WO2016052503A1 - Compresseur à spirales et dispositif à cycle de réfrigération l'utilisant - Google Patents

Compresseur à spirales et dispositif à cycle de réfrigération l'utilisant Download PDF

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Publication number
WO2016052503A1
WO2016052503A1 PCT/JP2015/077515 JP2015077515W WO2016052503A1 WO 2016052503 A1 WO2016052503 A1 WO 2016052503A1 JP 2015077515 W JP2015077515 W JP 2015077515W WO 2016052503 A1 WO2016052503 A1 WO 2016052503A1
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WIPO (PCT)
Prior art keywords
space
oil
scroll
chamber
pressure
Prior art date
Application number
PCT/JP2015/077515
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English (en)
Japanese (ja)
Inventor
近野　雅嗣
太田原　優
中村　聡
長谷川　修士
泰典 中野
坪野　勇
Original Assignee
日立アプライアンス株式会社
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.)
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Application filed by 日立アプライアンス株式会社 filed Critical 日立アプライアンス株式会社
Priority to CN201580052774.1A priority Critical patent/CN106795881B/zh
Priority to US15/511,323 priority patent/US20170306951A1/en
Publication of WO2016052503A1 publication Critical patent/WO2016052503A1/fr

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    • 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
    • F04C18/0261—Details of the ports, e.g. location, number, geometry
    • 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
    • F04C27/00—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids
    • 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
    • F04C27/00—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids
    • F04C27/005—Axial sealings for working fluid
    • 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
    • F04C29/021—Control systems for the circulation of the lubricant
    • 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
    • F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/04—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type

Definitions

  • the present invention relates to a scroll compressor used in a refrigeration cycle and a refrigeration cycle apparatus using the same, and in particular, a first space having a pressure close to a discharge pressure formed at the center of the rear surface of the orbiting scroll, and this
  • a scroll compressor including a second space which is a pressure between a discharge pressure and a suction pressure provided on the outer peripheral side of the first space.
  • Examples of scroll compressors used in refrigeration cycle apparatuses for refrigeration and air conditioning include those described in Japanese Patent Application Laid-Open No. 2011-58439 (Patent Document 1).
  • Patent Document 1 an end plate (base plate, end plate), a fixed scroll and a turning scroll having a spiral wrap standing on the end plate, and the fixed scroll and the turning scroll are meshed with each other.
  • a compression chamber formed; a crankshaft for orbiting the orbiting scroll; and a rear boss portion of the orbiting scroll, the orbiting scroll being axially movable relative to an eccentric pin portion of the crankshaft;
  • a orbiting bearing for rotatably supporting, a stationary frame provided so as to face the back side of the orbiting scroll, a main bearing provided on the frame and rotatably supporting the crankshaft,
  • a seal member that seals between the back side of the orbiting scroll and the frame, and a high-pressure hydraulic chamber and an outer periphery on the inner periphery defined by the seal member Back pressure chamber, and the high pressure hydraulic chamber is supplied with lubricating oil having a pressure substantially equal to the discharge pressure so as to be substantially maintained at the discharge pressure, and the back pressure chamber is maintained at a pressure lower than the discharge pressure.
  • a small hole is provided in the back portion of the orbiting scroll facing the seal member or the frame, and the small hole straddles the sealing means with the orbiting motion of the orbiting scroll.
  • An oil supply means for supplying the oil in the high pressure hydraulic chamber to the back pressure chamber side so as to open alternately on both the side and the back pressure chamber side, and the orbiting scroll or the frame.
  • a scroll compressor including an oil supply passage that communicates a pressure chamber and supplies oil in a high-pressure hydraulic chamber to the back pressure chamber with a differential pressure.
  • Patent Document 2 discloses a non-orbiting scroll (fixed scroll) having an end plate (base plate) and a spiral body (lap) standing on the end plate (end plate), an end plate (end plate), A orbiting scroll standing up therewith, and a revolving scroll which meshes with the non-orbiting scroll to form a suction chamber or a compression chamber between the non-orbiting scroll and the non-orbiting scroll.
  • a back pressure chamber for applying a pressing force to the back pressure chamber, a back pressure chamber fluid inflow means for allowing fluid to flow into the back pressure chamber to maintain the pressure of the back pressure chamber, and a fluid flowing into the back pressure chamber
  • a scroll compressor provided with a back pressure chamber fluid outflow means or the like for allowing the air to flow into the suction chamber or the compression chamber is described.
  • the back pressure chamber fluid outflow means controls the back pressure chamber fluid outflow path connecting the back pressure chamber and the suction chamber or the compression chamber to control the differential pressure across the back and forth.
  • a pressure control valve, a throttle channel part, and an intermittent channel part intermittently communicating with the orbiting movement of the orbiting scroll member are described in series.
  • JP 2012-92773 A includes a fixed scroll having an end plate (base plate) and a scroll wrap erected on the end plate, and a scroll plate erected on the end plate, A orbiting scroll that forms a compression chamber with the fixed scroll by meshing with the fixed scroll, and a back pressure chamber that applies an attractive force to the fixed scroll to the orbiting scroll; and the back pressure A scroll compressor having an oil supply passage for introducing oil on the discharge side of the compressor into the chamber, comprising a back pressure valve that communicates with the back pressure chamber and the compression chamber after the start of closing and opens and closes by a differential pressure before and after , Communicating with the compression chamber communication passage for controlling the pressure of the back pressure chamber by allowing the oil in the back pressure chamber to flow out to the compression chamber, and the suction region leading to the back pressure chamber and the compression chamber, and The condensation chamber is configured not to communicate, that the oil of the back pressure chamber and a suction zone communicating passage for supplying to said suction areas are described.
  • the thing of the said patent document 2 becomes a structure into which most of the oil supplied to the bearing part flows in into a back pressure chamber, and since all the oil of a back pressure chamber flows into a suction chamber after that, a suction chamber A very large amount of oil required for the bearing flows into the cylinder, and much more oil flows into the suction chamber than that of Patent Document 1, so that the suction gas is heated and the heating loss is further increased.
  • a large amount of oil is supplied to the compression chamber, no consideration is given to the possibility of causing oil compression.
  • the thing of the said patent document 3 also becomes the structure into which most of the oil supplied to the bearing part flows into a back pressure chamber similarly to the said patent document 2.
  • this Patent Document 3 by providing a compression chamber communication passage in addition to the suction region communication passage, a part of the oil in the back pressure chamber can be directly supplied to the compression chamber without going through the suction chamber.
  • the amount of oil supplied from the back pressure chamber to the suction chamber can be made smaller than that in Patent Document 2.
  • the amount of oil supplied to the suction chamber can be reduced from that of Patent Document 2, but the amount of oil required for the suction chamber is reduced. It is difficult to avoid much more oil flowing into the suction chamber.
  • the amount of oil required in the bearing portion is much larger, for example, about 10 times the amount of oil required in the suction chamber or the compression chamber, but most of the oil supplied to the bearing portion is in the back pressure chamber. Since it flows in, it cannot be avoided that the amount of oil supply to the suction chamber inevitably increases. For this reason, it cannot be avoided that the suction gas is heated and the heating loss increases. In addition, since a large amount of oil is supplied to the compression chamber from the back pressure chamber and merges with the oil from the suction chamber, the amount of oil supplied to the compression chamber may increase and cause oil compression. This is the same as 2 and no consideration is given to these issues.
  • An object of the present invention is to provide a scroll compressor capable of controlling the amount of oil supplied to the bearing portion, the amount of oil supplied to the suction chamber, and the amount of oil supplied to the compression chamber, respectively, and realizing an appropriate amount of oil supply to each
  • the object is to obtain a refrigeration cycle apparatus using this.
  • the present invention provides a fixed scroll having a spiral wrap standing on a base plate and a swivel having a spiral wrap standing on an end plate and meshing with the fixed scroll to make a swivel motion.
  • a scroll compressor configured to form a suction chamber and a compression chamber by orbiting the orbiting scroll with respect to the fixed scroll.
  • a second space serving as a pressure between the first space, a first oil leakage path for leaking a part of oil in the first space to the second space, and most of the oil in the first space.
  • Sealed capacity An oil return passage for returning to the bottom of the container, a second oil leakage path for allowing a part of the oil in the second space to leak into the suction chamber, the pressure in the compression chamber, and the second space
  • a third oil leakage path for adjusting the pressure in the second space so as to allow the oil in the second space to escape to the compression chamber in accordance with the difference between the pressure and the pressure in the second space.
  • Another feature of the present invention resides in a refrigeration cycle apparatus for refrigeration and air conditioning constructed using the scroll compressor constructed as described above.
  • a scroll compressor capable of controlling the amount of oil supplied to the bearing portion, the amount of oil supplied to the suction chamber, and the amount of oil supplied to the compression chamber, respectively, and realizing an appropriate amount of oil supply, and There exists an effect which can obtain the refrigerating cycle device using this.
  • FIG. 1 is a longitudinal sectional view showing a first embodiment of a scroll compressor according to the present invention.
  • FIG. 2 is a diagram showing a state in which a fixed scroll and a turning scroll shown in FIG. 1 are engaged with each other, as viewed from the II-II direction in FIG. The perspective view which looked at the turning scroll shown in FIG. 1 from upper direction.
  • FIG. 9 is a diagram for explaining another example of the orbiting scroll, and is a perspective view corresponding to FIG. 2.
  • FIG. 5 is a diagram for explaining Example 2 of the scroll compressor according to the present invention and corresponding to FIG. 4. It is a figure explaining Example 3 of this invention, and is the refrigerating-cycle block diagram which shows the example of the refrigerating-cycle apparatus using a scroll compressor.
  • FIG. 1 is a longitudinal sectional view showing a first embodiment of the scroll compressor of the present invention
  • FIG. 2 is a view showing a state where the fixed scroll and the orbiting scroll shown in FIG. 1 are engaged with each other, from the direction II-II in FIG.
  • FIG. 3 is a perspective view of the orbiting scroll shown in FIG. 1 as viewed from above
  • FIG. 4 is an enlarged cross-sectional view of the periphery of the back pressure valve in the scroll compressor shown in FIG. 1, and FIG. It is a figure to explain and is a perspective view equivalent to FIG.
  • the scroll compressor 1 is configured by housing a compression mechanism section 2 and a motor section 16 in a case (sealed container) 9.
  • the orbiting scroll 8 is meshed with the fixed scroll 7 fixed to the frame 17 to form a compression chamber 13, and the rotation of the motor section 16 causes the crankshaft (rotary shaft) 10 to pass through.
  • the crankshaft (rotary shaft) 10 causes the crankshaft (rotary shaft) 10 to pass through.
  • the working fluid is sucked into the suction chamber 20 (see FIG. 3) from the suction port 14, and the sucked working fluid passes through the compression stroke in the compression chamber 13 and is discharged from the discharge port 15 into the case 9. It is discharged into the discharge space 54.
  • the working fluid discharged into the discharge space 54 flows into the motor chamber 52 through a passage (not shown) formed in the outer periphery of the fixed scroll 7 and the outer periphery of the frame 17, and then from the discharge pipe 6 to the case. 9 is configured to be discharged outside.
  • the fixed scroll 7 is a disk-shaped base plate 7a, a wrap 7b erected on the base plate 7a in a spiral shape, and is positioned on the outer peripheral side of the base plate 7a, and is substantially the same height as the front end surface of the wrap 7b. And a support portion 7d provided in a cylindrical shape so as to surround the wrap 7b. Since the surface of the base plate 7a on which the wrap 7b is erected is located between the wraps 7b, it is called a tooth bottom 7c.
  • the end plate surface 7 e is a sliding surface in which the support portion 7 d of the fixed scroll 7 is in contact with the end plate 8 a of the orbiting scroll 8.
  • the fixed scroll 7 has the support portion 7d fixed to the frame 17 with bolts or the like, and the frame 17 integrally coupled with the fixed scroll 7 is fixed to the case 9 by fixing means such as welding.
  • the orbiting scroll 8 is disposed so as to face the fixed scroll 7, and the wrap 7 b of the fixed scroll 7 and the wrap 8 b of the orbiting scroll 8 are engaged with each other, and are provided in the frame 17 so as to be orbitable.
  • the orbiting scroll 8 includes a spiral wrap 8b erected from a tooth bottom 8c, which is the surface of a disc-shaped end plate 8a, and an orbiting boss portion (boss portion) 8d provided at the center of the rear surface of the end plate 8a.
  • the surface of the outer peripheral portion of the end plate 8 a that contacts the fixed scroll 7 is the end plate surface 8 e of the orbiting scroll 8.
  • the tip end portion (lap tooth tip) of the wrap 8b of the orbiting scroll 8 is configured to face the tooth bottom 7c of the fixed scroll 7 with a small gap.
  • the tip end portion (wrap tooth tip) of the wrap 7b of the fixed scroll 7 is also configured to face the tooth bottom 8c of the orbiting scroll 8 with a minute gap.
  • An oil sump 53 for storing lubricating oil (refrigerating machine oil) is provided at the bottom of the case 9 having a sealed container structure that accommodates the compression mechanism section 2 and the motor section 16.
  • the motor unit 16 includes a rotor 16a and a stator 16b, and the crankshaft 10 is integrally fixed to the rotor 16a.
  • the crankshaft 10 is rotatably supported by the frame 17 via the main bearing 5 and is coaxial with the central axis of the fixed scroll 7.
  • An eccentric crank portion 10 a is provided at the tip of the crankshaft 10, and this crank portion 10 a is inserted into the orbiting bearing 11 provided in the orbiting boss portion 8 d of the orbiting scroll 8.
  • the crankshaft 10 is configured to be able to turn as the crankshaft 10 rotates.
  • the center axis of the orbiting scroll 8 is decentered by a predetermined distance with respect to the center axis of the fixed scroll 7.
  • the wrap 8b of the orbiting scroll 8 is overlapped with the wrap 7b of the fixed scroll 7 while being shifted by a predetermined angle (generally 180 degrees) in the circumferential direction.
  • Reference numeral 12 denotes an Oldham ring for relatively turning the orbiting scroll 8 with respect to the fixed scroll 7 while restraining the orbiting scroll 8 from rotating.
  • FIG. 2 is a diagram for explaining the meshing state of the fixed scroll 7 and the orbiting scroll 8, and is a view seen from the II-II direction of FIG. 1. Therefore, the orbiting scroll wrap 8b is shown in section in the orbiting scroll 8. A portion corresponding to the outer periphery of the end plate 8a of the orbiting scroll 8 is indicated by a two-dot chain line (imaginary line).
  • a plurality of crescent-shaped compression chambers 13 are formed between the fixed scroll wrap 7b and the turning scroll wrap 8b.
  • Reference numeral 20 denotes a suction chamber, which is a space in the middle of sucking fluid. The suction chamber 20 becomes the compression chamber 13 when the phase of the orbiting motion of the orbiting scroll 8 advances and the closing of the fluid is completed.
  • the suction port 14 is provided in the fixed scroll 7 as shown in FIGS. 1 and 2.
  • the suction port 14 is formed on the outer peripheral side of the base plate 7 a of the fixed scroll 7 so as to communicate with the suction chamber 20.
  • the discharge port 15 is formed near the spiral center of the base plate 7a of the fixed scroll 7 so as to communicate with the compression chamber 13 on the innermost peripheral side.
  • the orbiting scroll 8 orbits around the central axis of the fixed scroll 7 with a predetermined orbiting radius.
  • the working fluid sucked from the suction port 14, for example, refrigerant gas (hereinafter also simply referred to as fluid) circulating in the refrigeration cycle is sequentially compressed in each compression chamber 13, and the compressed working fluid is discharged from the discharge chamber.
  • the gas is discharged from the port 15 into the discharge space 54 and, as described above, supplied from the discharge pipe 6 to, for example, a refrigeration cycle outside the compressor.
  • a positive displacement or centrifugal oil pump 21 is provided at the lower end of the crankshaft 10, and as the crankshaft 10 rotates, the oil pump 21 also rotates and accumulates in an oil sump 53 at the bottom of the case 9.
  • the obtained lubricating oil is sucked from the lubricating oil suction port 22 a of the oil supply pump case 22 and discharged from the discharge port 21 a of the oil supply pump 21.
  • the discharged lubricating oil passes through a through hole (oil supply hole) 3 formed in the axial direction in the crankshaft 10 and is sent to the space in the turning boss portion 8d at the upper end of the crank portion 10a.
  • a part of the lubricating oil flowing through the through hole 3 is sent to the auxiliary bearing 23 through a lateral hole 24 provided in the crankshaft 10, and after lubricating the auxiliary bearing 23, the oil at the bottom of the case 9 is supplied. Return to pool 53. Most of the other lubricating oil flowing through the through-hole 3 reaches the turning boss part space at the upper end of the crank part 10a, passes through the oil groove 57 provided on the outer peripheral surface of the crank part 10a, and the turning bearing 11. Lubricate.
  • This lubricating oil then lubricates the main bearing 5 provided at the lower part of the slewing bearing 11, and then passes through an oil return passage 26 constituted by an oil drain hole 26a and an oil drain pipe 26b, so that the bottom of the case 9 is The oil sump 53 is returned.
  • the space formed by the collar portion 34 and the seal member 32) will be collectively referred to as a first space 33.
  • the first space 33 is a space having a pressure close to the discharge pressure.
  • the lubricating oil flowing into the first space 33 for lubricating the main bearing 5 and the slewing bearing 11 passes through the oil drain hole 26a and the oil drain pipe 26b (oil return passage). Return to the oil sump 53 at the bottom of the case 9. Further, a part of the lubricating oil is used for sealing (sealing) such as lubrication of the Oldham ring 12, lubrication of the sliding portion between the fixed scroll 7 and the orbiting scroll 8, and gaps between the tips of the laps 7 b and 8 b.
  • the required amount is larger than that of the first space 33 via the first oil leakage path provided between the upper end surface of the seal member 32 and the end surface of the flange portion 34 of the turning boss portion 8d. It flows into the back pressure chamber 18 which is a second space provided on the outer peripheral side and serving as a pressure between the discharge pressure and the suction pressure.
  • the sealing member 32 is provided with a wave spring (not shown) in an annular groove 31 provided on a surface of the frame 17 facing the flange portion 34, and serves as a discharge pressure.
  • the back pressure chamber (second space) 18 which is an intermediate pressure between the suction pressure and the discharge pressure.
  • the first oil leakage path includes, for example, one or a plurality of radially long slits 60 (grooves) provided in the flange portion 34 of the turning boss portion 8d, and the seal member 32.
  • the slit 60 is intermittently disposed so as to straddle the seal member 32 by the orbiting motion of the orbiting scroll 8 so as to intermittently communicate the first space 33 and the back pressure chamber 18. It is configured.
  • the arrangement of the slit 60 is not limited to a configuration in which the seal member 32 is intermittently straddled with the orbiting motion of the orbiting scroll 8, and the seal member 32 may be always straddled.
  • one or a plurality of holes for example, one or more oil reservoirs (for example, circular grooves) are provided in the collar portion 34 of the orbiting boss portion.
  • a circular motion straddling the seal member 32 is performed in accordance with the swiveling motion.
  • the hole moves between the first space 33 and the back pressure chamber 18, the lubricating oil in the first space 33 is accumulated in the hole, and intermittently enters the back pressure chamber 18.
  • the oil can be transferred and discharged, and the oil in the first space 33 can be supplied to the back pressure chamber 18. In this way, the first oil leakage path may be configured.
  • a part of the lubricating oil that has flowed into the back pressure chamber 18 is configured to flow into the suction chamber 20 via a second oil leakage path to be described later.
  • it is also used for sealing between the compression chambers.
  • the remainder of the lubricating oil that has flowed into the back pressure chamber 18 is configured to flow into the compression chamber 13 via a third oil leakage path, which will be described later. It is used for sealing the gap between the tip and the like, and for sealing between the compression chambers.
  • a lap sliding surface, a lap tip clearance, and the like are passed from the first space 33 to the second space (back pressure chamber) 18 through the first oil leakage path.
  • Lubricating oil is leaked in an amount necessary for lubrication and sealing between the compression chambers, and the remaining lubricating oil is lubricated to the oil sump 53 through the oil draining hole 26a and the oil draining pipe 26b after lubricating the bearings. Can be returned. Therefore, in this embodiment, the amount of oil required for lubrication of each bearing portion and the amount of oil supplied to the back pressure chamber 18 can be controlled independently. Therefore, the amount of oil supplied to the back pressure chamber 18 can be minimized.
  • the lubricating oil flowing into the back pressure chamber 18 can be supplied to the suction chamber 20 through the second oil leakage path, and the remaining lubricating oil can be supplied to the third oil leakage. It supplies to the compression chamber 13 through a path. Therefore, since the amount of oil supplied to the suction chamber 20 and the compression chamber 13 can be minimized, the suction heating loss in the suction chamber 20 can be minimized, and in the compression chamber 13 Since it is possible to prevent oil compression and heating loss due to excessive supply of oil, a highly efficient and highly reliable scroll compressor can be realized.
  • 64 is an oil hole (groove) provided on the end plate surface 8e of the orbiting scroll 8 and serving as an oil reservoir.
  • This oil hole 64 is an orbiting motion of the orbiting scroll 8 as shown in FIG. Accordingly, the locus 65 shown in FIG. 2 is drawn, and the back pressure chamber (second space) 18 and the groove 66 communicating with the suction chamber 20 are intermittently communicated.
  • the oil in the back pressure chamber 18 (the pressure is an intermediate pressure between the discharge pressure and the suction pressure) is accumulated in the oil hole 64. Further, when the oil hole 64 communicates with the groove 66 (pressure is a suction pressure) as the orbiting scroll 8 rotates, the oil in the oil hole 64 passes through the groove 66 due to a pressure difference. It is introduced into the suction chamber 20. By repeating this action, the oil in the back pressure chamber 18 is sequentially transferred to the suction chamber 20. By adjusting the volume and number of the oil holes 64, the amount of oil supplied from the back pressure chamber 18 to the suction chamber 20 can be arbitrarily adjusted.
  • a back pressure chamber 18 serving as a pressure between the discharge pressure and the suction pressure is provided on the back side of the end plate 8a of the orbiting scroll 8, and the pulling force is canceled by the pressure (back pressure) of the back pressure chamber 18,
  • the orbiting scroll 8 is pressed against the fixed scroll 7. If the pressing force at this time is too large, the sliding loss between the end plate surface 8e of the orbiting scroll 8 and the end plate surface 7e of the fixed scroll 7 increases, and the compressor efficiency decreases.
  • the back pressure there is an optimum value for the back pressure. If the back pressure is too small, the hermeticity of the compression chamber is deteriorated and thermal fluid loss is increased. Therefore, maintaining the back pressure at an optimum value is important in improving the performance and reliability of the compressor.
  • the third oil leakage having a back pressure valve 61 for adjusting the back pressure in the back pressure chamber 18 is provided.
  • a path is provided in the support portion 7 d of the fixed scroll 7. The configuration of the third oil leakage path will be described in detail with reference to FIG. 4 which is an enlarged view showing the configuration around the back pressure valve 61 in FIG.
  • the third oil leakage path includes a back pressure valve inflow path (a space communicating with the back pressure chamber 18) 62a communicating the back pressure chamber 18 and the back pressure valve 61, and the back pressure valve 61.
  • a back pressure valve outflow passage (a space communicating with the compression chamber 13) 62c communicating with the compression chamber 13 and a space 62b accommodating the back pressure valve 61 are configured.
  • the back pressure valve 61 is provided with a valve 61a so as to partition the back pressure valve inflow passage 62a and the back pressure valve outflow passage 62c.
  • the valve 61a is provided to be pressed against the opening of the back pressure valve inflow passage 62a by a spring 61b fixed to the stopper 61c.
  • the valve 61a is configured such that the pressure in the back pressure valve inflow passage 62a, that is, the back pressure is introduced through the back pressure valve outflow passage 62c, that is, the pressure in the space 62b, that is, the pressure in the compression chamber, and the spring 61b.
  • the back pressure valve inflow path 62a and the back pressure valve outflow path 62c are communicated with each other by moving upward. That is, when the pressure in the back pressure chamber 18 becomes higher than a certain value, the back pressure valve 61 allows the fluid in the back pressure chamber 18 to escape to the compression chamber 13, and the back pressure in the back pressure chamber 18. Is adjusted to an appropriate value.
  • the oil that has flowed into the compression chamber 13 lubricates the lap sliding surface and the gap between the wrap tips, is used for sealing between the compression chambers, and the like, and is then discharged from the discharge port 15 into the discharge space 54.
  • a part of the discharged oil is discharged together with the refrigerant gas from the discharge pipe 6 to the refrigeration cycle, for example, and the rest is separated from the refrigerant gas in the case 9 and stored in the oil reservoir 53 at the bottom of the case.
  • the amount of oil supplied to each bearing portion and the amount of oil supplied to the back pressure chamber can be independently controlled by the first oil leakage path, and the backside by the second oil leakage path.
  • the back pressure valve outflow passage 62c communicates with the compression chamber 13 after the suction process is completed and compression is started. That is, the compression chamber 13 is a compression chamber in the middle of compression after the suction process is completed, and is a compression chamber isolated from the suction chamber 20. Further, as shown in FIG. 2, the back pressure valve outflow passage 62c is in a position where it alternately communicates with both the turning outer line chamber 13b and the turning inner line chamber 13a by the turning motion of the turning scroll. In addition, 63 shown in FIG. 4 is a stopcock for sealing and closing the edge part of the horizontal hole formed in order to provide the back pressure valve outflow path 62c.
  • the oil in the back pressure chamber 18 is compressed through the back pressure valve 61 without passing through the suction chamber 20. 13 can be supplied directly.
  • the amount of oil supplied to the compression chamber 13 is determined from the amount of oil supplied from the first space 33 to the back pressure chamber 18 by the first oil leakage path and from the back pressure chamber 18 by the second oil leakage path. This is the difference from the amount of oil supplied to the suction chamber 20. That is, oil is supplied from the first space 33 to the back pressure chamber 18 via the first oil leakage means, but only the amount determined by the second oil leakage path is sucked in the oil. The remaining oil is introduced into the compression chamber 13.
  • the amount of oil supplied to the suction chamber and the amount of oil supplied to the compression chamber can be controlled to appropriate amounts by adjusting the amount of oil supplied to each of the first oil leakage path and the second oil leakage path. It becomes possible.
  • the amount of oil required for sealing the compression chamber 13 is larger than the amount of oil required for sealing the suction chamber.
  • the amount of oil supplied in the first oil leakage path is set to the compression chamber.
  • the suction chamber 20 becomes excessively oiled and the suction heating loss increases.
  • the oil supply amount in the first oil leakage path is set to a low oil supply amount that is necessary for sealing the suction chamber 20, the compression chamber will become insufficiently oiled and the sealing effect by the oil will be reduced and leakage will occur. Loss increases.
  • each oil supply amount so that the amount of oil supplied by the first oil leak path is larger than the amount of oil supplied by the second oil leak path, the first oil leak path and the second oil leak path Since the difference in the amount of oil supply can be supplied to the compression chamber 13, the amount of oil supply to the compression chamber 13 can be reliably ensured.
  • the present embodiment is applied to a scroll compressor that uses a refrigerant that tends to be high temperature and has a heat insulation index greater than 1.09, such as R32, as the working fluid, the suction heating loss can be further reduced, and the efficiency is higher.
  • a scroll compressor can be obtained.
  • the second oil leakage path has been described by providing a circular oil hole (groove) 64 on the end plate surface 8 e of the orbiting scroll 8.
  • a circular oil hole (groove) 64 instead of the oil hole 64, a shallow slit (groove) 67 is formed, and the slit 67 communicates with the back pressure chamber 18 and the suction chamber 20 constantly or intermittently.
  • the oil in the back pressure chamber 18 may be introduced into the suction chamber 20 by a pressure difference so as to communicate with the groove 66. Even in this case, the amount of oil supply can be controlled by adjusting the depth, width, length, or number of the slits.
  • FIG. 6 is a diagram corresponding to FIG. 4 described above, and in FIG. 6, the portions denoted by the same reference numerals as those in FIGS. 1 to 5 described above indicate the same or corresponding portions.
  • the first oil leakage path allows the oil supply amount to each bearing portion and the oil supply amount to the back pressure chamber to be independently controlled.
  • the amount of oil supplied from the back pressure chamber 18 to the suction chamber 20 can be controlled independently by two oil leakage paths.
  • the second embodiment does not include a third oil leakage path for supplying oil from the back pressure chamber 18 to the compression chamber 13 via the back pressure valve 61 as shown in FIG.
  • the third oil leakage path is not provided in the support portion 7d of the fixed scroll 7, but by a back pressure hole 68 formed in the end plate 8a of the orbiting scroll 8, as shown in FIG. It is configured.
  • the back pressure hole 68 is provided in the orbiting scroll end plate 8a so as to communicate the back pressure chamber (second space) 18 with the compression chamber 13 after completing the suction process and starting the compression. ing. That is, the back pressure hole 68 is provided at a position communicating only with the compression chamber 13 isolated from the suction chamber 20. With the back pressure hole 68, the pressure in the back pressure chamber 18 can be maintained at a value close to the average pressure in the compression chamber 13.
  • each bearing is provided with the first oil leakage path, the second oil leakage path, and the back pressure hole 68 (third oil leakage path) in the same manner as in the first embodiment. It is possible to appropriately adjust the amount of oil supplied to each part, the suction chamber 20 and the compression chamber 13.
  • an appropriate amount of oil is realized by controlling the amount of oil supplied to the bearing portion, the amount of oil supplied to the suction chamber, and the amount of oil supplied to the compression chamber.
  • the oil (lubricating oil) leaking from the first to third oil leakage paths generally contains a refrigerant, but in the present invention, the oil containing the refrigerant is also described as oil. Yes.
  • FIG. 7 is a refrigeration cycle configuration diagram showing an example of a refrigeration cycle apparatus for refrigeration and air conditioning using the above-described scroll compressor of the present invention.
  • FIG. 7 1 is a scroll compressor, 43 is a four-way valve, 40 is an outdoor heat exchanger (condenser during cooling operation, evaporator during heating operation), and 41 is an electronic expansion valve.
  • An expansion valve 42 is an indoor heat exchanger (an evaporator during cooling operation and a condenser during heating operation), and these devices are sequentially connected by refrigerant piping to form a refrigeration cycle of the air conditioner.
  • any one of the scroll compressors described in the above embodiments is used as the scroll compressor 1.
  • the operating efficiency of the air conditioner can be significantly improved.
  • the year-round energy consumption efficiency (APF) of the machine can be greatly improved, and an air conditioner (refrigeration cycle apparatus) that is small in power consumption, has a wide operation range, and is easy to use can be obtained.
  • the outdoor heat exchanger 40 and the indoor heat exchanger 42 are applied to one air conditioner has been described, but a plurality of the indoor heat exchangers 42 are provided.
  • the present invention can be similarly applied to a multi-type air conditioner, and can also be applied to a refrigeration cycle apparatus such as a dedicated air conditioner or a refrigerator.
  • the amount of oil supplied to the bearing portion is required. Since it is possible to obtain an appropriate amount of oil supply only by the amount, a highly efficient scroll compressor and a refrigeration cycle apparatus for refrigeration and air conditioning using the scroll compressor can be obtained.
  • this invention is not limited to an above-described Example, Various modifications are included.
  • the above-described embodiments have been described in detail for easy understanding of the present invention, and are not necessarily limited to those having all the configurations described. Furthermore, it is possible to add, delete, and replace other configurations for a part of the configuration of each embodiment.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Rotary Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Abstract

Selon la présente invention, un compresseur à spirales est pourvu d'une spirale fixe et d'une spirale tournante, et en amenant la spirale tournante à tourner, une chambre d'aspiration et une chambre de compression sont formées. L'invention est en outre pourvue : d'un premier espace qui est formé au niveau de la partie centrale de surface arrière de la spirale tournante et dans lequel est acheminée de l'huile de lubrification dans une partie inférieure de réservoir étanche, de sorte que la pression dans l'espace s'approche d'une pression de refoulement ; d'un second espace qui est ménagé au niveau de la surface arrière de la spirale tournante davantage vers le côté périphérique extérieur que le premier espace, et dans lequel la pression atteint un niveau de pression situé entre la pression de refoulement et une pression d'aspiration ; d'un premier trajet d'infiltration d'huile qui permet qu'une partie de l'huile dans le premier espace s'infiltre dans le second espace ; d'un trajet d'écoulement de retour d'huile qui renvoie une partie importante de l'huile dans le premier espace vers la partie inférieure dans le réservoir étanche ; d'un deuxième trajet d'infiltration d'huile permettant qu'une partie de l'huile dans le second espace s'infiltre dans la chambre d'aspiration ; et d'un troisième trajet d'infiltration d'huile qui, en fonction de la différence entre la pression dans la chambre de compression et la pression dans le second espace, ajuste la pression dans le second espace par libération de l'huile présente dans le second espace dans la chambre de pression.
PCT/JP2015/077515 2014-09-30 2015-09-29 Compresseur à spirales et dispositif à cycle de réfrigération l'utilisant WO2016052503A1 (fr)

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CN201580052774.1A CN106795881B (zh) 2014-09-30 2015-09-29 涡旋压缩机及使用了该涡旋压缩机的冷冻循环装置
US15/511,323 US20170306951A1 (en) 2014-09-30 2015-09-29 Scroll compressor and refrigeration cycle apparatus using the same

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JP2014200554A JP6302813B2 (ja) 2014-09-30 2014-09-30 スクロール圧縮機及びこれを用いた冷凍サイクル装置
JP2014-200554 2014-09-30

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WO2019044326A1 (fr) * 2017-09-04 2019-03-07 パナソニックＩｐマネジメント株式会社 Compresseur
JP2020033881A (ja) * 2018-08-27 2020-03-05 日立ジョンソンコントロールズ空調株式会社 スクロール圧縮機及び冷凍空調装置
JP6773152B2 (ja) * 2019-02-28 2020-10-21 ダイキン工業株式会社 スクロール圧縮機
CN112483429A (zh) * 2019-09-12 2021-03-12 开利公司 离心压缩机和制冷装置
US11655820B2 (en) * 2020-02-04 2023-05-23 Aspen Compressor, Llc Horizontal rotary compressor with enhanced tiltability during operation
KR102512409B1 (ko) * 2021-02-15 2023-03-21 엘지전자 주식회사 스크롤 압축기
KR102454721B1 (ko) * 2021-02-19 2022-10-14 엘지전자 주식회사 스크롤 압축기
CN114215757B (zh) * 2021-12-17 2022-11-15 珠海格力电器股份有限公司 一种回油结构、压缩机及空调器
JP7253655B1 (ja) 2022-05-24 2023-04-06 日立ジョンソンコントロールズ空調株式会社 スクロール圧縮機及び冷凍サイクル装置

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JP6302813B2 (ja) 2018-03-28
CN106795881B (zh) 2018-07-31
CN108980036A (zh) 2018-12-11
CN106795881A (zh) 2017-05-31
JP2016070178A (ja) 2016-05-09
CN108980036B (zh) 2021-02-02
CN109026706B (zh) 2020-06-09
CN109026706A (zh) 2018-12-18

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