US20090100861A1 - Compressor - Google Patents

Compressor Download PDF

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Publication number
US20090100861A1
US20090100861A1 US12/297,505 US29750507A US2009100861A1 US 20090100861 A1 US20090100861 A1 US 20090100861A1 US 29750507 A US29750507 A US 29750507A US 2009100861 A1 US2009100861 A1 US 2009100861A1
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United States
Prior art keywords
oil
stator core
oil return
motor
return passages
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.)
Abandoned
Application number
US12/297,505
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English (en)
Inventor
Masahide Higuchi
Yasukazu Nabetani
Azusa Ujihara
Hideki Mori
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.)
Daikin Industries Ltd
Original Assignee
Daikin Industries Ltd
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 Daikin Industries Ltd filed Critical Daikin Industries Ltd
Assigned to DAIKIN INDUSTRIES, LTD. reassignment DAIKIN INDUSTRIES, LTD. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: HIGUCHI, MASAHIDE, NABETANI, YASUKAZU, UJIHARA, AZUSA, MORI, HIDEKI
Publication of US20090100861A1 publication Critical patent/US20090100861A1/en
Abandoned 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
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/02—Lubrication
    • F04B39/0284—Constructional details, e.g. reservoirs in the casing
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/02—Lubrication
    • 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
    • F04C29/028—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
    • 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
    • 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
    • F04C29/04—Heating; Cooling; Heat insulation
    • F04C29/045—Heating; Cooling; Heat insulation of the electric motor in hermetic pumps

Definitions

  • the present invention relates to a compressor to be used for, for example, air conditioners, refrigerators and the like.
  • a compressor includes a closed container, a compression element placed within the closed container, and a motor placed in the closed container and acting to drive the compression element via a shaft, with an oil reservoir formed at a bottom portion of the closed container so that lubricating oil is accumulated in the oil reservoir (see JP 2003-262192 A).
  • an object of the present invention is to provide a compressor which is prevented from shortage of oil in the oil reservoir while motor efficiency of a motor is maintained.
  • the present invention provides a compressor comprising:
  • a stator core of the motor has a plurality of oil return passages extending through one surface of the stator core located on its one side closer to the oil reservoir and the other surface of the stator core located on its another side opposite to the oil reservoir, and
  • a hydraulic diameter of each of the oil return passages is 5 mm or larger, and a ratio of a total area of the plurality of oil return passages to an area of a virtual circle having a diameter equal to a maximum outer diameter of the stator core is 5 to 15%.
  • the hydraulic diameter of each of the oil return passages is 5 mm or larger, and the ratio of the total area of the plurality of oil return passages to the area of the virtual circle having the diameter equal to the maximum outer diameter of the stator core is 5 to 15%. Therefore, lubricating oil accumulated on the other surface side of the stator core can be returned to the oil reservoir located on the one surface side of the stator core via the plurality of oil return passages, so that oil shortage in the oil reservoir can be prevented. Moreover, the cross-sectional area of the stator core can be ensured, and the motor efficiency can be maintained. Particularly when carbon dioxide is used as the refrigerant, in which use of a high-viscosity lubricating oil is involved, the lubricating oil can effectively be returned to the oil reservoir.
  • stator core is placed radially outside of a rotor of the motor
  • the oil return passages are located on an outer circumferential side of the stator core.
  • the oil return passages are located on the outer circumferential side of the stator core, lubricating oil that has been scattered radially outward by the rotor or lubricating oil that has stuck to the inner circumferential surface of the closed container can effectively be led to the oil return passages, so that oil shortage in the oil reservoir can be prevented more reliably.
  • a refrigerant in the closed container is carbon dioxide.
  • the refrigerant within the closed container is carbon dioxide, in which use of a high-viscosity lubricating oil is involved, the lubricating oil can effectively be returned to the oil reservoir.
  • the hydraulic diameter of each of the oil return passages is 5 mm or larger, and the ratio of the total area of the plurality of oil return passages to the area of the virtual circle having the diameter equal to the maximum outer diameter of the stator core is 5 to 15% so that oil shortage in the oil reservoir can be prevented and the motor efficiency can be maintained.
  • FIG. 1 is a longitudinal sectional view showing an embodiment of a compressor of the invention
  • FIG. 2 is a plan view of main part of the compressor
  • FIG. 3 is a cross-sectional view of a vicinity of a motor in the compressor
  • FIG. 4 is an enlarged view of part A of FIG. 3 ;
  • FIG. 5 is a graph showing relationships of oil shortage and motor efficiency with hydraulic diameter and area ratio
  • FIG. 6A is a graph showing a relationship between area ratio and motor-efficiency decreasing rate
  • FIG. 6B is a graph showing a relationship between area ratio and oil-level decreasing rate
  • FIG. 7A is a graph showing a relationship between hydraulic diameter and motor-efficiency decreasing rate
  • FIG. 7B is a graph showing a relationship between hydraulic diameter and oil-level decreasing rate.
  • FIG. 1 shows a longitudinal sectional view which is an embodiment of a compressor of the invention.
  • This compressor includes a closed container 1 , a compression element 2 placed within the closed container 1 , and a motor 3 placed in the closed container 1 and acting to drive the compression element 2 via a shaft 12 .
  • This compressor is a so-called vertical high-pressure dome-type rotary compressor, in which the compression element 2 is placed below and the motor 3 is placed above within the closed container 1 .
  • the compression element 2 is driven by a rotor 6 of the motor 3 via the shaft 12 .
  • the compression element 2 sucks in a refrigerant gas from an accumulator 10 through a suction pipe 11 .
  • the refrigerant gas can be obtained by controlling unshown condenser, expansion mechanism and evaporator that constitute an air conditioner as an example of a refrigeration system in combination with the compressor.
  • the refrigerant gas which is carbon dioxide, becomes as high a pressure as about 12 MPa within the closed container 1 .
  • R410A or R22 or other like refrigerant may be used as the refrigerant.
  • a compressed high-temperature, high-pressure refrigerant gas is discharged from the compression element 2 to fill the closed container 1 therewith internally, while the refrigerant gas is passed through a gap between the stator 5 and the rotor 6 of the motor 3 to cool the motor 3 .
  • the refrigerant gas is thereafter discharged outside from a discharge pipe 13 provided on the upper side of the motor 3 .
  • an oil reservoir 9 In lower portion of a high-pressure region within the closed container 1 is formed an oil reservoir 9 in which lubricating oil is accumulated.
  • This lubricating oil moves from the oil reservoir 9 through oil passages (not shown) provided in the shaft 12 to sliding parts such as the compression element 2 and a bearing of the motor 3 , thus lubricating the sliding parts.
  • the lubricating oil to be used is a high-viscosity one.
  • a lubricating oil having a viscosity of 5-300 cSt at 40° C. is used as this lubricating oil.
  • This lubricating oil is exemplified by polyalkylene glycol oil (such as polyethylene glycol and polypropylene glycol), ether oil, ester oil, and mineral oil.
  • the compression element 2 includes a cylinder 21 fitted to an inner surface of the closed container 1 , and an upper-side end plate member 50 and a lower-side end plate member 60 fitted to upper and lower opening ends of the cylinder 21 , respectively.
  • a cylinder chamber 22 is defined by the cylinder 21 , the upper-side end plate member 50 and the lower-side end plate member 60 .
  • the upper-side end plate member 50 has a disc-shaped body portion 51 , and a boss portion 52 provided upwardly at a center of the body portion 51 .
  • the shaft 12 is inserted into the body portion 51 and the boss portion 52 .
  • a discharge hole 51 a communicating with the cylinder chamber 22 .
  • a discharge valve 31 is fitted to the body portion 51 so as to be positioned on one side of the body portion 51 opposite to the side on which the cylinder 21 is provided.
  • This discharge valve 31 is, for example, a reed valve which opens and closes the discharge hole 51 a.
  • a cup-type muffler cover 40 is fitted on the body portion 51 on its one side opposite to the cylinder 21 so as to cover the discharge valve 31 .
  • the muffler cover 40 is fixed to the body portion 51 by fixing members 35 (e.g., bolt).
  • the boss portion 52 is inserted into the muffler cover 40 .
  • the muffler cover 40 and the upper-side end plate member 50 define a muffler chamber 42 .
  • the muffler chamber 42 and the cylinder chamber 22 are communicated with each other via the discharge hole 51 a.
  • the muffler cover 40 has a hole portion 43 .
  • the hole portion 43 By the hole portion 43 , the muffler chamber 42 and an outer side of the muffler cover 40 are communicated with each other.
  • the lower-side end plate member 60 has a disc-shaped body portion 61 , and a boss portion 62 provided downwardly at a center of the body portion 61 .
  • the shaft 12 is inserted into the body portion 61 and the boss portion 62 .
  • one end portion of the shaft 12 is supported by the upper-side end plate member 50 and the lower-side end plate member 60 . That is, the shaft 12 cantilevers. One end portion (on the support end side) of the shaft 12 intrudes into the cylinder chamber 22 .
  • an eccentric pin 26 is provided so as to be positioned within the cylinder chamber 22 of the compression element 2 .
  • the eccentric pin 26 is fitted into a roller 27 .
  • the roller 27 is placed revolvable in the cylinder chamber 22 so that compression action is exerted by revolving motion of the roller 27 .
  • one end portion of the shaft 12 is supported by a housing 7 of the compression element 2 on both sides of the eccentric pin 26 .
  • the housing 7 includes the upper-side end plate member 50 and the lower-side end plate member 60 .
  • the cylinder chamber 22 is internally partitioned by a blade 28 integrally provided with the roller 27 . That is, in a chamber on the right side of the blade 28 , the suction pipe 11 is opened in the inner surface of the cylinder chamber 22 to form a suction chamber (low-pressure chamber) 22 a . In a chamber on the left side of the blade 28 , the discharge hole 51 a (shown in FIG. 1 ) is opened in the inner surface of the cylinder chamber 22 to form a discharge chamber (high-pressure chamber) 22 b.
  • Semicolumnar-shaped bushes 25 , 25 are set in close contact with both surfaces of the blade 28 to provide a seal. Lubrication with the lubricating oil is implemented between the blade 28 and the bushes 25 , 25 .
  • the blade 28 moves back and forth while both side faces of the blade 28 are held by the bushes 25 , 25 . Then, the low-pressure refrigerant gas is sucked from the suction pipe 11 into the suction chamber 22 a and compressed into a high pressure in the discharge chamber 22 b , so that a high-pressure refrigerant gas is discharged from the discharge hole 51 a (shown in FIG. 1 ).
  • the refrigerant gas discharged from the discharge hole 51 a is discharged via the muffler chamber 42 outward of the muffler cover 40 .
  • the motor 3 has the rotor 6 , and the stator 5 placed radially outside of the rotor 6 with an air gap interposed therebetween.
  • the rotor 6 has a rotor body 610 , and magnets 620 embedded in the rotor body 610 .
  • the rotor body 610 is cylindrical shaped and formed of, for example, multilayered electromagnetic steel plates.
  • the shaft 12 is fitted to a hole portion at a center of the rotor body 610 .
  • Each of the magnets 620 is a flat permanent magnet. Six of the magnets 620 are arrayed at center angles of equal intervals in the circumferential direction of the rotor body 610 .
  • the stator 5 has a stator core 510 , and coils 520 wound around the stator core 510 .
  • the coils 520 are partly omitted in illustration.
  • the stator core 510 has an annular portion 511 , and nine teeth 512 protruding radially inwardly from an inner circumferential surface of the annular portion 511 and arrayed circumferentially at equal intervals.
  • the stator core 510 is formed of a plurality of multilayered steel plates.
  • the coils 520 are wound around the individual teeth 512 , respectively, and not wound over the plurality of teeth 512 , hence a concentrated winding.
  • the motor 3 is a so-called 6-pole, 9-slot type one.
  • the rotor 6 is rotated along with the shaft 12 .
  • the stator core 510 has a plurality of oil return passages 530 extending through one surface (lower surface) 510 a of the stator core 510 located on its one side closer to the oil reservoir 9 and the other surface (upper surface) 510 b of the stator core 510 located on the other side opposite to the oil reservoir 9 .
  • the oil return passages 530 are located on the outer circumferential side of the stator core 510 .
  • the oil return passages 530 are formed by so-called core cuts of recessed grooves or D-cut surfaces or the like formed in the outer circumferential surface of the stator core 510 . That is, the oil return passages 530 are spaces each surrounded by an inner surface of a core cut and an inner circumferential surface 1 b of the closed container 1 .
  • the oil return passages 530 are provided radially outside of the teeth 512 , respectively, counting nine equal to that of the teeth 512 .
  • the oil return passages 530 are formed each into a generally rectangular shape as viewed along a center axis 1 a of the closed container 1 .
  • the hydraulic diameter of each oil return passage 530 is 5 mm or larger, and the ratio of the total area of the plural oil return passages 530 to the area of the virtual circle having a diameter equal to the maximum outer diameter of the stator core 510 (hereinafter, referred to as area ratio) is 5 to 15%.
  • FIG. 4 is an enlarged view of part A of FIG. 3 .
  • the area S of the oil return passage 530 is, as shown by hatching in FIG. 4 , an area surrounded by the inner surface of the recessed groove of the stator core 510 and the inner circumferential surface 1 b of the closed container 1 .
  • the circumferential length L of the oil return passage 530 is, as shown by bold line in FIG. 4 , a value resulting from adding up a length of the inner surface of the recessed groove of the stator core 510 and a length of the inner circumferential surface 1 b of the closed container 1 .
  • the virtual circle having a diameter equal to the maximum outer diameter of the stator core 510 is, as shown in FIG. 3 , coincident with the inner circumferential surface 1 b of the closed container 1 . That is, the area of this virtual circle is coincident with a cross-sectional area of the inside of the closed container 1 on the other surface 510 b .
  • the total area of the plurality of oil return passages 530 refers to a total sum of areas S of the oil return passages 530 on the other surface 510 b.
  • the hydraulic diameter of each oil return passage 530 on the other surface 510 b of the stator core 510 is 5 mm or larger, and the area ratio is 5 to 15%. Therefore, lubricating oil that has flowed to the downstream side (upper side) of the motor 3 along with the refrigerant gas so as to be accumulated on the other surface 510 b side of the stator core 510 can be returned to the oil reservoir 9 on the one surface 510 a side of the stator core 510 via the plurality of oil return passages 530 , so that oil shortage in the oil reservoir 9 can be prevented.
  • lubricating oil in the oil reservoir 9 can effectively be fed via the shaft 12 to sliding parts such as the compression element 2 and the bearing of the motor 3 , so that the reliability of the compressor is improved.
  • stator core 510 the cross-sectional area of the stator core 510 can be ensured, and the motor efficiency can be maintained. Particularly when carbon dioxide is used as the refrigerant, in which use of a high-viscosity lubricating oil is involved, the lubricating oil can effectively be returned to the oil reservoir 9 .
  • each oil return passage 530 satisfies to be 5 mm only on the other surface 510 b of the stator core 510 , the lubricating oil overcomes the viscosity by its dead weight to move down along the oil return passages 530 up to the oil reservoir 9 .
  • each oil return passage 530 is smaller than 5 mm, then the oil return passages 530 are each formed into, for example, a slit shape as its planar shape, so that the lubricating oil sticks to the other surface 510 b of the stator core 510 by its viscosity, thus not going down along the oil return passages 530 , and not moving to the oil reservoir 9 . That is, there is a problem of occurrence of oil shortage.
  • the hydraulic diameter of each oil return passage 530 is larger than 15 mm, then the effective surface area of the annular portion 511 of the stator core 510 becomes smaller, resulting in a deteriorated motor efficiency.
  • the area ratio is smaller than 5%, then the number of oil return passages 530 becomes smaller, so that lubricating oil cannot effectively be returned to the oil reservoir 9 , giving rise to occurrence of oil shortage as a problem.
  • the area ratio is larger than 15%, then the number or area of the oil return passages 530 becomes larger, causing the surface area of the stator core 510 to be smaller, so that the motor efficiency decreases as a problem.
  • each oil return passage 530 is not more than 20 mm (more preferably, not more than 15 mm), in which case the cross-sectional area of the stator core 510 can more reliably be ensured and the motor efficiency can more reliably be maintained.
  • oil return passages 530 are located on the outer circumferential side of the stator core 510 , lubricating oil that has been scattered radially outward by the rotor 6 or lubricating oil that has stuck to the inner circumferential surface 1 b of the closed container 1 can effectively be led to the oil return passages 530 , so that oil shortage in the oil reservoir 9 can more reliably be prevented.
  • FIG. 5 shows relationships of oil shortage and motor efficiency with hydraulic diameter and area ratio.
  • the horizontal axis represents the hydraulic diameter of each oil return passage
  • the vertical axis represents the area ratio (the ratio of the total area of the oil return passages to an outer-diametral area of the stator core, i.e., the area of a circle having a diameter equal to the outer diameter of the stator core).
  • a first region Z 1 i.e., on condition that the hydraulic diameter is 5 to 15 mm and the area ratio is 5 to 15%, then there is no problem in oil shortage or motor efficiency.
  • a third region Z 3 i.e., on condition that the hydraulic diameter is 5 mm or larger and the area ratio is larger than 15%, there is no problem in oil shortage but is a problem in motor efficiency.
  • a fourth region Z 4 i.e., on condition at least either that the hydraulic diameter is smaller than 5 mm or that the area ratio is smaller than 5%, there is no problem in motor efficiency but is a problem in oil shortage.
  • FIG. 6A shows a relationship between area ratio (ratio of the total area of the oil return passages to the outer-diametral area of the stator core) and motor-efficiency decreasing rate.
  • the vertical axis represents motor-efficiency decreasing rate, where the motor efficiency decreases more and more downward of the vertical axis.
  • the motor efficiency is extremely decreases.
  • FIG. 6B shows a relationship between area ratio (ratio of the total area of the oil return passages to the outer-diametral area of the stator core) and oil-level decreasing rate.
  • the vertical axis represents oil-level decreasing rate, where the oil level decreases more and more downward of the vertical axis.
  • the oil level extremely decreases.
  • the area ratio (ratio of total area of oil return passages/outer-diametral area of stator core) needs to be smaller than 15%. Also, since a smaller total area of the oil return passages causes oil returnability to worsen, enough oil level cannot be ensured. Therefore, the area ratio (ratio of total area of oil return passages/outer-diametral area of stator core) needs to be larger than 5%.
  • FIG. 7A shows a relationship between hydraulic diameter of the oil return passages and motor-efficiency decreasing rate.
  • the vertical axis represents motor-efficiency decreasing rate, where the motor efficiency decreases more and more downward of the vertical axis.
  • hydraulic diameters larger than 15 mm lead to occurrence of a problem in motor efficiency.
  • FIG. 7B shows a relationship between hydraulic diameter of the oil return passages and oil-level decreasing rate.
  • the vertical axis represents oil-level decreasing rate, where the oil level decreases more and more downward of the vertical axis.
  • the oil level extremely decreases.
  • a larger hydraulic diameter causes the surface area of the annular portion 511 of the stator core 510 to become smaller, so that the motor efficiency decreases. Therefore, the hydraulic diameter needs to be smaller than 15 mm. Also, since a smaller hydraulic diameter causes oil returnability to worsen, enough oil level cannot be ensured. Therefore, the hydraulic diameter needs to be larger than 5 mm.
  • the compression element 2 may also be a rotary type one in which its roller and blade are provided independent of each other.
  • the compression element 2 may further be a scroll type or reciprocating type one other than the rotary type.
  • the compression element 2 may also be a two-cylinder type one having two cylinder chambers.
  • the coils 520 may be of the so-called distributed winding in which the coils 520 are wound over the plurality of teeth 512 .
  • the oil return passages 530 may be provided on the inner circumferential side of the stator core 510 , or provided at an intermediate portion between the inner circumferential surface and the outer circumferential surface of the stator core 510 . Furthermore, the oil return passages 530 may be provided at any position in the circumferential direction of the stator core 510 , and may be provided at equal or unequal pitches.

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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)
US12/297,505 2006-04-19 2007-04-16 Compressor Abandoned US20090100861A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP2006116226A JP5050393B2 (ja) 2006-04-19 2006-04-19 圧縮機
JP2006-116226 2006-04-19
PCT/JP2007/058246 WO2007123074A1 (ja) 2006-04-19 2007-04-16 圧縮機

Publications (1)

Publication Number Publication Date
US20090100861A1 true US20090100861A1 (en) 2009-04-23

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Application Number Title Priority Date Filing Date
US12/297,505 Abandoned US20090100861A1 (en) 2006-04-19 2007-04-16 Compressor

Country Status (8)

Country Link
US (1) US20090100861A1 (de)
EP (1) EP2009285B1 (de)
JP (1) JP5050393B2 (de)
KR (1) KR101156261B1 (de)
CN (1) CN101415948A (de)
AU (1) AU2007242125B2 (de)
ES (1) ES2594654T3 (de)
WO (1) WO2007123074A1 (de)

Cited By (5)

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US20100296950A1 (en) * 2008-01-24 2010-11-25 Daikin Industries, Ltd. Compressor
US20140140867A1 (en) * 2012-11-19 2014-05-22 Danfoss Commercial Compressors Variable speed scroll compressor
US20160301266A1 (en) * 2015-04-07 2016-10-13 Lg Innotek Co., Ltd. Stator core, a stator and a motor
US20210270271A1 (en) * 2018-07-11 2021-09-02 Fujitsu General Limited Compressor
US20220235770A1 (en) * 2019-10-15 2022-07-28 Daikin Industries, Ltd. Rotary compressor

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Publication number Priority date Publication date Assignee Title
KR101462929B1 (ko) 2008-04-29 2014-11-19 엘지전자 주식회사 밀폐형 압축기
CN110863990B (zh) * 2019-11-19 2021-06-04 珠海格力节能环保制冷技术研究中心有限公司 压缩机、空调器
CN112855535A (zh) * 2019-11-27 2021-05-28 上海海立电器有限公司 压缩机气缸及包括其的压缩机
JP7469405B2 (ja) 2022-08-25 2024-04-16 愛知電機株式会社 電動機および圧縮機

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JP5050393B2 (ja) 2012-10-17
AU2007242125A1 (en) 2007-11-01
KR101156261B1 (ko) 2012-06-13
EP2009285A4 (de) 2014-01-15
CN101415948A (zh) 2009-04-22
EP2009285A1 (de) 2008-12-31
JP2007285266A (ja) 2007-11-01
AU2007242125B2 (en) 2010-05-27
EP2009285B1 (de) 2016-09-14
KR20080099347A (ko) 2008-11-12
WO2007123074A1 (ja) 2007-11-01

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