231 and the cylinder 232.
  • the shaft cover 233 and the main cover 234 are bolt-fastened in the axial direction of the rotor 231 and the cylinder 232, with the shaft cover 233 covering the upper surface of the roller 242 while the main cover 234 covering the roller 242 even if the axis of rotation 241 may pass through the main cover 234.
  • the muffler 250 is bolt-fastened in the axial direction of the shaft cover 233, with the shaft 233B of the shaft cover 233 fitting into a shaft cover mount hole 253 of the muffler 250 to pass through the muffler 250.
  • a separate sealing member may be provided additionally to the joint area between the shaft cover 233 and the muffler 250.
  • the bearing 260 is bolt-fastened to the lower shell 213, and the rotation assembly is then assembled to the bearing 260, with the inner circumferential surface of the shaft 234a of the main cover 234 circumscribing the outer circumferential surface of the shaft 262 of the bearing 260, with the outer circumferential surface of the axis of rotation 241 being inscribed in the hollow 262a of the bearing 260.
  • the stator 220 is press fitted into the body 211, and the body 211 is joined to the upper shell 212, with the stator 220 being positioned to maintain an air-gap with the outer circumferential surface of the rotation assembly.
  • the mechanical seal 270 is assembled within the upper shell 212 in a way that it is communicated with the discharge tube 215, and the upper shell 212 having the mechanical seal 270 being secured thereon is joined to the body 211, with the mechanical seal 270 being inserted into a stepped portion on the outer circumferential surface of the shaft 233B of the shaft cover 233.
  • the mechanical seal 270 is assembled to enable the communication between the shaft 233B of the shaft cover 233 and the discharge tube 215 of the upper shell 212.
  • FIG. 21 is a transverse cross-sectional view showing how refrigerant and oil flow in the compressor in accordance with the second embodiment of the present invention.
  • the vane is 234 is installed at the cylinder 231 to be able to linearly reciprocate, a rotational force of the first rotating member 230 is transferred to the second rotating member 240 so the second rotating member 240, i.e., the axis of rotation 241, the roller 242 and the vane 243, rotate together as one unit.
  • the first and second rotating members 230 and 240 are disposed eccentric with respect to each other, they repeatedly contact, separate, and retouch, thereby varjing the volume of the suction region/the discharge region divided by the vane 243 so as to compress refrigerant and to pump oil at the same time to lubricate between two slidingly contacting members.
  • the oil pumps up or ascends along the helical member 245a or grooves 245c disposed within an oil feeder 241a of the axis of the rotation 241 and flows out through an oil feed hole 241b of the axis of the rotation 241, not only to gather up at an oil storage cavity 241c between the axis of rotation 241 and the bearing 260, but also to lubricate between the axis of rotation 241, the roller 242, the bearing 260, and the main cover 234.
  • the oil having been gathered up at the oil storage cavity 241c between the axis of rotation 241 and the bearing 260 pumps up or ascends through the oil feed hole 242b of the roller 242, not only to gather up at oil storage cavities 233e and 242c between the axis of rotation 241, the roller 242 and the fist cover 233, but also to lubricate between the axis of rotation 241, the roller 242, the shaft cover 233.
  • FIGS. 22 and 23 each illustrate a perspective view of an example of how the roller 242 and the oil feed member 245 are assembled in the compressor in accordance with the second embodiment of the present invention.
  • an oil feed member 245a may be provided to the oil feeder 241b within the axis of rotation 241.
  • the oil fee member 245a may take the form of a helical shape to function as a centrifugal pump for example.
  • the helical oil feed member can be prepared by twisting a roughly rectangular board in a spiral form. In such case, the board may be twisted to the left or right to help the oil climb up along the face of the board according to the rotational direction of the axis of rotation 241.
  • the oil feed member may also take the form of a pillar shape with a helical groove formed in its outer circumferential surface, or a propeller shape.
  • the helical oil feed member 245a rotates together with the axis of rotation 141 within the oil feeder 241b to pump up oil by the rotational force.
  • FIG. 23 shows yet another preferred embodiment of the oil feed member 245b, with the oil feeder 241a pumping up oil using a capillary phenomenon.
  • a pillar shape oil feed member 245b is press fitted into the oil feeder 241a within the axis of rotation 241, and plural grooves 245 c with a diameter small enough for the capillary process to take place between the inner circumferential surface of the axis of rotation 241 and the oil feed member are formed.
  • the grooves 245c may be formed in the inner circumferential surface of the oil feeder 241a, or one side of the oil feed member 245b, or both sides.
  • an oil feed passage communicating with peripheral area and the roller 242 to evenly distribute the oil having been pumped up along the axis of rotation 241.
  • a refrigerant suction passage is separately formed above the roller 242, with the axis of rotation 241 being integrally formed with the roller 241 underneath it, and an oil passage is formed on the lower side (i.e. below the roller 242 of the axis of rotation 241).
  • the oil feeder 241a is arranged even in the interior of the roller 242 in the axial direction, and the roller has one end blocked inside.
  • the blocked end of the roller may be covered by the cover portion 233A of the shaft cover 233, or the upper side of the roller may optionally be blocked.
  • the oil feed hole 241b is drilled, radially passing through the axis of rotation 241 located contiguous with the lower side of the roller 242.
  • the oil flowing out through the oil feed hole 241c is fed between the outer circumferential surface of the axis of rotation 241 and the second bearing 260, and between the roller 242 and the second cover 234, thereby forming an oil film of a uniform thickness for lubrication.
  • the second cover 234 has a collection cavity to collect the oil having been used for lubricating between the roller 242 and the contact surface to the bottom of the hermetic container 210.
  • an oil storage cavity 241c is formed between the axis of rotation 241 and the second bearing 260 to serve as a temporal reservoir of the oil flowing out from the oil feed hole 241b.
  • the roller 242 has an oil feed hole 242b that is drilled in the axial direction to be in communication with the oil storage cavity 241c, so the oil is temporarily collected at the oil storage cavities 233e and 242c formed between the shaft cover 233 and the roller 233 and then used for lubrication of friction between the roller 242 and the shaft cover 233.
  • the oil which is supplied directly from the oil feeder 241a and the oil which is supplied through the oil feed hole 242b are temporarily stored at the oil storage cavity 233e formed in the roller 242 and the oil storage cavity 242c formed in the shaft cover 233 contacting the roller 242, and then form an oil film between the roller 242 and the shaft cover 233 to lubricate the friction between them.
  • the oil feeder 242a of the compressor of the second embodiment of the present invention up to the height of a contact portion between the roller 242 and the shaft cover 233 and feed oil directly to the oil storage cavities 233e and 242c.
  • the oil feed hole 242b may not necessarily drilled in the roller 242.
  • FIG. 24 shows one embodiment of the construction to feed oil to the vane 243 and the bushes 244 in accordance with the second embodiment of the present invention, with the oil being fed between the vane 243 and the bushes 244 through an oil groove 243a or an oil hole.
  • the passage going through the vane 243 and the bushes 244 is formed extendedly from the oil storage cavities 233e and 242c placed contiguous with the upper portion of the roller 242. In so doing oil flows down, by the gravity, along the vane 243 and the bushes 244 from the upper side of the roller 241 evenly to achieve lubrication.
  • the bushes 244 may be made of natural-lubricating materials.
  • refrigerant is compressed, and when a discharge valve (not shown) is open at a pressure above the preset level the compressed refrigerant is then discharged in the direction of the shaft cover 233 through the discharge incline part 236(see FIG. 17).
  • the discharged refrigerant flows into the discharge chamber 252 of the muffler 250 through the discharge port 233b of the shaft cover 233.
  • the noise level is reduced as the high-pressure refrigerant passes through the discharge chamber 252 of the muffler 250.
  • the refrigerant flow inducing a lower noise is eventually exits outside of the hermetic container 210 through the discharge passages 233c and 233d formed in the shaft of the shaft cover 233, and the discharge tube 215 of the hermetic container 210.
  • the sliding contact between the cylinder 132, 232 and the roller 142, 242 is noticeably reduced by rotating the roller 142, 242, the cylinder 132, 232, the cover 133, 134, 233, 234 together with the rotor 131, 231.
  • the friction between the roller and the cover is relatively smaller than that of the conventional compressors. This is primarily because the roller of the present invention compressor makes a translational motion at the contact surface with the cover, unlike the conventional roller making both rotational and translational motions between the covers.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Abstract

Un compresseur élimine les contacts glissants entre un cylindre et un rouleau afin de réduire au minimum le mélange d’huile de lubrification dans un fluide frigorigène, et est structuré pour répartir de façon uniforme l’huile de lubrification sur les parties de contact glissant d’un actionneur de compresseur grâce au pompage de l’huile depuis l’intérieur sur un axe de rotation, le compresseur comprenant : un récipient hermétique stockant de l’huile dans une partie inférieure; un stator monté dans le récipient hermétique; un rotor de type cylindre tournant dans le stator par un champ électromagnétique rotatif provenant du stator, le rotor délimitant une chambre de compression à l’intérieur; un rouleau tournant dans la chambre de compression du rotor de type cylindre par une force de rotation transférée depuis le rotor, le rouleau comprimant le fluide frigorigène au cours de la rotation; un axe de rotation formant un seul bloc avec le rouleau et s’étendant dans une direction axiale; une aube divisant la chambre de compression en une région aspiration dans laquelle le fluide frigorigène est aspiré et une région compression d’où le fluide frigorigène est comprimé/évacué, l’aube transférant la force de rotation du rotor de type cylindre vers le rouleau; et des passages d’acheminement d’huile situés sur l’axe de rotation et le rouleau, le passage d’acheminement d’huile acheminant l’huile qui est pompée le long du mouvement de l’axe de rotation vers une zone où deux, ou plus, éléments glissent dans la chambre de compression.
PCT/KR2008/007015 2008-07-22 2008-11-28 Compresseur WO2010010998A2 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
CN200880130055.7A CN102076966B (zh) 2008-07-22 2008-11-28 压缩机
US13/054,981 US9097254B2 (en) 2008-07-22 2008-11-28 Compressor

Applications Claiming Priority (10)

Application Number Priority Date Filing Date Title
KR10-2008-0071381 2008-07-22
KR1020080071381 2008-07-22
KR10-2008-0112746 2008-11-13
KR10-2008-0112750 2008-11-13
KR1020080112746A KR101467577B1 (ko) 2008-07-22 2008-11-13 압축기
KR1020080112750A KR101521300B1 (ko) 2008-07-22 2008-11-13 압축기
KR10-2008-0112761 2008-11-13
KR1020080112737A KR101452509B1 (ko) 2008-07-22 2008-11-13 압축기
KR10-2008-0112737 2008-11-13
KR1020080112761A KR101528643B1 (ko) 2008-07-22 2008-11-13 압축기

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WO2010010998A2 true WO2010010998A2 (fr) 2010-01-28
WO2010010998A3 WO2010010998A3 (fr) 2010-04-08

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2016065257A1 (fr) * 2014-10-24 2016-04-28 Bristol Compressors International, Llc Compresseur de fluide

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB478146A (en) * 1935-08-19 1938-01-13 William Ward Davidson Improvements in rotary pumps

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB478146A (en) * 1935-08-19 1938-01-13 William Ward Davidson Improvements in rotary pumps

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2016065257A1 (fr) * 2014-10-24 2016-04-28 Bristol Compressors International, Llc Compresseur de fluide

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