US20170306951A1 - Scroll compressor and refrigeration cycle apparatus using the same - Google Patents

Scroll compressor and refrigeration cycle apparatus using the same Download PDF

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Publication number
US20170306951A1
US20170306951A1 US15/511,323 US201515511323A US2017306951A1 US 20170306951 A1 US20170306951 A1 US 20170306951A1 US 201515511323 A US201515511323 A US 201515511323A US 2017306951 A1 US2017306951 A1 US 2017306951A1
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United States
Prior art keywords
space
oil
orbiting
scroll
chamber
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
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US15/511,323
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English (en)
Inventor
Masatsugu Chikano
Masaru Ohtahara
Satoshi Nakamura
Syuuji Hasegawa
Yasunori Nakano
Isamu Tsubono
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Hitachi Johnson Controls Air Conditioning Inc
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Hitachi Johnson Controls Air Conditioning Inc
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Assigned to JOHNSON CONTROLS-HITACHI AIR CONDITIONING TECHNOLOGY (HONG KONG) LIMITED reassignment JOHNSON CONTROLS-HITACHI AIR CONDITIONING TECHNOLOGY (HONG KONG) LIMITED ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: HASEGAWA, SYUUJI, CHIKANO, MASATSUGU, NAKAMURA, SATOSHI, NAKANO, YASUNORI, OHTAHARA, MASARU, TSUBONO, ISAMU
Publication of US20170306951A1 publication Critical patent/US20170306951A1/en
Assigned to HITACHI-JOHNSON CONTROLS AIR CONDITIONING, INC. reassignment HITACHI-JOHNSON CONTROLS AIR CONDITIONING, INC. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: JOHNSON CONTROLS-HITACHI AIR CONDITIONING TECHNOLOGY (HONG KONG) LIMITED
Abandoned legal-status Critical Current

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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 scroll compressor and, more particularly, to a scroll compressor including a first space, which has pressure close to discharge pressure, formed in a back surface center of an orbiting scroll and a second space, which has pressure between the discharge pressure and suction pressure, provided further on the outer circumference side than the first space.
  • Patent Literature 1 As a scroll compressor used in refrigeration cycle apparatuses for refrigeration, for air conditioning, and the like, there is a scroll compressor described in JP-A-2011-58439 (Patent Literature 1) .
  • the scroll compressor described in Patent Literature 1 includes a fixed scroll and an orbiting scroll including end plates (base plates or mirror plates) and a spiral wrap erected on the end plates, a compression chamber formed by meshing the fixed scroll and the orbiting scroll each other, a crankshaft for causing the orbiting scroll to perform an orbiting motion, an orbiting bearing provided in a back surface boss section of the orbiting scroll to support the orbiting scroll to be movable in the axial direction and rotatable with respect to an eccentric pin section of the crankshaft, a frame on a stationary side provided to be opposed to the back surface side of the orbiting scroll, a main bearing provided in the frame to rotatably support the crankshaft, a seal member that seals a space between the orbiting scroll back surface side and the frame, and a high
  • Lubricant having pressure substantially equal to the discharge pressure is supplied to the high-pressure hydraulic chamber and the high-pressure hydraulic chamber is maintained substantially at the discharge pressure.
  • the backpressure chamber is maintained at pressure lower than the discharge pressure.
  • a small hole is provided in an orbiting scroll back surface section or the frame in a portion opposed to the seal member. The small hole is alternately opened to both of the high-pressure hydraulic chamber side and the backpressure chamber side across the seal means according to the orbiting motion of the orbiting scroll.
  • the scroll compressor includes oil supplying means for supplying oil in the high-pressure hydraulic chamber to the backpressure chamber side and an oil supply path provided in the orbiting scroll or the frame to cause the high-pressure hydraulic chamber and the backpressure chamber to communicate and supply the oil in the high-pressure hydraulic chamber to the backpressure chamber side with differential pressure.
  • Patent Literature 2 JP-A-2005-163655 (Patent Literature 2) describes a scroll compressor including a non-orbiting scroll (a fixed scroll) including an end plate (a base plate) and a spiral body (a wrap) erected on the end plate, an orbiting scroll including an end plate (a mirror plate) and a spiral body erected on the end plate and meshing with the non-orbiting scroll to perform an orbiting motion to thereby form a suction chamber or a compression chamber between the orbiting scroll and the non-orbiting scroll, a backpressure chamber for applying a pressing force on the non-orbiting scroll to the orbiting scroll, backpressure chamber fluid inflow means for causing fluid to flow into the backpressure chamber in order to maintain the pressure of the backpressure chamber, and backpressure chamber fluid outflow means for causing the fluid flowed into the backpressure chamber to flow out to the suction chamber or the compression chamber.
  • a non-orbiting scroll a fixed scroll
  • an orbiting scroll including an end plate (a mirror plate) and
  • a backpressure control valve for controlling differential pressure between the front and the back of the backpressure control valve, a reduced channel section, and an intermittent channel section that intermittently communicates according to the orbiting motion of the orbiting scroll member are disposed in series in a backpressure chamber fluid outflow path that connects the backpressure chamber and the suction chamber or the compression chamber.
  • JP-A-2012-92773 (Patent Literature 3) describes a scroll compressor including a fixed scroll including a mirror plate (a base plate) and a scroll wrap erected on the mirror plate, an orbiting scroll including a mirror plate and a scroll wrap erected on the mirror plate and meshed with the fixed scroll to perform an orbiting motion to thereby form a compression chamber between the orbiting scroll and the fixed scroll, a backpressure chamber that applies an attracting force on the fixed scroll to the orbiting scroll, and an oil supply path for leading oil on a compressor discharge side into the backpressure chamber.
  • the scroll compressor includes a compression chamber communication path including a backpressure valve that is caused to communicate with the backpressure chamber and the compression chamber after a closing start and opens and closes with differential pressure between the front and the back of the backpressure valve, the compression chamber communication path causing oil in the backpressure chamber to flow out to the compression chamber and controlling the pressure of the backpressure chamber and a suction region communication path configured to communicate with a suction region leading to the backpressure chamber and the compression chamber and not to communicate with the compression chamber after the closing start, the suction region communication path supplying the oil in the backpressure chamber to the suction region.
  • Patent Literature 1 JP-A-2011-58439
  • Patent Literature 2 JP-A-2005-163655
  • Patent Literature 3 JP-A-2012-92773
  • the scroll compressor described in Patent Literature 1 includes the oil supplying means and the oil supply path for supplying the oil in the high-pressure hydraulic chamber to the backpressure chamber side to make it possible to adjust an amount of the oil flowing into the backpressure chamber from the high-pressure hydraulic chamber.
  • the oil supplied to the backpressure chamber entirely flows into the suction chamber and flows to the compression chamber through the suction chamber. Therefore, no consideration is made to the fact that an oil supply amount necessary in the compression chamber is added to an oil supply amount necessary in the suction chamber and a large amount of high-temperature oil flows into the suction chamber, and sucked gas is heated and a heating loss (a suction heating loss) increases.
  • An object of the present invention is to obtain a scroll compressor that can control each of an oil supply amount to a bearing section, an oil supply amount to a suction chamber, and an oil supply amount to a compression chamber and realize proper amounts of oil supply to the bearing section, the suction chamber, and the compression chamber and a refrigeration cycle apparatus using the scroll compressor.
  • the present invention provides a scroll compressor including a fixed scroll in which a spiral wrap is erected on a base plate and an orbiting scroll including a spiral wrap erected on a mirror plate and meshed with the fixed scroll to perform an orbiting motion, the scroll compressor causing the orbiting scroll to perform the orbiting motion with respect to the fixed scroll to thereby form a suction chamber and a compression chamber.
  • the scroll compressor includes: a first space formed in a back surface center of the orbiting scroll, lubricant stored in a bottom of a sealed container being led to the first space, and the first space having pressure close to discharge pressure; a second space provided further on an outer circumference side than the first space on a back surface of the orbiting scroll, the second space having pressure between the discharge pressure and suction pressure; a first oil leak path for causing a part of oil in the first space to leak to the second space; an oil return passage for returning most of the oil in the first space to the bottom in the sealed container; a second oil leak path for causing a part of the oil in the second space to leak to the suction chamber; and a third oil leak path for allowing the oil in the second space to escape to the compression chamber to adjust the pressure in the second space according to a difference between pressure in the compression chamber and the pressure in the second space.
  • FIG. 1 is a longitudinal sectional view showing a first embodiment of a scroll compressor of the present invention.
  • FIG. 2 is a view showing a state in which a fixed scroll and an orbiting scroll shown in FIG. 1 are meshed with each other and is a view of the fixed scroll and the orbiting scroll viewed from a II-II direction in FIG. 1 .
  • FIG. 3 is a perspective view of the orbiting scroll shown in FIG. 1 viewed from above.
  • FIG. 4 is an enlarged sectional view around a backpressure valve in the scroll compressor shown in FIG. 1 .
  • FIG. 5 is a view for explaining another example of the orbiting scroll and is a perspective view equivalent to FIG. 2 .
  • FIG. 6 is a view for explaining a second embodiment of the scroll compressor of the present invention and is a view equivalent to FIG. 4 .
  • FIG. 7 is a view for explaining a third embodiment of the present invention and is a refrigeration cycle configuration diagram showing an example of a refrigeration cycle apparatus using the scroll compressor.
  • FIG. 1 is a longitudinal sectional view showing the first embodiment of the scroll compressor of the present invention.
  • FIG. 2 is a view showing a state in which a fixed scroll and an orbiting scroll shown in FIG. 1 are meshed with each other and is a view of the fixed scroll and the orbiting scroll viewed from a II-II direction in FIG. 1 .
  • FIG. 3 is a perspective view of the orbiting scroll shown in FIG. 1 viewed from above.
  • FIG. 4 is an enlarged sectional view around a backpressure valve in the scroll compressor shown in FIG. 1 .
  • FIG. 5 is a view for explaining another example of the orbiting scroll and is a perspective view equivalent to FIG. 3 .
  • a scroll compressor 1 is configured by housing a compression mechanism section 2 , a motor unit 16 , and the like in a case (a sealed container) 9 .
  • an orbiting scroll 8 is meshed with a fixed scroll 7 fixed to a frame 17 to form compression chambers 13 .
  • the orbiting scroll 8 is caused to perform an orbiting motion via a crankshaft (a rotating shaft) 10 according to rotation of the motor unit 16 , whereby the capacity of the compression chambers 13 is reduced to perform compressing operation.
  • working fluid is sucked into a suction chamber 20 (see FIG. 3 ) from a suction port 14 .
  • the sucked working fluid is discharged from a discharge port 15 to a discharge space 54 in the case 9 through a compression stroke in the compression chambers 13 .
  • the working fluid discharged to the discharge space 54 flows to a motor chamber 52 passing through a passage (not shown in the figure) formed in the outer circumference of the fixed scroll 7 and the outer circumference of the frame 17 . Thereafter, the working fluid is discharged to the outside of the case 9 from a discharge pipe 6 .
  • the fixed scroll 7 includes a disk-like base plate 7 a, a wrap 7 b spirally erected on the base plate 7 a, and a supporting section 7 d located on the outer circumference side of the base plate 7 a, including a mirror plate surface 7 e having height substantially the same as the height of the distal end face of the wrap 7 b and provided in a cylinder shape to surround the wrap 7 b.
  • the surface of the base plate 7 a, on which the wrap 7 b is erected, is called teeth bottom 7 c because the surface is present among spirals of the wrap 7 b.
  • the mirror plate surface 7 e is formed as a sliding surface on which the supporting section 7 d of the fixed scroll 7 is in contact with a mirror plate 8 a of the orbiting scroll 8 .
  • the supporting section 7 d is fixed to the frame 17 by a bolt or the like.
  • the frame 17 integrally combined with the fixed scroll 7 is fixed to the case 9 by fixing means such as welding.
  • the orbiting scroll 8 is disposed to be opposed to the fixed scroll 7 .
  • the orbiting scroll 8 is turnably provided in the frame 17 with the wrap 7 b of the fixed scroll 7 and a wrap 8 b of the orbiting scroll 8 meshed with each other.
  • the orbiting scroll 8 includes the spiral wrap 8 b erected from a teeth bottom 8 c, which is the surface of the disk-like mirror plate 8 a, and an orbiting boss section (a boss section) 8 d provided in the back surface center of the mirror plate 8 a.
  • the surface of the outer circumferential section of the mirror plate 8 a in contact with the fixed scroll 7 is formed as a mirror plate surface 8 e of the orbiting scroll 8 .
  • the distal end portion (a wrap teeth tip) of the wrap 8 b of the orbiting scroll 8 is configured to be opposed to the teeth bottom 7 c of the fixed scroll 7 with a very small gap.
  • the distal end portion (the wrap teeth tip) of the wrap 7 b of the fixed scroll 7 is configured to be opposed to the teeth bottom 8 c of the orbiting scroll 8 with a very small gap.
  • An oil reservoir 53 for storing lubricant is provided in the bottom of the case 9 of a sealed container structure in which the compression mechanism section 2 , the motor unit 16 , and the like are housed.
  • the motor unit 16 is configured by a rotor 16 a and a stator 16 b.
  • the crankshaft 10 is integrally fixed to the rotor 16 a.
  • the crankshaft 10 is rotatably supported on the frame 17 via a main bearing 5 and is coaxial with the center axis of the fixed scroll 7 .
  • An eccentric crank section 10 a is provided at the distal end of the crankshaft 10 .
  • the crank section 10 a is inserted into an orbiting bearing 11 provided in the orbiting boss section 8 d of the orbiting scroll 8 .
  • the orbiting scroll 8 is configured to be capable of orbiting according to rotation of the crankshaft 10 .
  • the center axis of the orbiting scroll 8 is in an eccentric state by a predetermined distance with respect to the center axis of the fixed scroll 7 .
  • the wrap 8 b of the orbiting scroll 8 is superimposed on the wrap 7 b of the fixed scroll 7 while being shifted by a predetermined angle (in general, 180 degrees) in the circumferential direction.
  • Reference numeral 12 denotes an Oldham ring for causing the orbiting scroll 8 to perform an orbiting motion relatively to the fixed scroll 7 while restraining the orbiting scroll 8 not to revolve.
  • FIG. 2 is a view for explaining a meshing state of the fixed scroll 7 and the orbiting scroll 8 and is a view of the fixed scroll 7 and the orbiting scroll 8 viewed from a II-II direction in FIG. 1 . Therefore, concerning the orbiting scroll 8 , the orbiting scroll wrap 8 b is shown as a cross section.
  • a portion equivalent to the outer circumference of the mirror plate 8 a of the orbiting scroll 8 is indicated by an alternate long and two short dashes line (an imaginary line).
  • a plurality of crescent compression chambers 13 are formed between the fixed scroll wrap 7 b and the orbiting scroll wrap 8 b.
  • the orbiting scroll 8 is caused to perform an orbiting motion, as the compression chambers 13 move in the direction to the center, capacities of the compression chambers 13 are continuously reduced.
  • Reference numeral 20 denotes a suction chamber and a space halfway in suction of the fluid.
  • the suction chamber 20 changes to the compression chambers 13 at a point in time when the phase of the orbiting motion of the orbiting scroll 8 advances and confining of the fluid is completed.
  • the suction port 14 is provided in the fixed scroll 7 .
  • the suction port 14 is drilled on the outer circumference side of the base plate 7 a of the fixed scroll 7 to communicate with the suction chamber 20 .
  • the discharge port 15 is drilled near the spiral center of the base plate 7 a of the fixed scroll 7 to communicate with the compression chamber 13 on the innermost circumference side.
  • the orbiting scroll 8 When the crankshaft 10 is rotated by the motor unit 16 shown in FIG. 1 , the orbiting scroll 8 performs an orbiting motion with a predetermined orbiting radius centering on the center axis of the fixed scroll 7 . Consequently, the working fluid sucked from the suction port 14 , for example, refrigerant gas (hereinafter simply referred to as fluid) circulating in a refrigeration cycle is sequentially compressed in the compression chambers 13 . The compressed working fluid is discharged from the discharge port 15 to the discharge space 54 . As explained above, the working fluid is supplied to, for example, the refrigeration cycle outside the compressor from the discharge pipe 6 .
  • fluid refrigerant gas
  • An oil supply pump 21 of a displacement type or a centrifugal type is provided at the lower end of the crankshaft 10 .
  • the oil supply pump 21 According to the rotation of the crankshaft 10 , the oil supply pump 21 also rotates, sucks the lubricant stored in the oil reservoir 53 in the bottom of the case 9 from a lubricant suction port 22 a of an oil supply pump case 22 , and discharges the lubricant from a discharge port 21 a of the oil supply pump 21 .
  • the discharged lubricant is sent to a space in the orbiting boss section 8 d at the upper end of the crank section 10 a through a through-hole (an oil supply hole) 3 formed in the axial direction in the crankshaft 10 .
  • a part of the lubricant flowing through the through-hole 3 is sent to a sub-bearing 23 via a lateral hole 24 provided in the crankshaft 10 .
  • the lubricant After lubricating the sub-bearing 23 , the lubricant returns to the oil reservoir 53 in the bottom of the case 9 .
  • the most of the other lubricant flowing through the through-hole 3 reaches the orbiting boss section space at the upper end of the crank section 10 a, passes through an oil groove 57 provided on the outer circumferential surface of the crank section 10 a, and lubricates the orbiting bearing 11 .
  • the lubricant is returned to the oil reservoir 53 in the bottom of the case 9 through an oil return passage 26 configured by an oil discharge hole 26 a and an oil discharge pipe 26 b.
  • the orbiting boss section space formed by the oil groove 57 , the orbiting bearing 11 , and the like and a space in which the main bearing 5 is housed are collectively referred to as first space 33 .
  • the first space 33 is a space having pressure close to the discharge pressure.
  • a part of the lubricant flows into a backpressure chamber 18 , which is a second space having pressure between the discharge pressure and the suction pressure provided further on the outer circumference side than the first space 33 , via a first oil leak path provided between the upper end face of the seal member 32 and the end face of the brim section 34 of the orbiting boss section 8 d by an amount necessary for lubrication of the Oldham ring 12 , lubrication of sliding sections of the fixed scroll 7 and the orbiting scroll 8 , and seal (sealing) of, for example, distal end gaps of the wraps 7 b and 8 b.
  • the seal member 32 is provided, together with a wavy spring (not shown in the figure), in an annular groove 31 provided on a surface opposed to the brim section 34 of the frame 17 and partitions the first space 33 having the discharge pressure and the backpressure chamber (the second space) 18 having the pressure in the middle of the suction pressure and the discharge pressure.
  • the first oil leak path is configured by, for example, one or a plurality of slits 60 (grooves) long in the radial direction provided in the brim section 34 of the orbiting boss section 8 d and the seal member 32 .
  • the slits 60 are disposed to intermittently straddle the seal member 32 according to the orbiting motion of the orbiting scroll 8 to be configured to cause the first space 33 and the backpressure chamber 18 to intermittently communicate.
  • the slits 60 are not limited to be disposed to intermittently straddle the seal member 32 according to the orbiting motion of the orbiting scroll 8 and may be disposed to always straddle the seal member 32 .
  • one or a plurality of, that is, one or more holes (e.g., circular grooves) functioning as oil reservoirs are provided in the brim section 34 of the orbiting boss section.
  • the holes are configured to perform a circular motion straddling the seal member 32 according to the orbiting motion of the orbiting scroll 8 . Consequently, the holes move between the first space 33 and the backpressure chamber 18 . It is possible to accumulate, in the holes, the lubricant in the first space 33 and intermittently transfer the lubricant to the backpressure chamber 18 and discharge the lubricant. It is possible to supply the oil in the first space 33 to the backpressure chamber 18 .
  • the first oil leak path may be configured in this way.
  • a part of the lubricant flowed into the backpressure chamber 18 flows into the suction chamber 20 via a second oil leak path explained below.
  • the part of the lubricant lubricates wrap sliding surfaces, wrap distal end gaps, and the like and is used for seal of, for example, a space between compression chambers.
  • the remainder of the lubricant lubricates wrap sliding surfaces, wrap distal end gaps, and the like of the compression chambers and is used for seal of the space between the compression chambers.
  • the lubricant can be caused to leak from the first space 33 to the second space (the backpressure chamber) 18 via the first oil leak path by an amount necessary for the lubrication of the wrap sliding surfaces and the wrap distal end gaps and the seal of the space between the compression chambers.
  • the remaining lubricant can be returned to the oil reservoir 53 via the oil discharge hole 26 a and the oil discharge pipe 26 b after the lubrication of the bearing sections. Therefore, in this embodiment, it is possible to independently control an oil supply amount necessary for the lubrication of the bearing sections and an oil supply amount to the backpressure chamber 18 . Therefore, it is possible to reduce the oil supply amount to the backpressure chamber 18 to the necessary minimum.
  • the lubricant flowed into the backpressure chamber 18 can be supplied to the suction chamber 20 via the second oil leak path by a necessary oil supply amount.
  • the remaining lubricant is supplied to the compression chambers 13 via the third oil leak path. Therefore, it is possible to respectively reduce the oil supply amounts to the suction chamber 20 and the compression chambers 13 to the necessary minimums. Therefore, it is possible to minimize a suction heating loss in the suction chamber 20 . It is possible to prevent oil compression, a heating loss, and the like due to excessive supply of the oil in the compression chambers 13 . Therefore, it is possible to realize a scroll compressor having high efficiency and high reliability.
  • reference numeral 64 denotes an oil hole (a groove) provided on the mirror plate surface 8 e of the orbiting scroll 8 and functioning as an oil reservoir. As shown in FIG. 2 , according to the orbiting motion of the orbiting scroll 8 , the oil hole 64 draws a track 65 shown in FIG. 2 and intermittently communicates with the backpressure chamber (the second space) 18 and a groove section 66 that communicates with and the suction chamber 20 .
  • the oil in the backpressure chamber 18 pressure is the pressure in the middle of the discharge pressure and the suction pressure
  • pressure is the suction pressure
  • the oil in the backpressure chamber 18 is sequentially transferred to the suction chamber 20 .
  • the capacity of the oil hole 64 and the number of oil holes 64 it is possible to optionally adjust the oil supply amount from the backpressure chamber 18 to the suction chamber 20 .
  • the function of the backpressure chamber (the second space) 18 is explained.
  • a force (a separating force) in the axial direction for separating the fixed scroll 7 and the orbiting scroll 8 is generated by the compression action of the scroll compressor 1 .
  • sealability of the compression chambers 13 is deteriorated and to reduce compressor efficiency.
  • the backpressure chamber 18 having the pressure between the discharge pressure and the suction pressure is provided on the back surface side of the mirror plate 8 a of the orbiting scroll 8 .
  • the separating force is cancelled and the orbiting scroll 8 is pressed against the fixed scroll 7 by pressure (backpressure) of the backpressure chamber 18 .
  • a pressing force at this point is too large, a sliding loss of the mirror plate surface 8 e of the orbiting scroll 8 and the mirror plate surface 7 e of the fixed scroll 7 increases and the compressor efficiency decreases.
  • the third oil leak path (the compression chamber communication path) including a backpressure valve 61 for adjusting the backpressure of the backpressure chamber 18 is included in the supporting section 7 d of the fixed scroll 7 .
  • FIG. 4 is an enlarged view showing the configuration around the backpressure valve 61 in FIG. 1 .
  • the third oil leak path (a compression chamber communication path) is configured by a backpressure valve inflow path (a space communicating with the backpressure chamber 18 ) 62 a that causes the backpressure chamber 18 and the backpressure valve 61 to communicate, a backpressure valve outflow path (a space communicating with the compression chambers 13 ) 62 c that causes the backpressure valve 61 and the compression chambers 13 to communicate, and a space 62 b in which the backpressure valve 61 is housed.
  • a valve 61 a is disposed to partition the backpressure valve inflow path 62 a and the backpressure valve outflow path 62 c.
  • the valve 61 a is provided to be pressed against an opening section of the backpressure valve inflow path 62 a by a spring 61 b fixed to a stopper 61 c.
  • the oil flowed into the compression chambers 13 lubricates the wrap sliding surfaces, the wrap distal end gaps, and the like and is used for seal of the space between the compression chambers. Thereafter, the oil is discharged to the discharge space 54 from the discharge port 15 . Apart of the discharged oil is discharged from the discharge pipe 6 to the refrigeration cycle, for example, together with the refrigerant gas. The remainder is separated from the refrigerant gas in the case 9 and stored in the oil reservoir 53 in the bottom of the case.
  • the oil supply amount to the bearing sections and the oil supply amount to the backpressure chamber can be independently controlled by the first oil leak path.
  • the oil supply amount supplied from the backpressure chamber 18 to the suction chamber 20 are independently controlled by the second oil leak path.
  • the scroll compressor includes the third oil leak path for supplying the oil from the backpressure chamber 18 to the compression chambers 13 after the completion of a suction process via the backpressure valve 61 . Therefore, it is possible to appropriately adjust the oil supply amounts respectively to the bearing sections, the suction chamber 20 , and the compression chambers 13 .
  • the backpressure valve outflow path 62 c communicates with the compression chambers 13 after the completion of the suction process and the start of the compression. That is, the compression chambers 13 are compression chambers halfway in compression after the completion of the suction process and are compression chambers separated from the suction chamber 20 . As shown in FIG. 2 , the backpressure valve outflow path 62 c is in a position that alternately communicates with both of the orbiting outer line compression chambers 13 b and the orbiting inner line compression chamber 13 a according to the orbiting motion of the orbiting scroll.
  • 63 shown in FIG. 4 denotes a stop cock.
  • the stop cock 63 seals and closes an end portion of a lateral hole formed to provide the backpressure valve outflow path 62 c.
  • An oil supply amount to the compression chambers 13 is a difference between an oil supply amount from the first space 33 to the backpressure chamber 18 by the first oil leak path and an oil supply amount from the backpressure chamber 18 to the suction chamber 20 by the second oil leak path. That is, the oil is supplied to the backpressure chamber 18 from the first space 33 via the first oil leak means. However, the oil is led into the suction chamber by only an amount determined by the second oil leak path. The remaining oil is led into the compression chambers 13 .
  • an oil supply amount necessary for seal of the compression chambers 13 is larger than an oil supply amount necessary for seal of the suction chamber. Therefore, for example, in the scroll compressor described in Patent Literature 1, when the oil supply amount in the first oil leak path is set to the oil supply amount necessary for seal of the compression chambers, the oil supply becomes excessive and the suction heating loss increases in the suction chamber 20 . Conversely, when the oil supply amount in the first oil leak path is set to a small oil supply amount only necessary for seal of the suction chamber 20 , the oil supply becomes in sufficient, the sealing effect by the oil decreases, and a leak loss increases in the compression chambers.
  • the backpressure valve outflow path 62 c is formed in the position that alternately communicates with both of the orbiting outer line compression chambers 13 b and the orbiting inner line compression chamber 13 a according to the orbiting motion of the orbiting scroll. Therefore, it is possible to supply the oil to both the compression chambers. It is possible to avoid a deficiency in which oil supply is insufficient in any one of the compression chambers 13 .
  • this embodiment is applied to a scroll compressor that uses, as working fluid, a refrigerant that easily has high temperature and has an adiabatic exponent larger than 1.09, for example, R32, it is possible to further reduce the suction heating loss. It is possible to obtain a scroll compressor having higher efficiency.
  • the second oil leak path is configured by providing the circular oil hole (groove) 64 on the mirror plate surface 8 e of the orbiting scroll 8 .
  • the present invention is not limited to this. That is, as shown in FIG. 5 , instead of the oil hole 64 , a shallow slit (groove) 67 may be provided.
  • the slit 67 may always or intermittently communicate with the backpressure chamber 18 and the groove section 66 , which communicates with the suction chamber 20 , to lead the oil in the backpressure chamber 18 into the suction chamber 20 according to a pressure difference. Even in this case, it is possible to control an oil supply amount by adjusting the depth, the width, and the length of the slit, the number of slits, or the like.
  • FIG. 6 is a view equivalent to FIG. 4 referred to above.
  • portions denoted by reference numerals and signs same as those in FIG. 1 to FIG. 5 are the same or equivalent portions.
  • an oil supply amount to the bearing sections and an oil supply amount to the backpressure chamber can be independently controlled by the first oil leak path.
  • An oil supply amount supplied from the backpressure chamber 18 to the suction chamber 20 can be independently controlled by the second oil leak path.
  • the scroll compressor does not include the third oil leak path for supplying oil from the backpressure chamber 18 to the compression chambers 13 via the backpressure valve 61 shown in FIG. 4 .
  • the third oil leak path in the second embodiment is not included in the supporting section 7 d of the fixed scroll 7 .
  • the third oil leak path is configured by a backpressure hole 68 formed in the mirror plate 8 a of the orbiting scroll 8 .
  • the backpressure hole 68 is provided in the orbiting scroll mirror plate 8 a to cause the backpressure chamber (the second space) 18 and the compression chambers 13 after the completion of the suction process and the start of compression to communicate. That is, the backpressure hole 68 is provided in a position that communicates with only the compression chambers 13 separated from the suction chamber 20 .
  • the pressure in the backpressure chamber 18 can be maintained at a value close to average pressure in the compression chambers 13 by the backpressure hole 68 .
  • the scroll compressor includes the first oil leak path, the second oil leak path, and the backpressure hole 68 (the third oil leak path). Therefore, as in the first embodiment, it is possible to appropriately adjust the oil supply amounts respectively to the bearing sections, the suction chamber 20 , and the compression chambers 13 .
  • the refrigerant is also included in the oil (the lubricant) leaking from the first to third oil leak paths.
  • the oil including the refrigerant is also explained as the oil.
  • FIG. 7 is a refrigeration cycle configuration diagram showing an example of a refrigeration cycle apparatus for refrigeration and air conditioning using the scroll compressor of the present invention explained above.
  • FIG. 7 an example in which the scroll compressor of the present invention is applied to an air conditioner functioning as a refrigeration cycle apparatus is explained with reference to FIG. 7 .
  • reference numeral 1 denotes a scroll compressor
  • 43 denotes a four-way valve
  • 40 denotes an outdoor side heat exchanger (functioning as a condenser during cooling operation and functioning as an evaporator during heating operation)
  • 41 denotes an expansion valve configured by an electronic expansion valve or the like
  • 42 denotes an indoor side heat exchanger (functioning as an evaporator during cooling operation and functioning as a condenser during heating operation).
  • the scroll compressor of the present invention is applied to the air conditioner including one outdoor side heat exchanger 40 and one indoor side heat exchanger 42 .
  • the scroll compressor of the present invention can also be applied to, for example, a multi-type air conditioner including a plurality of the indoor side heat exchangers 42 .
  • the scroll compressor of the present invention can also be applied to refrigeration cycle apparatuses such as an air conditioner exclusive for cooling and a refrigerator.
  • the embodiments of the present invention it is possible to control each of the oil supply amount to the bearing sections, the oil supply amount to the backpressure chamber, the oil supply amount to the suction chamber, and the oil supply amount to the compression chambers to proper oil supply amounts necessary for the bearing sections, the backpressure chamber, the suction chamber, and the compression chambers. Therefore, it is possible to obtain a scroll compressor having high efficiency and a refrigeration cycle apparatus for refrigeration and air conditioning using the scroll compressor.
  • crankshaft (rotating shaft)
  • crank section 10 a crank section
  • 26 oil return passage ( 26 a: oil discharge hole, 26 b: oil discharge pipe)

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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)
US15/511,323 2014-09-30 2015-09-29 Scroll compressor and refrigeration cycle apparatus using the same Abandoned US20170306951A1 (en)

Applications Claiming Priority (3)

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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
PCT/JP2015/077515 WO2016052503A1 (fr) 2014-09-30 2015-09-29 Compresseur à spirales et dispositif à cycle de réfrigération l'utilisant

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US (1) US20170306951A1 (fr)
JP (1) JP6302813B2 (fr)
CN (3) CN106795881B (fr)
WO (1) WO2016052503A1 (fr)

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US20210239118A1 (en) * 2020-02-04 2021-08-05 Aspen Compressor, Llc Horizontal rotary compressor with enhanced tiltability during operation and other performance metrics
CN114215757A (zh) * 2021-12-17 2022-03-22 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
EP4043732A1 (fr) * 2021-02-15 2022-08-17 LG Electronics Inc. Compresseur à spirales
US11506210B2 (en) * 2019-09-12 2022-11-22 Carrier Corporation Centrifugal compressor and refrigerating device
US12078180B2 (en) * 2019-09-12 2024-09-03 Carrier Corporation Centrifugal compressor having a motor cooling passage

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JP6302813B2 (ja) * 2014-09-30 2018-03-28 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これを用いた冷凍サイクル装置
JP6688972B2 (ja) * 2017-01-27 2020-04-28 パナソニックＩｐマネジメント株式会社 スクロール圧縮機
CN111033045A (zh) * 2017-09-04 2020-04-17 松下知识产权经营株式会社 压缩机
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
KR102454721B1 (ko) * 2021-02-19 2022-10-14 엘지전자 주식회사 스크롤 압축기
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
CN115450910A (zh) * 2022-10-18 2022-12-09 珠海格力电器股份有限公司 泵体组件和涡旋压缩机

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US11506210B2 (en) * 2019-09-12 2022-11-22 Carrier Corporation Centrifugal compressor and refrigerating device
US12078180B2 (en) * 2019-09-12 2024-09-03 Carrier Corporation Centrifugal compressor having a motor cooling passage
US20210239118A1 (en) * 2020-02-04 2021-08-05 Aspen Compressor, Llc Horizontal rotary compressor with enhanced tiltability during operation and other performance metrics
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CN106795881B (zh) 2018-07-31
CN108980036A (zh) 2018-12-11
WO2016052503A1 (fr) 2016-04-07
JP6302813B2 (ja) 2018-03-28
CN109026706B (zh) 2020-06-09
CN109026706A (zh) 2018-12-18
CN106795881A (zh) 2017-05-31
JP2016070178A (ja) 2016-05-09

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