US20120230853A1 - Scroll Compressor - Google Patents

Scroll Compressor Download PDF

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Publication number
US20120230853A1
US20120230853A1 US13/372,780 US201213372780A US2012230853A1 US 20120230853 A1 US20120230853 A1 US 20120230853A1 US 201213372780 A US201213372780 A US 201213372780A US 2012230853 A1 US2012230853 A1 US 2012230853A1
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US
United States
Prior art keywords
pressure chamber
orbiting
scroll
orbiting scroll
back pressure
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
US13/372,780
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English (en)
Inventor
Yuichi Yanagase
Isamu Tsubono
Eiji Sato
Masatsugu Chikano
Takeshi Tsuchiya
Mutsunori Matsunaga
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.)
Hitachi Global Life Solutions Inc
Original Assignee
Hitachi Appliances 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
Application filed by Hitachi Appliances Inc filed Critical Hitachi Appliances Inc
Assigned to HITACHI APPLIANCES, INC. reassignment HITACHI APPLIANCES, INC. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: CHIKANO, MASATSUGU, SATO, EIJI, TSUBONO, ISAMU, MATSUNAGA, MUTSUNORI, TSUCHIYA, TAKESHI, YANAGASE, YUICHI
Publication of US20120230853A1 publication Critical patent/US20120230853A1/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
    • 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
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
    • 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
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F04C18/0246—Details concerning the involute wraps or their base, e.g. geometry
    • F04C18/0253—Details concerning the base
    • 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
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/02—Lubrication; Lubricant separation
    • F04C29/023—Lubricant distribution through a hollow driving shaft

Definitions

  • the present invention relates to a scroll compressor which handles an HFC type cooking medium, an air and a carbon dioxide corresponding to a natural refrigerant, and the other compressible gas, and more particularly to a scroll compressor which zones a high pressure chamber (having an approximately equal pressure to a discharge pressure) which is constructed by a back face side of an orbiting scroll and a back pressure chamber (a pressure space having a lower pressure than the discharge pressure) by a sealing means in a pressure manner.
  • a high pressure chamber having an approximately equal pressure to a discharge pressure
  • a back pressure chamber a pressure space having a lower pressure than the discharge pressure
  • a so-called high pressure chamber type scroll compressor is provided with a crank shaft which has a crank portion, an orbiting scroll which has an orbiting bearing to which the crank portion is inserted, and a fixed scroll which forms a compression chamber by being engaged with the orbiting scroll, and changes a volumetric capacity of the compression chamber so as to compress the refrigerant by pressing the orbiting scroll to the fixed scroll on the basis of a pressure of the back pressure chamber and turning the orbiting scroll on the basis of a rotation of the crank shaft.
  • patent document 1 JP-A-2003-176794
  • a lubricating oil is intermittently fed by setting a sealing means for sealing a high pressure chamber in the periphery of a center portion of a back face of an orbiting scroll and a back pressure chamber (a low pressure chamber) which is formed by an internal space of an outer periphery in a frame inner peripheral surface which is opposed to an end surface of a boss portion of the back face of the orbiting scroll, and setting a small hole which retains the lubricating oil in the end surface of the boss portion, thereby reciprocating the high pressure chamber in the periphery of the center portion of the back face of the orbiting scroll and the back pressure chamber while being astride the sealing means.
  • an amount of the lubricating oil which is fed to the back pressure chamber from the high pressure chamber is adjusted, an efficiency of the compressor can be widely improved, and it is also possible to improve a reliability of the compressor.”
  • the scroll compressor in accordance with the known art in the patent document 1, it is general to form a vertical structure in which a compression mechanism portion is positioned above and an electric motor portion is positioned below, and it is structured such that the lubricating oil is intermittently fed by setting the sealing means for sealing the high pressure chamber in the center portion of the back face boss portion of the orbiting scroll and the back pressure chamber (the low pressure chamber) which is formed by the internal space of the outer periphery in the frame inner peripheral surface which is opposed to the end surface of the boss portion of the back face of the orbiting scroll, and setting the small hole which retains the lubricating oil in the end surface of the boss portion, thereby reciprocating while being astride the sealing means which zones the high pressure chamber and the back pressure chamber.
  • the seal member since it is structured such that the seal member is arranged in the back face of the orbiting scroll end plate, it has a lubricating oil reservoir in addition to an upper lubricating oil reservoir in the high pressure orbiting bearing upper space in the inner region of the seal member, and there is such a problem that a loss in agitating the lubricating oil becomes larger on the basis of the turning motion of the orbiting scroll in the space portion of the lubricating oil reservoir, and an efficiency becomes lowered.
  • the oil feeding amount is in proportion to a cubic of the bearing gap, there is a limit for controlling an appropriate oil feeding amount by the bearing gap, and it becomes very hard.
  • it is more easily control the oil feeding amount to the back pressure chamber by a scroll compressor which zones a high pressure chamber (having an approximately equal pressure to a discharge pressure) which is constructed in a back face side of an orbiting scroll, and a back pressure chamber (a pressure space having a lower pressure than the discharge pressure) by a seal means in a pressure manner, and uses a displacement type pump or a centrifugal pump for the oil feeding pump. If the oil feeding amount can be appropriately controlled, it is possible to improve an efficiency.
  • An object of the present invention is to provide a compressor having a high efficiency.
  • a scroll compressor provided with a compression chamber formed by engaging a fixed scroll and an orbiting scroll with each other, each of which has an end plate and a spiral lap provided in a rising manner in the end plate, a crank shaft making the orbiting scroll carry out a turning motion, an orbiting bearing portion engaging the orbiting scroll and an eccentric pin portion of the crank shaft so as to be movable in a direction of a rotating axis and be rotatable and provided in a back face of the orbiting scroll, a main bearing portion arranging a support portion which rotatably engages the crank shaft in a center portion of a frame member, a back pressure chamber zoned by a seal member which is arranged between the back face of the orbiting scroll and the frame member, and a high pressure chamber zoned in an inner side of the seal member being maintained at a pressure which is approximately equal to a discharge pressure, in which the back pressure chamber zoned in an outer side of the seal member is maintained at a pressure which is lower than the discharge pressure, wherein
  • the spiral shaped groove passage is formed in an inner peripheral surface of a boss portion in the back face of the orbiting scroll, and the throttle passage communicating with the back pressure chamber is arranged so as to be provided with such the throttle passage as to be capable of continuously feeding the lubricating oil to the back pressure chamber from the high pressure chamber.
  • the spiral shaped groove passage is formed in an outer peripheral surface of the orbiting bearing, and the throttle passage communicating with an end surface of a turning boss portion is arranged so as to be provided with such the throttle passage as to be capable of intermittently feeding the lubricating oil to the back pressure chamber from the high pressure chamber.
  • the spiral shaped groove passage is formed in an inner peripheral surface of a boss portion in a back face of the orbiting scroll, and the throttle passage communicating with an end surface of a turning boss portion is arranged so as to be provided with such the throttle passage as to be capable of intermittently feeding the lubricating oil to the back pressure chamber from the high pressure chamber.
  • the orbiting bearing employs a winding bush which is formed as a cylindrical shape by rolling a flat plate, and a groove which is diagonal in a state of the flat plate or a rectangular groove is applied in accordance with a press molding or an etching process.
  • a scroll compressor provided with a crank shaft having an eccentric pin portion, an orbiting scroll having an orbiting bearing to which the eccentric pin portion is inserted, a fixed scroll forming a compression chamber by being engaged with the orbiting scroll, and a volumetric capacity of the compression chamber being changed by pressing the orbiting scroll to the fixed scroll on the basis of a pressure of a back pressure chamber and turning the orbiting scroll on the basis of a rotation of the crank shaft so as to compress a refrigerant, wherein a high pressure chamber is formed between an end surface of the eccentric pin portion and a back face of the orbiting scroll, a throttle passage is provided between the eccentric pin portion and the orbiting bearing, and the orbiting scroll is provided with a discharge passage which introduces an oil to the back pressure chamber from the high pressure chamber via the throttle passage.
  • the throttle passage is formed as a spiral shape.
  • FIG. 1 is a view of a whole structure of a scroll compressor in accordance with a first embodiment
  • FIG. 2 is an enlarged view in the vicinity of a boss portion of an orbiting scroll in accordance with the first embodiment
  • FIG. 3 is an explanatory view of an effect in connection with an oil feeding amount of a back pressure chamber
  • FIG. 4 is an explanatory view of an effect in connection with an efficiency
  • FIG. 5 is an enlarged view in the vicinity of a boss portion of an orbiting scroll in accordance with a second embodiment
  • FIG. 6 is an enlarged view in the vicinity of a boss portion of an orbiting scroll in accordance with a third embodiment
  • FIG. 7 is an enlarged view in the vicinity of a boss portion of an orbiting scroll in accordance with a fourth embodiment
  • FIG. 8 is a cross sectional view of an assembled state of the boss portion of the orbiting scroll in accordance with the first embodiment
  • FIG. 9 is a cross sectional view of an assembled state of the boss portion of the orbiting scroll in accordance with the second embodiment.
  • FIG. 10 is an expansion plan view before rolling an orbiting bearing in accordance with a fifth embodiment.
  • FIG. 11 is an enlarged view in the vicinity of a boss portion of an orbiting scroll in accordance with a conventional art.
  • FIG. 1 and FIG. 2 A description will be given in detail of a scroll compressor which shows a first embodiment in accordance with the present invention, with reference to FIG. 1 and FIG. 2 . A description will be given of a whole structure of the scroll compressor showing the first embodiment in accordance with the present invention.
  • a scroll compressor 1 is constructed by storing a compression mechanism portion 2 and a driving portion 3 within a sealed container 100 .
  • the compression mechanism portion 2 is constructed by a fixed scroll 110 , an orbiting scroll 120 and a frame 160 .
  • the fixed scroll 110 has an end plate 110 b and a spiral lap 110 a which is provided in a rising manner so as to be vertical to the end plate 110 b, has a discharge port 110 e in a center portion of the lap, and is fixed to the frame 160 via a plurality of bolts.
  • the orbiting scroll 120 has an end plate 120 b and a spiral lap 120 a which is provided in a rising manner so as to be vertical to the end plate 120 b, and is constructed in a back face side of the end plate 120 b by a boss portion 120 e and a boss portion end surface 120 f.
  • a compression chamber 130 constructed by engaging the fixed scroll 110 and the orbiting scroll 120 carries out such a compression motion that a volumetric capacity thereof is reduced on the basis of a turning movement of the orbiting scroll 120 .
  • a working fluid is sucked into the compression chamber 130 from a suction port 140 in connection with the turning movement of the orbiting scroll 120 , and the sucked working fluid is discharged to a discharge space 136 within the sealed container 100 from the discharge port 110 e of the fixed scroll 110 via a compression stroke, and is further discharged from the sealed container 100 via a discharge port 150 .
  • a space within the sealed container 100 is kept at a discharge pressure.
  • the compressor mentioned above is called as a so-called high pressure chamber type.
  • the driving portion 3 making the orbiting scroll 120 carry out a turning movement is constructed by a stator 108 and a rotor 107 , a crank shaft 101 , an Oldham's coupling 134 which corresponds to a main part of an autorotation preventing mechanism of the orbiting scroll 120 , a frame 160 , a main bearing 104 , an auxiliary bearing 105 , and an orbiting bearing 103 .
  • the crank shaft 101 is structured such as to be integrally provided with a main shaft portion 101 b and an eccentric pin portion 101 a.
  • the main bearing 104 and the auxiliary bearing 105 are structured such as to rotatably engage the crank shaft 101 .
  • the orbiting bearing 103 is provided in the boss portion 120 e of the orbiting scroll in such a manner as to engage the eccentric pin portion 101 a of the crank shaft 101 so as to be movable in a direction of a rotating axis and be rotatable.
  • the main bearing 104 and the auxiliary bearing 105 which rotatably engage the crank shaft are arranged in a side of the compression mechanism portion 2 which is constructed by the stator 108 and the rotor 107 and a side of an oil reservoir portion 131 , respectively.
  • a sliding bearing is used in the main bearing 104 in the vicinity of the side of the compression mechanism portion 3 , however, a rolling bearing may be used.
  • the auxiliary bearing 105 in the vicinity of the oil reservoir portion 131 may employ a rolling bearing which can be adapted to a used condition or the other spherical bearing members, in addition to the illustrated sliding bearing.
  • the Oldham's coupling 134 is arranged in a back pressure chamber 180 which is constructed by the orbiting scroll 120 and the frame 160 , and is an autorotation preventing member of the fixed scroll 110 and the orbiting scroll 120 .
  • One set of two sets of orthogonal key portions which are formed in the Oldham's coupling 134 slides on a key groove which is constructed in the frame 160 , and the remaining one set slides on a key groove which is constructed in the back face side of the orbiting scroll 120 .
  • FIG. 2 is an enlarged view (a portion A in FIG. 1 ) in the vicinity of the high pressure chamber and the back pressure chamber in FIG. 1 .
  • a space constructed in the back face side of the orbiting scroll 120 is a space which is constructed by being surrounded by the orbiting scroll 120 , the frame 160 and the fixed scroll 110 .
  • the separating means of the high pressure chamber and the back pressure chamber is structured such as to be provided with a boss portion end surface 120 f in the back face of the orbiting scroll, a frame end surface portion 164 which faces thereto, a ring-like groove 161 which is constructed in the end surface portion 164 , and a seal member 172 which is arranged in the ring-like groove 161 .
  • the boss portion end surface 120 f is a seal surface which comes into contact with the seal member 172 .
  • the seal member 172 is a sealing means separating the back pressure chamber 180 and the high pressure chamber 181 in a pressure manner.
  • the high pressure chamber 181 is formed between an end surface of the eccentric pin portion 101 a of the crank shaft 101 and a back face of the orbiting scroll 120 .
  • the high pressure chamber 181 seals a lubricating oil which is discharged from the orbiting bearing 103 , the main bearing 104 and a thrust bearing 204 by a seal member 172 , and comes to a pressure space at an approximately discharge pressure while being exposed to a boosting action caused by a pumping action and a depressing action at a time of passing through the bearing portion and the gap portion.
  • the lubricating oil in the high pressure chamber 181 is depressurized by passing through a groove 200 a which corresponds to a spiral shaped throttle passage arranged in an outer peripheral surface of the boss portion 120 e and the orbiting bearing 103 , and lubricating oil is continuously fed to the back pressure chamber 180 through a discharge passage 201 which is communicated with the back pressure chamber 180 .
  • the discharge passage 201 introduces the lubricating oil to the back pressure chamber 180 from the high pressure chamber 181 via the throttle passage, that is, the groove 200 a.
  • the discharge passage 201 is provided in the orbiting scroll 120 .
  • the spiral formed groove 200 a can be formed only by forming the groove 200 a on an open outer peripheral surface of the orbiting bearing 103 before being fitted between the members in which the outer peripheral surface of the boss portion 120 e and the inner peripheral surface of the orbiting bearing 103 are fitted to each other, and carrying out the fitting of the orbiting bearing 103 to the boss portion 120 e.
  • the orbiting bearing 103 is constructed as a cylindrical member, a process of the spiral formed groove 200 a can be carried out by a comparatively easy turning machine process or the like. Therefore, a low cost can be achieved.
  • the drawing shows a relationship between a rotational frequency and an amount ratio of oil supply.
  • the amount ratio of oil supply on the basis of an oil feeding amount under a rated condition (a rotational frequency: 60 Hz).
  • a rotational frequency 60 Hz.
  • the structure in accordance with the present embodiment is of the type which depends on the pressure difference, and can retain the oil feeding amount constant in a range from the low speed condition to the high speed condition, it is possible to increase the oil feeding amount under the low speed condition without coming to an excessive oil feeding amount in comparison with the conventional one under the high speed condition.
  • FIG. 4 describes an efficiency and an effect in accordance with the present embodiment.
  • the present drawing shows a compressor efficiency ratio between the present embodiment and the conventional structure in a half-load cooling condition and a rated cooling condition under an APF condition.
  • the compressor efficiency ratio is based on the conventional efficiency.
  • the half-load cooling condition having a high rate of contribution can improve the efficiency 2% more than the conventional oil feeding system by the small hole, and approximately the same efficiency can be maintained under the rated cooling condition. Accordingly, it is possible to achieve the scroll compressor in which an energy compressor efficiency ratio is good all year.
  • the throttle passage which can continuously feed the lubricating oil from the high pressure chamber to the back pressure chamber is provided by arranging the discharge passage which communicates with the spiral shaped groove and the back pressure chamber between the orbiting scroll boss portion and the orbiting bearing.
  • the structure is made such that the throttle passage which can continuously feed the lubricating oil from the high pressure chamber to the back pressure chamber is provided by arranging the throttle passage which communicates with the spiral shaped groove and the back pressure chamber between the orbiting scroll boss portion and the orbiting bearing.
  • the spiral shaped groove passage having a predetermined length extends along the outer peripheral surface of the orbiting bearing, and the high pressure chamber and the back pressure chamber are communicated via the throttle passage.
  • FIG. 5 is a cross sectional view in the vicinity of an orbiting scroll boss portion.
  • FIG. 9 shows a cross sectional view of an assembled state in the vicinity of the boss portion of a back face of the orbiting scroll.
  • the other than the installing means of the spiral shaped groove arranged in the orbiting scroll boss portion is the same as the first embodiment, and a description will be given of only a different portion.
  • the structure is made such as to be provided with a throttle passage which can continuously feed the lubricating oil from the high pressure chamber 181 to the back pressure chamber 180 by forming a spiral shaped groove 200 b in an outer peripheral surface of the boss portion 120 e of the orbiting bearing 103 , and arranging the discharge passage 201 which communicates with the back pressure chamber 180 .
  • the throttle passage of the spiral formed groove 200 b can be formed only by forming the spiral shaped groove 200 b on the inner peripheral surface of the boss portion 120 e before being fitted between the members in which the outer peripheral surface of the boss portion 120 e and the inner peripheral surface of the orbiting bearing 103 are fitted to each other, and carrying out the fitting of the orbiting bearing 103 to the boss portion 120 e.
  • a process of the spiral formed groove 200 b on the inner peripheral surface of the turning boss portion can be carried out by a comparatively easy turning machine process or the like, a low cost can be achieved.
  • FIG. 6 shows a cross sectional view in the vicinity of the boss portion of the back face of the orbiting scroll.
  • the other than the discharge passage arranged in the orbiting scroll boss portion is the same as the first embodiment, and a description will be given of only a different portion.
  • the structure is made such that the spiral shaped groove 200 a is formed on the outer peripheral surface of the boss portion 120 e and the orbiting bearing 103 , and a throttle passage 202 communicating with the boss portion end surface 120 f is arranged, whereby if it reciprocates astride the seal member 172 , the lubricating oil fed to the throttle passage 202 can be intermittently fed to the back pressure chamber 180 from the high pressure chamber 181 .
  • the intermediate oil feeding means such as the third embodiment
  • the continuous oil feeding means such as the first embodiment
  • the same depressurizing effect can be obtained even if a cross sectional area of the spiral shaped groove passage is further enlarged, it is possible to enlarge a dimensional tolerance of the cross sectional area of the spiral shaped groove passage. If the cross sectional area of the passage is enlarged, it is possible to suppress a dispersion of the oil feeding amount in comparison with the first embodiment, it is possible to further simplify a workability, and a cost reduction can be achieved.
  • the present embodiment is structured such that the throttle passage communicating with the spiral shaped groove and the end surface of the turning boss portion is arranged between the orbiting scroll boss portion and the orbiting bearing, and reciprocates astride the sealing means which zones the high pressure chamber and the back pressure chamber, whereby the throttle passage can intermittently feed the lubricating oil.
  • the constructing means mentioned above since the same depressurizing effect can be obtained even if the cross sectional area of the passage is enlarged further in comparison with the continuous oil feeding means in accordance with the first invention, it is possible to hold down the dispersion of the oil feeding amount even if the dimensional tolerance of the cross sectional area of the passage is enlarged.
  • FIG. 7 shows a cross sectional view in the vicinity of the boss portion of the back face of the orbiting scroll.
  • the structure is made such that the spiral shaped groove 200 b is formed on the inner peripheral surface of the orbiting bearing 103 and the boss portion 120 e, and the throttle passage 202 communicating with the boss portion end surface 120 f is arranged, whereby if it reciprocates astride the seal member 172 , the lubricating oil fed to the throttle passage 202 can be intermittently fed to the back pressure chamber 180 from the high pressure chamber 181 .
  • a winding bush showing a fifth embodiment in accordance with the present invention is expanded to a flat plate shape with reference to FIG. 10 .
  • a cylindrical bush shape is formed by rolling a flat plate so as to wind as a cylindrical shape.
  • the diagonal groove 200 c comes to the groove 200 b and the rectangular groove 200 d can form the same throttle passage as the groove 200 b, by roll forming the flat plate.
  • the structure is made such that the sealing means sealing the high pressure chamber in the center portion of the back face boss portion of the orbiting scroll and the back pressure chamber (the low pressure chamber) formed by the internal space of the outer periphery is provided, the spiral shaped passage groove is provided between the inner peripheral surface of the boss portion in the back face of the orbiting scroll and the outer peripheral surface of the orbiting bearing, and the lubricating oil in the high pressure chamber can be continuously or intermittently fed to the back pressure chamber while being depressurized within the spiral shaped throttle passage.
  • the spiral shaped groove passage is installed between the inner peripheral surface of the turning boss portion and the outer peripheral surface of the orbiting bearing, it is possible to enlarge the cross sectional area at such a degree as to be set longer than the length of the spiral throttle passage in the end plate surface of the orbiting scroll, and it is possible to hold down the dispersion of the oil feeding amount even if the diametrical tolerance is enlarged.
  • the compressor having the lower cost can be provided in accordance with the enlargement of the diametrical tolerance.
  • the sealing means is provided in the end surface of the back face boss portion of the orbiting scroll, and is structured such as to seal the high pressure chamber in the center portion of the back face boss portion of the orbiting scroll and the back pressure chamber formed by the internal space of the outer periphery, it is not necessary to form the high pressure oil reservoir. Accordingly, since the orbiting scroll carried out the turning movement, the lubricating oil having the high pressure is not agitated, and it is possible to reduce the agitating loss, whereby it is possible to provide a compressor having a high efficiency.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
US13/372,780 2011-03-08 2012-02-14 Scroll Compressor Abandoned US20120230853A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2011049758A JP5380482B2 (ja) 2011-03-08 2011-03-08 スクロール圧縮機
JP2011-049758 2011-03-08

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US20120230853A1 true US20120230853A1 (en) 2012-09-13

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US (1) US20120230853A1 (enrdf_load_stackoverflow)
JP (1) JP5380482B2 (enrdf_load_stackoverflow)
CN (1) CN102678546B (enrdf_load_stackoverflow)
IN (1) IN2012DE00361A (enrdf_load_stackoverflow)

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US10718329B2 (en) 2015-05-19 2020-07-21 Hitachi-Johnson Controls Air Conditiong, Inc. Scroll compressor
CN114033694A (zh) * 2021-12-15 2022-02-11 广东美的环境科技有限公司 节流装置、涡旋压缩机及温控设备

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JP6022375B2 (ja) * 2013-02-21 2016-11-09 ジョンソンコントロールズ ヒタチ エア コンディショニング テクノロジー（ホンコン）リミテッド スクロール圧縮機
US9222475B2 (en) 2013-03-18 2015-12-29 Lg Electronics Inc. Scroll compressor with back pressure discharge
JP6165576B2 (ja) 2013-09-30 2017-07-19 株式会社日立産機システム スクロール式流体機械
JP6679399B2 (ja) * 2016-04-27 2020-04-15 日立ジョンソンコントロールズ空調株式会社 スクロール圧縮機
CN107605726B (zh) * 2017-09-04 2023-07-14 珠海格力电器股份有限公司 涡旋压缩机及具有其的空调器
KR20220153923A (ko) * 2021-05-12 2022-11-21 한온시스템 주식회사 스크롤 압축기
CN116201733B (zh) * 2023-01-04 2024-11-05 珠海格力节能环保制冷技术研究中心有限公司 压缩机
CN118391265B (zh) * 2024-06-27 2024-09-13 珠海凌达压缩机有限公司 涡旋压缩机、空调器

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