US20170089624A1 - Hermetic compressor and vapor compression-type refrigeration cycle device including the hermetic compressor - Google Patents
Hermetic compressor and vapor compression-type refrigeration cycle device including the hermetic compressor Download PDFInfo
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- US20170089624A1 US20170089624A1 US15/126,203 US201415126203A US2017089624A1 US 20170089624 A1 US20170089624 A1 US 20170089624A1 US 201415126203 A US201415126203 A US 201415126203A US 2017089624 A1 US2017089624 A1 US 2017089624A1
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- Prior art keywords
- rotator
- electric motor
- space
- hermetic compressor
- refrigerant
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- 238000005057 refrigeration Methods 0.000 title claims description 16
- 239000003507 refrigerant Substances 0.000 claims abstract description 84
- 230000001965 increasing effect Effects 0.000 claims abstract description 67
- 230000006835 compression Effects 0.000 claims abstract description 38
- 238000007906 compression Methods 0.000 claims abstract description 38
- 239000010687 lubricating oil Substances 0.000 claims abstract description 22
- 238000000638 solvent extraction Methods 0.000 claims abstract description 5
- 230000002093 peripheral effect Effects 0.000 claims description 72
- 238000005192 partition Methods 0.000 claims description 8
- 230000000903 blocking effect Effects 0.000 claims description 5
- 238000007599 discharging Methods 0.000 claims 1
- 239000003921 oil Substances 0.000 description 44
- 230000000694 effects Effects 0.000 description 17
- 230000015556 catabolic process Effects 0.000 description 13
- 238000006731 degradation reaction Methods 0.000 description 13
- 238000000926 separation method Methods 0.000 description 10
- 238000005461 lubrication Methods 0.000 description 7
- 238000000034 method Methods 0.000 description 7
- 239000000758 substrate Substances 0.000 description 7
- 239000007787 solid Substances 0.000 description 4
- 238000003756 stirring Methods 0.000 description 3
- 229910000576 Laminated steel Inorganic materials 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 238000005516 engineering process Methods 0.000 description 2
- 239000012530 fluid Substances 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 230000002265 prevention Effects 0.000 description 2
- VOPWNXZWBYDODV-UHFFFAOYSA-N Chlorodifluoromethane Chemical compound FC(F)Cl VOPWNXZWBYDODV-UHFFFAOYSA-N 0.000 description 1
- 229910000831 Steel Inorganic materials 0.000 description 1
- 230000002159 abnormal effect Effects 0.000 description 1
- 238000005452 bending Methods 0.000 description 1
- 238000006243 chemical reaction Methods 0.000 description 1
- 238000005520 cutting process Methods 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 230000007613 environmental effect Effects 0.000 description 1
- 238000002474 experimental method Methods 0.000 description 1
- 238000010030 laminating Methods 0.000 description 1
- 238000011089 mechanical engineering Methods 0.000 description 1
- 239000002245 particle Substances 0.000 description 1
- 230000010349 pulsation Effects 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
- 238000004088 simulation Methods 0.000 description 1
- 230000003068 static effect Effects 0.000 description 1
- 239000010959 steel Substances 0.000 description 1
- 238000003466 welding Methods 0.000 description 1
- 238000004804 winding Methods 0.000 description 1
Images
Classifications
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- 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
- F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
- F25B43/02—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat for separating lubricants from the refrigerant
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/02—Lubrication
- F04B39/0223—Lubrication characterised by the compressor type
- F04B39/023—Hermetic compressors
- F04B39/0238—Hermetic compressors with oil distribution channels
- F04B39/0246—Hermetic compressors with oil distribution channels in the rotating shaft
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/04—Measures to avoid lubricant contaminating the pumped 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
- 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
- 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
- F04C23/005—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 of dissimilar working principle
-
- 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
- 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
- F04C23/02—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
-
- 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
- F04C29/04—Heating; Cooling; Heat insulation
- F04C29/045—Heating; Cooling; Heat insulation of the electric motor in hermetic pumps
-
- 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
-
- 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
- F25B31/00—Compressor arrangements
- F25B31/002—Lubrication
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2240/00—Components
- F04C2240/60—Shafts
Definitions
- the present invention relates to a hermetic compressor, and a vapor compression-type refrigeration cycle device including the hermetic compressor.
- the present invention relates to a hermetic compressor excellent in oil separation effect, and a vapor compression-type refrigeration cycle device including the hermetic compressor.
- a rotational force of an electric motor is transmitted to a compression mechanism by a drive shaft so that refrigerant gas is compressed.
- the refrigerant gas compressed by the compression mechanism is discharged into a hermetic container, moved from a space below the electric motor into a space above the same through electric motor unit gas passages, and then discharged into a refrigerant circuit on an outside of the hermetic container.
- lubricating oil supplied to the compression mechanism and mixed with the refrigerant gas is discharged to the outside of the hermetic container.
- the high-pressure shell type scroll compressor disclosed in Patent Literature 1 sucked refrigerant is compressed by the compression mechanism arranged on an upper side in the hermetic container, and once caused to flow down to an oil reservoir at a bottom of the hermetic container. After that, the refrigerant is caused to flow up from a space below the electric motor to a space above the same through electric motor gas passages, and then discharged as high pressure gas through a discharge pipe of the compressor.
- the high-pressure shell type scroll compressor disclosed in Patent Literature 1 includes a fan arranged on an upper portion of a rotator of the electric motor, and partition walls for separating a stator side of the electric motor and a rotator side of the electric motor from each other above the fan.
- the refrigerant and the lubricating oil are separated from each other by using a centrifugal force generated by rotation of the fan and by using pressure resistance generated through gaps between the partition walls.
- the lubricating oil is prevented from flowing directly into the discharge pipe without being separated from the refrigerant, in other words, the lubricating oil is prevented from flowing out from the hermetic container.
- an oil separation device for a hermetic electric compressor including: an electric component housed in an upper portion of a hermetic container; a compression component that is driven by the electric component; an oil separation plate arranged to face an upper end ring of a rotor of the electric component across a predetermined clearance; and stirring vanes arranged upright to the oil separation plate, in which the stirring vanes are arranged upright only to a lower surface of the oil separation plate.
- Patent Literature 3 there is disclosed a refrigerant compressor in which an increase in head pressure that is generated near a leading end in a rotation direction of an upper balance weight at an upper end of the rotator of the electric motor arranged in the hermetic container is used to form an oil return passage from a vicinity of a leading end portion toward a lower end so that high density lubricating oil that appears around the rotator is returned below the electric motor, to thereby prevent the oil from flowing out.
- Patent Literatures 1 and 2 no theoretical design methods are disclosed for the fan and the vanes that are each attached on the upper portion of the rotator (rotor) of the electric motor disclosed therein, and optimum configurations for the fan and the vanes for improving the oil separation condition have not yet been specified.
- the present invention has been made to solve the problem as described above, and it is an object thereof to provide a hermetic compressor capable of reducing an amount of oil flowing to an outside of a hermetic container than that in the related art by using rotation of a rotator of an electric motor arranged in the hermetic container, and to provide a vapor compression-type refrigeration cycle device including the hermetic compressor.
- a hermetic compressor including: a hermetic container having a bottom portion for storing lubricating oil; an electric motor arranged in the hermetic container, the electric motor including: a stator and a rotator through which a rotator vent is formed in a vertical direction; a drive shaft attached to the rotator; a compression mechanism arranged in the hermetic container, for compressing refrigerant by using rotation of the drive shaft; a rotary pressure increasing mechanism arranged on an upper portion of the rotator, for increasing a pressure of refrigerant gas by allowing the refrigerant gas to flow through the rotary pressure increasing mechanism while rotating about the drive shaft; a cylindrical lateral wall for partitioning a space above the electric motor into an outer space on the stator side and inner space on the rotator side in such a manner that the cylindrical lateral wall surrounds the rotary pressure increasing mechanism positioned in the inner space; and a discharge pipe communicated to the inner space, for allowing the ref
- a vapor compression-type refrigeration cycle device including: the hermetic compressor of the one embodiment of the present invention; a radiator for transferring heat of refrigerant that is compressed by the hermetic compressor; an expansion mechanism for expanding the refrigerant that flows out from the radiator; and an evaporator for causing the refrigerant that flows out from the expansion mechanism to receive heat.
- the one embodiment of the present invention can prevent a decrease in amount of lubricating oil stored in the hermetic container and can obtain an effect of suppressing reliability degradation to be caused by insufficient lubrication, and an effect of achieving high energy-saving performance.
- FIG. 1 is a vertical sectional view of a structure of a hermetic compressor according to Embodiment 1 of the present invention.
- FIG. 2 is a horizontal sectional view of the structure of the hermetic compressor according to Embodiment 1 of the present invention (sectional view taken along the line A-A in FIG. 1 ).
- FIG. 3 is a perspective view of a rotary pressure increasing mechanism that is arranged on an upper portion of a rotator of the hermetic compressor according to Embodiment 1 of the present invention.
- FIG. 4 is a vertical sectional view of a structure of a hermetic compressor according to Embodiment 2 of the present invention.
- FIG. 5 is a horizontal sectional view of the structure of the hermetic compressor according to Embodiment 2 of the present invention (sectional view taken along the line A-A in FIG. 4 ).
- FIG. 6 is a perspective view of a rotary pressure increasing mechanism that is arranged on an upper portion of a rotator of the hermetic compressor according to Embodiment 2 of the present invention.
- FIG. 7 is a vertical sectional view of a structure of a hermetic compressor according to Embodiment 3 of the present invention.
- FIG. 8 is a horizontal sectional view of the structure of the hermetic compressor according to Embodiment 3 of the present invention (sectional view taken along the line A-A in FIG. 7 ).
- FIG. 9 is a vertical sectional view of a structure of a hermetic compressor according to Embodiment 4 of the present invention.
- FIG. 10 is a horizontal sectional view of the structure of the hermetic compressor according to Embodiment 4 of the present invention (sectional view taken along the line A-A in FIG. 9 ).
- FIG. 11 is a perspective view of a rotary pressure increasing mechanism that is arranged on an upper portion of a rotator of the hermetic compressor according to Embodiment 4 of the present invention.
- FIG. 12 is a configuration diagram of a vapor compression-type refrigeration cycle device according to Embodiment 5 of the present invention.
- FIG. 1 is a vertical sectional view of a structure of a hermetic compressor according to Embodiment 1 of the present invention.
- FIG. 2 is a horizontal sectional view of the structure of the hermetic compressor according to Embodiment 1 of the present invention (sectional view taken along the line A-A in FIG. 1 ).
- FIG. 3 is a perspective view of a rotary pressure increasing mechanism that is arranged on an upper portion of a rotator of the hermetic compressor according to Embodiment 1 of the present invention.
- the solid arrow shown in FIG. 2 indicates a rotation direction of the rotary pressure increasing mechanism.
- the rotary pressure increasing mechanism illustrated in FIG. 3 is viewed in a direction of the three-dimensional arrow shown in FIG. 2 .
- the hermetic compressor 100 according to Embodiment 1 is a high-pressure shell hermetic scroll compressor, which includes a hermetic container 1 having a bottom portion in which a lower oil reservoir 2 for storing lubricating oil is formed, and an electric motor 8 , a drive shaft 3 , a compression mechanism 60 , and a rotary pressure increasing mechanism 49 that are housed in the hermetic container 1 .
- the electric motor 8 includes a substantially cylindrical stator 7 having an inner peripheral portion through which a through-hole is formed in a vertical direction, and a substantially cylindrical rotator 6 arranged on an inner peripheral side of the stator 7 across a predetermined air gap 27 a .
- the electric motor 8 according to Embodiment 1 is, for example, a DC brushless motor.
- the stator 7 is formed of laminated steel plates, and includes a core 7 c that is formed into a wound coil block by winding a coil therearound at a high density. Further, at an upper end of the stator 7 , coil parts projecting from the wound coil block toward an upper side of the stator 7 , that is, a plurality of electric motor upper coil-interconnecting portion 7 a are formed.
- stator 7 At a lower end of the stator 7 , coil parts projecting from the wound coil block toward a lower side of the stator 7 , that is, a plurality of electric motor lower coil-interconnecting portions 7 b are formed.
- This stator 7 is attached to an inner peripheral surface of the hermetic container 1 by press fitting, welding, and the like. Note that, an outer peripheral portion of the core 7 c of the stator 7 is partially cut out so that stator outer peripheral passages 25 are formed between the core 7 c and the hermetic container 1 under a state in which the stator 7 is attached to the inner peripheral surface of the hermetic container 1 .
- the rotator 6 is formed by laminating steel plates and sandwiching uppermost and lowermost ones of the laminated steel plates respectively with a rotator upper end fixing substrate 33 and a rotator lower end fixing substrate 34 . Further, magnets are arranged in the rotator 6 . Still further, respectively on an upper surface of the rotator upper end fixing substrate 33 and a lower surface of the rotator lower end fixing substrate 34 , an upper balance weight 31 and a lower balance weight 32 , which have a predetermined thickness and are arranged in reverse phases, are arranged along outer rims of the rotator 6 . Yet further, four rotator vents 26 are formed in the vertical direction through the rotator 6 according to Embodiment 1. Note that, the number of the rotator vents 26 is not particularly limited as long as at least one rotator vent 26 is formed.
- a lower end portion of the drive shaft 3 is attached to the rotator 6 of the electric motor 8 , and an upper end portion thereof is attached to the compression mechanism 60 described below.
- the drive shaft 3 is configured to transmit a driving force of the electric motor 8 to the compression mechanism 60 .
- An upper side of the drive shaft 3 is held in a freely rotatable manner by a main bearing unit 55 of an upper bearing member 11 arranged above the electric motor 8 , and a lower side thereof is held in a freely rotatable manner by a sub bearing unit 54 of a lower bearing member 12 arranged below the electric motor 8 .
- the compression mechanism 60 is arranged above the electric motor 8 , and includes a fixed scroll 51 and an orbiting scroll 52 .
- Plate-like scroll teeth are formed on a lower surface of the fixed scroll 51 , which is attached to a compression mechanism casing 50 that is fixed to the inner peripheral surface of the hermetic container 1 .
- Plate-like scroll teeth to mesh with the plate-like scroll teeth of the fixed scroll 51 are formed on an upper surface of the orbiting scroll 52 , which is provided in a freely slidable manner at the upper end portion of the drive shaft 3 .
- a lower surface of the orbiting scroll 52 is supported in a freely slidable manner by an upper surface portion of the upper bearing member 11 .
- An outer peripheral surface of the upper bearing member 11 is supported in a freely slidable manner by an inner peripheral surface of the compression mechanism casing 50 .
- a refrigerant passage 57 is formed between an outer peripheral portion of the compression mechanism casing 50 and the hermetic container 1 . Further, a discharge cover 56 for partitioning an electric motor superjacent space 9 (more specifically, upper part of a cylindrical lateral wall 37 described below) into an electric motor stator superjacent space 9 a (outer space) and an electric motor rotator superjacent space 9 b (inner space) is arranged under the compression mechanism casing 50 .
- the rotary pressure increasing mechanism 49 is arranged on an upper portion of the rotator 6 .
- the rotary pressure increasing mechanism 49 according to Embodiment 1 is a centrifugal impeller 40 , which includes a plurality of vanes 41 arranged in a manner of extending from an inner peripheral side to an outer peripheral side about the drive shaft 3 .
- the centrifugal impeller 40 according to Embodiment 1 also includes a vane superjacent disk 43 (upper surface plate) for blocking inflow of refrigerant gas from above the vanes 41 into the centrifugal impeller 40 , and a vane subjacent disk 44 (lower surface plate) for blocking inflow of refrigerant gas from below the vanes 41 into the centrifugal impeller 40 .
- an inner peripheral flow guide 42 (partition plate) is extended downward from a rim of an opening portion of the vane subjacent disk 44 , which is formed at a position on an inner peripheral side of the vanes 41 , in a manner that an outer peripheral portion of the rotator vents 26 is surrounded.
- the centrifugal impeller 40 is rotated about the drive shaft 3 through, for example, connection between the drive shaft 3 and the vane superjacent disk 43 , connection between the cylindrical lateral wall 37 described below and the vane subjacent disk 44 , or connection between the rotator 6 and the inner peripheral flow guide 42 .
- connection between the drive shaft 3 and the vane superjacent disk 43 connection between the cylindrical lateral wall 37 described below and the vane subjacent disk 44 , or connection between the rotator 6 and the inner peripheral flow guide 42 .
- the cylindrical lateral wall 37 is arranged to surround the centrifugal impeller 40 (more specifically, refrigerant outlet on the outer peripheral side), in other words, to partition the electric motor superjacent space 9 into the electric motor stator superjacent space 9 a (outer space) and the electric motor rotator superjacent space 9 b (inner space). Further, in the cylindrical lateral wall 37 , an oil drain hole 39 is formed on a rotation direction leading end portion 31 a side of the upper balance weight 31 . This cylindrical lateral wall 37 is attached to an upper surface portion of a disk portion 38 a of a balancer fixing bottom plate 38 for fixing the upper balance weight 31 to the rotator upper end fixing substrate 33 .
- a stator inner peripheral passage closing portion 38 b (closing member) is arranged to project from an outer peripheral portion of the disk portion 38 a of the balancer fixing bottom plate 38 .
- This stator inner peripheral passage closing portion 38 b is arranged to close an upper part of a stator inner peripheral passage 27 formed between the rotator 6 and the stator 7 (specifically, air gap 27 a between the rotator 6 and the stator 7 , and core inner peripheral portion cut-out passage 27 b formed by cutting out the inner peripheral side of the stator 7 ).
- the orbiting scroll 52 of the compression mechanism 60 performs eccentric orbital operation along with rotation of the drive shaft 3 , causing sucked low-pressure refrigerant to enter the compression chamber 4 through a compressor suction pipe 21 . Then, the sucked pressure refrigerant is increased in pressure through a compression step of gradually decreasing a volume of the compression chamber 4 , and is discharged into a discharge space 10 (( 1 ) in FIG. 1 ) in the hermetic container 1 through a discharge port 18 of the fixed scroll 51 .
- the lubricating oil stored in the lower oil reservoir 2 is sucked upward from a lower end of the drive shaft 3 , and flows into a hollow hole 3 a .
- Part of the lubricating oil is supplied, for example, to the sub bearing unit 54 and the main bearing unit 55 through oil supply holes (not shown). Further, part of the lubricating oil flows out from an upper end of the drive shaft 3 , and then is supplied into the compression chamber 4 through, for example, a gap between the upper bearing member 11 and the orbiting scroll 52 and an oil supply hole 3 b , increasing effects of lubrication of the compression mechanism 60 and sealing of the compressed gas.
- the lubricating oil that is supplied in the compression chamber 4 is discharged into the discharge space 10 (( 1 ) in FIG. 1 ) in the hermetic container 1 through the discharge port 18 of the fixed scroll 51 together with the refrigerant compressed to have a high pressure in the compression chamber 4 .
- the refrigerant that is discharged through the discharge port 18 flows downward through the refrigerant passage 57 formed of a gap between an outer peripheral side of the compression mechanism casing 50 and the hermetic container 1 , and reaches the electric motor stator superjacent space 9 a (( 2 ) in FIG. 1 ). Further, this refrigerant flows downward into an electric motor stator subjacent space (( 3 ) in FIG. 1 ) in an electric motor subjacent space 5 through the stator outer peripheral passages 25 formed between the core 7 c of the stator 7 and the hermetic container 1 , and reaches the lower bearing member 12 including the sub bearing unit 54 .
- the refrigerant and the lubricating oil mixed in an atomized form with the refrigerant are separated from each other, and the separated lubricating oil is refluxed to the lower oil reservoir 2 through an oil return hole 12 a formed through the lower bearing member 12 .
- the refrigerant that flows in the electric motor stator subjacent space in the electric motor subjacent space 5 flows up from an electric motor rotator subjacent space (( 4 ) in FIG. 1 ) in the electric motor subjacent space 5 through the rotator vents 26 into a vane inner passage 46 of the centrifugal impeller 40 attached on an upper portion of the rotator 6 (passage on an inner peripheral side of the inner peripheral flow guide 42 , that is, space represented by ( 5 ) in FIG. 1 ).
- the refrigerant that flows in the vane inner passage 46 is sucked into inter-vane passages 47 formed between the vanes 41 of the centrifugal impeller 40 , flows to the outer peripheral side while being increased in pressure in accordance with a rotational speed of the centrifugal impeller 40 , and, on an outer peripheral side of the vanes 41 , flows up through a vane outer passage 48 formed in a region on an inner peripheral side of the cylindrical lateral wall 37 . Then, this refrigerant is once released into the electric motor rotator superjacent space 9 b (( 6 ) in FIG.
- a gap between the electric motor upper coil-interconnecting portions 7 a and the discharge cover 56 that is, a short circuit passage 23 needs to be formed.
- the refrigerant may flow from the electric motor stator superjacent space 9 a (( 2 ) in FIG. 1 ) directly into the electric motor rotator superjacent space 9 b (( 6 ) in FIG. 1 ) without flowing through the electric motor stator subjacent space (( 3 ) in FIG.
- the cylindrical lateral wall 37 is arranged upright to the balancer fixing bottom plate 38 so that a passage area of the short circuit passage 23 is reduced, and thus the passage resistance is increased. Further, a lower end portion of the discharge cover 56 is bent so that a passage shape of the short circuit passage 23 is made complicated, and thus the passage resistance of the short circuit passage 23 is further increased.
- the cylindrical lateral wall 37 is interposed to separate the centrifugal impeller 40 arranged on the rotator 6 and the electric motor upper coil-interconnecting portions 7 a from each other.
- the refrigerant gas that is increased in pressure by the centrifugal impeller 40 can be suppressed from reversely flowing into the electric motor stator superjacent space 9 a (( 2 ) in FIG. 1 ) through radial passages 28 in the electric motor upper coil-interconnecting portions 7 a .
- the pressure in the electric motor rotator superjacent space 9 b (( 6 ) in FIG. 1 ) can be increased.
- the stator inner peripheral passage 27 (air gap 27 a and core inner peripheral portion cut-out passage 27 b ) is formed as an upward refrigerant passage from the electric motor subjacent space 5 (( 3 ) or ( 4 ) in FIG. 1 ) to the electric motor superjacent space 9 (( 2 ) or ( 5 ) in FIG. 1 ), and the pressure increasing effect by the centrifugal impeller 40 cannot be exerted to the refrigerant gas that flows through the stator inner peripheral passage 27 . Therefore, a greater pressure increasing effect can be obtained by the centrifugal impeller 40 when the stator inner peripheral passage 27 is closed as much as possible.
- the stator inner peripheral passage closing portion 38 b is arranged to the outer peripheral portion of the disk portion 38 a so that the upper part of the stator inner peripheral passage 27 is closed.
- an amount of the refrigerant gas that flows through the stator inner peripheral passage 27 can be suppressed, and thus the pressure in the electric motor rotator superjacent space 9 b (( 6 ) in FIG. 1 ) can be further increased.
- the shape of the vanes and the passages of the centrifugal impeller 40 need to be designed such that a pressure (P 6 ) in the electric motor rotator superjacent space 9 b (( 6 ) in FIG. 1 ) is higher than a pressure (P 2 ) in the electric motor stator superjacent space 9 a (( 2 ) in FIG. 1 ).
- a pressure in the centrifugal impeller 40 input to the compressor (electric power consumption thereof) is increased.
- Non Patent Literature 2 (p. 132), of centrifugal fans, a turbofan (having vanes that are formed rearward with respect to a rotation direction) is advantageous in terms of efficiency.
- the shape of the vanes 41 of the centrifugal impeller 40 is determined to be rearward with respect to the rotation direction, and eight vanes 41 formed into this shape are arranged in axial symmetry with respect to the drive shaft 3 .
- an inlet angle of each of the vanes 41 is determined such that the vanes 41 each form an angle within a range of ⁇ 5 degrees with respect to a circle formed by connecting end positions on the inner peripheral side of the vanes 41 . This is because, according to Non Patent Literature 1 (p.
- a collision loss occurs when an entry angle ib that is equal to a difference between a relative inflow angle 131 and a vane inlet angle ⁇ 1 b at an inlet of the impeller ranges from 2 degrees to 5 degrees or more, causing losses in the compressor.
- the pressure in the electric motor rotator superjacent space 9 b (( 6 ) in FIG. 1 ) can be increased by using rotation of the rotator 6 in the hermetic container 1 .
- the hermetic compressor 100 that is configured to output three horsepower and operated at a constant speed (50 rps)
- a refrigerant R 22 under the condition of Ashrae standard
- an effect of increasing the pressure in the electric motor rotator superjacent space 9 b (( 6 ) in FIG. 1 ) in units of several kPa can be obtained.
- the refrigerant is less liable to flow from the electric motor stator superjacent space 9 a (( 2 ) in FIG. 1 ) directly into the electric motor rotator superjacent space 9 b (( 6 ) in FIG. 1 ) through the short circuit passage 23 , and the large number of droplets of the unseparated oil are less liable to flow out from the hermetic container 1 to the external circuit.
- an effect of suppressing the degradation in performance of the hermetic compressor 100 and an effect of suppressing the degradation in reliability thereof due to insufficient lubrication that may be caused by a decrease in amount of the oil stored in the hermetic container 1 can be obtained.
- FIG. 4 is a vertical sectional view of a structure of a hermetic compressor according to Embodiment 2 of the present invention.
- FIG. 5 is a horizontal sectional view of the structure of the hermetic compressor according to Embodiment 2 of the present invention (sectional view taken along the line A-A in FIG. 4 ).
- FIG. 6 is a perspective view of a rotary pressure increasing mechanism that is arranged on an upper portion of a rotator of the hermetic compressor according to Embodiment 2 of the present invention.
- the solid arrow shown in FIG. 5 indicates a rotation direction of the rotary pressure increasing mechanism.
- the rotary pressure increasing mechanism illustrated in FIG. 6 is viewed in a direction of the three-dimensional arrow shown in FIG. 5 .
- the hermetic compressor 100 according to Embodiment 2 is described. Note that, the fundamental structure and the operation of the hermetic compressor 100 according to Embodiment 2 are the same as those in Embodiment 1, and hence description thereof is omitted.
- Embodiment 2 is different from Embodiment 1 in that only four of the eight vanes 41 of the centrifugal impeller 40 in Embodiment 1 that are positioned on one side on which the upper balance weight 31 is absent are left, and that a height of each of the four vanes 41 is designed to be equal to a height of the upper balance weight 31 .
- Embodiment 1 to allow the refrigerant flowing through the rotator vents 26 to flow out from the centrifugal impeller 40 through the vane inner passage 46 , the inner peripheral flow guide 42 and the vane subjacent disk 44 are needed.
- Embodiment 2 there is an advantage in that the inner peripheral flow guide 42 and the vane subjacent disk 44 can be omitted, and hence the centrifugal impeller 40 is easily processed.
- centrifugal impeller 40 in a case where the centrifugal impeller 40 is configured as in Embodiment 2, fan efficiency is lower than that of the centrifugal impeller 40 according to Embodiment 1, in which the vanes 41 are arranged in axial symmetry. Further, in the case where the centrifugal impeller 40 is configured as in Embodiment 2, pressure pulsation by the centrifugal impeller 40 is increased in comparison with that by the centrifugal impeller 40 according to Embodiment 1, in which the vanes 41 are arranged in axial symmetry. As a result, vibration and noise may occur. Thus, in a case where the fan efficiency and prevention of the vibration and noise are regarded as important, it is preferred that the centrifugal impeller 40 be configured as in Embodiment 1.
- Embodiment 1 the cylindrical lateral wall 37 for preventing short-circuit flow of the refrigerant through the short circuit passage 23 , and the balancer fixing bottom plate 38 for fixing the cylindrical lateral wall 37 are formed as separate members. Meanwhile, in Embodiment 2, the cylindrical lateral wall 37 and the balancer fixing bottom plate 38 according to Embodiment 1 are provided as an oil separating cup 36 obtained by a process of integrating a cylindrical lateral wall 36 a and a bottom plate 36 b with each other. Note that, similarly to Embodiment 1, an oil drain hole 36 c is formed in the oil separating cup 36 on the rotation direction leading end portion 31 a side of the upper balance weight 31 .
- the hermetic compressor 100 configured as in Embodiment 2 the decrease in amount of the lubricating oil stored in the hermetic container 1 can be prevented.
- an effect of suppressing reliability degradation caused by insufficient lubrication and an effect of suppressing energy-saving performance degradation, which are comparably less than those in Embodiment 1 but are equivalent thereto, can be obtained.
- the hermetic compressor 100 configured as in Embodiment 2 there is an advantage in that a manufacturing cost for the centrifugal impeller 40 is lower than that in Embodiment 1.
- FIG. 7 is a vertical sectional view of a structure of a hermetic compressor according to Embodiment 3 of the present invention.
- FIG. 8 is a horizontal sectional view of the structure of the hermetic compressor according to Embodiment 3 of the present invention (sectional view taken along the line A-A in FIG. 7 ). Note that, the solid arrow shown in FIG. 8 indicates a rotation direction of the rotary pressure increasing mechanism.
- the hermetic compressor 100 according to Embodiment 3 is described. Note that, the fundamental structure and the operation of the hermetic compressor 100 according to Embodiment 3 are the same as those in Embodiment 1, and hence description thereof is omitted.
- the cylindrical lateral wall (cylindrical lateral wall 37 or cylindrical lateral wall 36 a ) for preventing the short-circuit flow of the refrigerant through the short circuit passage 23 is arranged on the upper portion of the rotator 6 so that the cylindrical lateral wall is rotated together with the rotator 6 .
- a closing cover 29 (more specifically, cylindrical portion 29 a ) as a counterpart of the cylindrical lateral wall is arranged on an inner side of the electric motor upper coil-interconnecting portions 7 a of the stator 7 so that the radial passages 28 are closed.
- a projecting portion 29 b for closing the upper part of the stator inner peripheral passage 27 is formed on an inner peripheral side of the cylindrical portion 29 a .
- This projecting portion 29 b is a counterpart of the stator inner peripheral passage closing portion 38 b in Embodiment 1, and is designed such that a smallest gap 29 c between the projecting portion 29 b and the disk portion 38 a of the balancer fixing bottom plate 38 is narrowed (for example, approximately 1 mm to 2 mm) within a range in which electrical short-circuiting does not occur. Note that, in a case where this design is employed, a pressure increasing effect by rotation of the cylindrical lateral wall about the drive shaft cannot be obtained.
- the hermetic compressor 100 configured as in Embodiment 3, the decrease in amount of the lubricating oil stored in the hermetic container 1 can be prevented.
- the effect of suppressing reliability degradation caused by insufficient lubrication and the effect of suppressing energy-saving performance degradation which are comparably less than those in Embodiment 1 but are equivalent thereto, can be obtained.
- FIG. 9 is a vertical sectional view of a structure of a hermetic compressor according to Embodiment 4 of the present invention.
- FIG. 10 is a horizontal sectional view of the structure of the hermetic compressor according to Embodiment 4 of the present invention (sectional view taken along the line A-A in FIG. 9 ).
- FIG. 11 is a perspective view of a rotary pressure increasing mechanism that is arranged on an upper portion of a rotator of the hermetic compressor according to Embodiment 4 of the present invention.
- the solid arrow shown in FIG. 10 indicates a rotation direction of the rotary pressure increasing mechanism.
- the rotary pressure increasing mechanism illustrated in FIG. 11 is viewed in a direction of the three-dimensional arrow shown in FIG. 10 .
- the hermetic compressor 100 according to Embodiment 4 is described. Note that, the fundamental structure and the operation of the hermetic compressor 100 according to Embodiment 4 are the same as those in Embodiment 1, and hence description thereof is omitted.
- the configuration of the hermetic compressor 100 according to Embodiment 4 is the same as the configuration of the hermetic compressor 100 described in Embodiment 2 except the configuration of the rotary pressure increasing mechanism 49 .
- the rotary pressure increasing mechanism 49 according to Embodiment 4 is obtained by removing all the vanes 41 from the centrifugal impeller 40 described in Embodiment 1.
- the rotary pressure increasing mechanism 49 according to Embodiment 4 includes an oil separating rotary disk 35 as a counterpart of the vane superjacent disk 43 in Embodiment 1, and a balancer cover 30 including a rotary disk 30 b and an inner peripheral flow guide 30 c as respective counterparts of the vane subjacent disk 44 and the inner peripheral flow guide 42 in Embodiment 1.
- the refrigerant that flows out from the rotator vents 26 flows into an inner passage 30 a formed on an inner peripheral side of the inner peripheral flow guide 30 c , flows between the rotary disk 30 b and the oil separating rotary disk 35 , and flows out into the electric motor rotator superjacent space 9 b (( 6 ) in FIG. 9 ) through a cup inner passage 36 d formed on an inner peripheral side of the oil separating cup 36 .
- a pressure increasing effect for example, 1 kPa or less
- rotations of the rotary disk 30 b of the balancer cover 30 , the oil separating rotary disk 35 , and the cylindrical lateral wall 36 a of the oil separating cup 36 can be obtained by rotations of the rotary disk 30 b of the balancer cover 30 , the oil separating rotary disk 35 , and the cylindrical lateral wall 36 a of the oil separating cup 36 .
- the hermetic compressor 100 configured as in Embodiment 4 the decrease in amount of the lubricating oil stored in the hermetic container 1 can be prevented.
- the effect of suppressing reliability degradation caused by insufficient lubrication and the effect of suppressing energy-saving performance degradation which are comparably less than (for example, less than half of) those in Embodiment 1 but are equivalent thereto, can be obtained.
- the hermetic compressor 100 configured as in Embodiment 4 there is an advantage in that a manufacturing cost for the rotary pressure increasing mechanism 49 is lower than that in Embodiment 1.
- Embodiments 1 to 4 the present invention is described with an example of the high-pressure shell hermetic scroll compressor.
- other rotary compression types such as sliding-vane type and swing type
- the same effects as those in Embodiments 1 to 4 can be obtained as long as the arrangement of the rotator 6 and the stator 7 of the electric motor 8 , and the flow of the refrigerant from the electric motor subjacent space 5 to the electric motor superjacent space 9 are unchanged.
- Embodiment 5 an example of the vapor compression-type refrigeration cycle device including the hermetic compressor 100 described in any one of Embodiments 1 to 4 is described.
- FIG. 12 is a configuration diagram of a vapor compression-type refrigeration cycle device 101 according to Embodiment 5.
- the vapor compression-type refrigeration cycle device 101 includes the hermetic compressor 100 described in any one of Embodiments 1 to 4, a radiator 102 for transferring heat of the refrigerant compressed by the hermetic compressor 100 , an expansion mechanism 103 for expanding the refrigerant that flows out from the radiator 102 , and an evaporator 104 for causing the refrigerant that flows out from the expansion mechanism 103 to receive heat.
- the hermetic compressor 100 according to any one of Embodiments 1 to 4 is used in the vapor compression-type refrigeration cycle device 101 , the vapor compression-type refrigeration cycle device 101 can be improved in energy saving efficiency, reduced in vibration and noise, and increased in reliability.
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Abstract
A hermetic compressor, includes: a hermetic container storing a lubricating oil; an electric motor; a drive shaft; a compression mechanism; a rotary pressure increasing mechanism increasing pressure of refrigerant gas; a cylindrical lateral wall partitioning a space above the electric motor into outer and inner spaces; and a discharge pipe allowing refrigerant to flow out from the inner space into an external circuit. The refrigerant gas discharged from the compression mechanism into the hermetic container is moved from a space below the electric motor up to an upper end of the rotator through rotator vents of the rotator, flows into the rotary pressure increasing mechanism to be increased in pressure, flows into the inner space to increase a pressure in the inner space, and is discharged to an outside through the discharge pipe while suppressing inflow of the refrigerant gas from the outer space to the inner space.
Description
- The present invention relates to a hermetic compressor, and a vapor compression-type refrigeration cycle device including the hermetic compressor. In particular, the present invention relates to a hermetic compressor excellent in oil separation effect, and a vapor compression-type refrigeration cycle device including the hermetic compressor.
- Hitherto, in a refrigerant compressor used in vapor compression-type refrigeration cycle devices (such as heat pump equipment and refrigeration cycle equipment), a rotational force of an electric motor is transmitted to a compression mechanism by a drive shaft so that refrigerant gas is compressed. In such a refrigerant compressor, the refrigerant gas compressed by the compression mechanism is discharged into a hermetic container, moved from a space below the electric motor into a space above the same through electric motor unit gas passages, and then discharged into a refrigerant circuit on an outside of the hermetic container. At this time, lubricating oil supplied to the compression mechanism and mixed with the refrigerant gas is discharged to the outside of the hermetic container. Hitherto, there is a problem in that an increase in amount of the oil to be discharged into the refrigerant circuit causes degradation in performance of a heat exchanger. In addition, there is another problem in that a decrease in amount of the oil stored in the hermetic container causes insufficient lubrication, resulting in degradation in reliability of the refrigerant compressor.
- In recent years, there have been promoted development of refrigerant compressors having smaller sizes, and conversion to use of alternative refrigerants (including natural refrigerant) having a lower environmental load. Under the circumstances, advanced technology for separating the oil in the hermetic container has been demanded. However, how the refrigerant and the lubricating oil flow and how the oil separation occurs during high speed rotation of the electric motor in the hermetic container are significantly complicated, and observation experiments in the hermetic container under high pressure are not easy. Thus, there are a large number of unknown factors, and a large number of technical problems have not yet been solved.
- In the high-pressure shell type scroll compressor disclosed in
Patent Literature 1, sucked refrigerant is compressed by the compression mechanism arranged on an upper side in the hermetic container, and once caused to flow down to an oil reservoir at a bottom of the hermetic container. After that, the refrigerant is caused to flow up from a space below the electric motor to a space above the same through electric motor gas passages, and then discharged as high pressure gas through a discharge pipe of the compressor. The high-pressure shell type scroll compressor disclosed inPatent Literature 1 includes a fan arranged on an upper portion of a rotator of the electric motor, and partition walls for separating a stator side of the electric motor and a rotator side of the electric motor from each other above the fan. Then, the refrigerant and the lubricating oil are separated from each other by using a centrifugal force generated by rotation of the fan and by using pressure resistance generated through gaps between the partition walls. The lubricating oil is prevented from flowing directly into the discharge pipe without being separated from the refrigerant, in other words, the lubricating oil is prevented from flowing out from the hermetic container. - Further, in
Patent Literature 2, there is disclosed an oil separation device for a hermetic electric compressor including: an electric component housed in an upper portion of a hermetic container; a compression component that is driven by the electric component; an oil separation plate arranged to face an upper end ring of a rotor of the electric component across a predetermined clearance; and stirring vanes arranged upright to the oil separation plate, in which the stirring vanes are arranged upright only to a lower surface of the oil separation plate. - Effects of improving an oil separation condition in the hermetic container of the compressor by using the fan and the partition walls in
Patent Literature 1 and the oil separation plate and the stirring vanes inPatent Literature 2 are generally observed. - Further, in recent years, by using significantly advanced three-dimensional fluid simulation technology, flow conditions of the refrigerant and the lubricating oil in the hermetic container of the compressor can be visualized. Thus, new findings are obtained. Specifically, in
Patent Literature 3, there is disclosed a refrigerant compressor in which an increase in head pressure that is generated near a leading end in a rotation direction of an upper balance weight at an upper end of the rotator of the electric motor arranged in the hermetic container is used to form an oil return passage from a vicinity of a leading end portion toward a lower end so that high density lubricating oil that appears around the rotator is returned below the electric motor, to thereby prevent the oil from flowing out. -
- Patent Literature 1: Japanese Patent No. 3925392
- Patent Literature 2: Japanese Unexamined Utility Model Application Publication No. Hei 5-61487
- Patent Literature 3: Japanese Unexamined Patent Application Publication No. 2009-264175
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- Non Patent Literature 1: “Turbofan and compressor”, Corona Publishing Co., Ltd. (1988)
- Non Patent Literature 2: “Fluid mechanical engineering”, Corona Publishing Co., Ltd. (1983)
- In general, to provide a high-performance centrifugal air-sending device, as described in
Non Patent Literature 1, the shape of the impeller itself, the shape of the passage of flow extending into the impeller, the shape of the passage of flow extending outside of the impeller, and the like need to be theoretically designed. - However, in
Patent Literatures - Specifically, in the high-pressure shell type scroll compressor disclosed in
Patent Literature 1, unless the fan and the partition walls to be attached on the upper portion of the rotator of the electric motor are appropriately designed and arranged, the fan and the partition walls cannot prevent the refrigerant, which flows from the compression mechanism into the space above the electric motor (refrigerant mixed with fine oil particles), from flowing from the stator side of the electric motor directly into the rotator side of the electric motor. Thus, there is a problem in that the oil separation effect cannot be fully exerted. - The present invention has been made to solve the problem as described above, and it is an object thereof to provide a hermetic compressor capable of reducing an amount of oil flowing to an outside of a hermetic container than that in the related art by using rotation of a rotator of an electric motor arranged in the hermetic container, and to provide a vapor compression-type refrigeration cycle device including the hermetic compressor.
- According to one embodiment of the present invention, there is provided a hermetic compressor, including: a hermetic container having a bottom portion for storing lubricating oil; an electric motor arranged in the hermetic container, the electric motor including: a stator and a rotator through which a rotator vent is formed in a vertical direction; a drive shaft attached to the rotator; a compression mechanism arranged in the hermetic container, for compressing refrigerant by using rotation of the drive shaft; a rotary pressure increasing mechanism arranged on an upper portion of the rotator, for increasing a pressure of refrigerant gas by allowing the refrigerant gas to flow through the rotary pressure increasing mechanism while rotating about the drive shaft; a cylindrical lateral wall for partitioning a space above the electric motor into an outer space on the stator side and inner space on the rotator side in such a manner that the cylindrical lateral wall surrounds the rotary pressure increasing mechanism positioned in the inner space; and a discharge pipe communicated to the inner space, for allowing the refrigerant to flow out from the inner space into an external circuit that is external to the hermetic container, in which the refrigerant gas that is compressed by the compression mechanism and discharged into the hermetic container is moved from a space below the electric motor up to an upper end of the rotator through the rotator vents, flows into the rotary pressure increasing mechanism to be increased in pressure, flows into the inner space to increase a pressure in the inner space, and is discharged to an outside through the discharge pipe while suppressing inflow of the refrigerant gas from the outer space to the inner space.
- Further, according to one embodiment of the present invention, there is provided a vapor compression-type refrigeration cycle device, including: the hermetic compressor of the one embodiment of the present invention; a radiator for transferring heat of refrigerant that is compressed by the hermetic compressor; an expansion mechanism for expanding the refrigerant that flows out from the radiator; and an evaporator for causing the refrigerant that flows out from the expansion mechanism to receive heat.
- The one embodiment of the present invention can prevent a decrease in amount of lubricating oil stored in the hermetic container and can obtain an effect of suppressing reliability degradation to be caused by insufficient lubrication, and an effect of achieving high energy-saving performance.
-
FIG. 1 is a vertical sectional view of a structure of a hermetic compressor according toEmbodiment 1 of the present invention. -
FIG. 2 is a horizontal sectional view of the structure of the hermetic compressor according toEmbodiment 1 of the present invention (sectional view taken along the line A-A inFIG. 1 ). -
FIG. 3 is a perspective view of a rotary pressure increasing mechanism that is arranged on an upper portion of a rotator of the hermetic compressor according toEmbodiment 1 of the present invention. -
FIG. 4 is a vertical sectional view of a structure of a hermetic compressor according toEmbodiment 2 of the present invention. -
FIG. 5 is a horizontal sectional view of the structure of the hermetic compressor according toEmbodiment 2 of the present invention (sectional view taken along the line A-A inFIG. 4 ). -
FIG. 6 is a perspective view of a rotary pressure increasing mechanism that is arranged on an upper portion of a rotator of the hermetic compressor according toEmbodiment 2 of the present invention. -
FIG. 7 is a vertical sectional view of a structure of a hermetic compressor according toEmbodiment 3 of the present invention. -
FIG. 8 is a horizontal sectional view of the structure of the hermetic compressor according toEmbodiment 3 of the present invention (sectional view taken along the line A-A inFIG. 7 ). -
FIG. 9 is a vertical sectional view of a structure of a hermetic compressor according toEmbodiment 4 of the present invention. -
FIG. 10 is a horizontal sectional view of the structure of the hermetic compressor according toEmbodiment 4 of the present invention (sectional view taken along the line A-A inFIG. 9 ). -
FIG. 11 is a perspective view of a rotary pressure increasing mechanism that is arranged on an upper portion of a rotator of the hermetic compressor according toEmbodiment 4 of the present invention. -
FIG. 12 is a configuration diagram of a vapor compression-type refrigeration cycle device according toEmbodiment 5 of the present invention. -
FIG. 1 is a vertical sectional view of a structure of a hermetic compressor according toEmbodiment 1 of the present invention.FIG. 2 is a horizontal sectional view of the structure of the hermetic compressor according toEmbodiment 1 of the present invention (sectional view taken along the line A-A inFIG. 1 ). Further,FIG. 3 is a perspective view of a rotary pressure increasing mechanism that is arranged on an upper portion of a rotator of the hermetic compressor according toEmbodiment 1 of the present invention. Note that, the solid arrow shown inFIG. 2 indicates a rotation direction of the rotary pressure increasing mechanism. Further, the rotary pressure increasing mechanism illustrated inFIG. 3 is viewed in a direction of the three-dimensional arrow shown inFIG. 2 . - First, with reference to
FIGS. 1 to 3 , a fundamental structure and operation of ahermetic compressor 100 according toEmbodiment 1 is described. - <Fundamental structure and operation of
hermetic compressor 100> - The
hermetic compressor 100 according toEmbodiment 1 is a high-pressure shell hermetic scroll compressor, which includes ahermetic container 1 having a bottom portion in which alower oil reservoir 2 for storing lubricating oil is formed, and anelectric motor 8, adrive shaft 3, acompression mechanism 60, and a rotarypressure increasing mechanism 49 that are housed in thehermetic container 1. - The
electric motor 8 includes a substantiallycylindrical stator 7 having an inner peripheral portion through which a through-hole is formed in a vertical direction, and a substantiallycylindrical rotator 6 arranged on an inner peripheral side of thestator 7 across apredetermined air gap 27 a. Theelectric motor 8 according toEmbodiment 1 is, for example, a DC brushless motor. Thestator 7 is formed of laminated steel plates, and includes acore 7 c that is formed into a wound coil block by winding a coil therearound at a high density. Further, at an upper end of thestator 7, coil parts projecting from the wound coil block toward an upper side of thestator 7, that is, a plurality of electric motor upper coil-interconnectingportion 7 a are formed. At a lower end of thestator 7, coil parts projecting from the wound coil block toward a lower side of thestator 7, that is, a plurality of electric motor lower coil-interconnectingportions 7 b are formed. Thisstator 7 is attached to an inner peripheral surface of thehermetic container 1 by press fitting, welding, and the like. Note that, an outer peripheral portion of thecore 7 c of thestator 7 is partially cut out so that stator outerperipheral passages 25 are formed between the core 7 c and thehermetic container 1 under a state in which thestator 7 is attached to the inner peripheral surface of thehermetic container 1. - The
rotator 6 is formed by laminating steel plates and sandwiching uppermost and lowermost ones of the laminated steel plates respectively with a rotator upperend fixing substrate 33 and a rotator lowerend fixing substrate 34. Further, magnets are arranged in therotator 6. Still further, respectively on an upper surface of the rotator upperend fixing substrate 33 and a lower surface of the rotator lowerend fixing substrate 34, anupper balance weight 31 and alower balance weight 32, which have a predetermined thickness and are arranged in reverse phases, are arranged along outer rims of therotator 6. Yet further, fourrotator vents 26 are formed in the vertical direction through therotator 6 according toEmbodiment 1. Note that, the number of the rotator vents 26 is not particularly limited as long as at least onerotator vent 26 is formed. - A lower end portion of the
drive shaft 3 is attached to therotator 6 of theelectric motor 8, and an upper end portion thereof is attached to thecompression mechanism 60 described below. In other words, thedrive shaft 3 is configured to transmit a driving force of theelectric motor 8 to thecompression mechanism 60. An upper side of thedrive shaft 3 is held in a freely rotatable manner by amain bearing unit 55 of anupper bearing member 11 arranged above theelectric motor 8, and a lower side thereof is held in a freely rotatable manner by asub bearing unit 54 of alower bearing member 12 arranged below theelectric motor 8. - The
compression mechanism 60 is arranged above theelectric motor 8, and includes a fixedscroll 51 and anorbiting scroll 52. Plate-like scroll teeth are formed on a lower surface of the fixedscroll 51, which is attached to acompression mechanism casing 50 that is fixed to the inner peripheral surface of thehermetic container 1. Plate-like scroll teeth to mesh with the plate-like scroll teeth of the fixedscroll 51 are formed on an upper surface of the orbitingscroll 52, which is provided in a freely slidable manner at the upper end portion of thedrive shaft 3. When the plate-like scroll teeth of the fixedscroll 51 and the plate-like scroll teeth of the orbitingscroll 52 mesh with each other,compression chambers 4 are formed between the plate-like scroll teeth on both sides. A lower surface of the orbitingscroll 52 is supported in a freely slidable manner by an upper surface portion of theupper bearing member 11. An outer peripheral surface of theupper bearing member 11 is supported in a freely slidable manner by an inner peripheral surface of thecompression mechanism casing 50. With this configuration, theupper bearing member 11 can be retracted downward in response to application of pressure of a predetermined value or more in thecompression chamber 4, and thus an abnormal pressure increase in thecompression chamber 4 can be avoided. - Note that, a
refrigerant passage 57 is formed between an outer peripheral portion of thecompression mechanism casing 50 and thehermetic container 1. Further, adischarge cover 56 for partitioning an electric motor superjacent space 9 (more specifically, upper part of a cylindricallateral wall 37 described below) into an electric motor statorsuperjacent space 9 a (outer space) and an electric motor rotatorsuperjacent space 9 b (inner space) is arranged under thecompression mechanism casing 50. - The rotary
pressure increasing mechanism 49 is arranged on an upper portion of therotator 6. The rotarypressure increasing mechanism 49 according toEmbodiment 1 is acentrifugal impeller 40, which includes a plurality ofvanes 41 arranged in a manner of extending from an inner peripheral side to an outer peripheral side about thedrive shaft 3. Further, thecentrifugal impeller 40 according toEmbodiment 1 also includes a vane superjacent disk 43 (upper surface plate) for blocking inflow of refrigerant gas from above thevanes 41 into thecentrifugal impeller 40, and a vane subjacent disk 44 (lower surface plate) for blocking inflow of refrigerant gas from below thevanes 41 into thecentrifugal impeller 40. Further, to prevent inflow of refrigerant gas through passages other than the rotator vents 26 into an inlet on an inner peripheral side of thecentrifugal impeller 40, an inner peripheral flow guide 42 (partition plate) is extended downward from a rim of an opening portion of the vanesubjacent disk 44, which is formed at a position on an inner peripheral side of thevanes 41, in a manner that an outer peripheral portion of the rotator vents 26 is surrounded. Thecentrifugal impeller 40 is rotated about thedrive shaft 3 through, for example, connection between thedrive shaft 3 and the vanesuperjacent disk 43, connection between the cylindricallateral wall 37 described below and the vanesubjacent disk 44, or connection between therotator 6 and the innerperipheral flow guide 42. With this configuration, the refrigerant that flows in through the inlet on the inner peripheral side is increased in pressure and is caused to flow out through an outlet on the outer peripheral side. - Further, in the
hermetic compressor 100 according toEmbodiment 1, the cylindricallateral wall 37 is arranged to surround the centrifugal impeller 40 (more specifically, refrigerant outlet on the outer peripheral side), in other words, to partition the electric motorsuperjacent space 9 into the electric motor statorsuperjacent space 9 a (outer space) and the electric motor rotatorsuperjacent space 9 b (inner space). Further, in the cylindricallateral wall 37, anoil drain hole 39 is formed on a rotation direction leadingend portion 31 a side of theupper balance weight 31. This cylindricallateral wall 37 is attached to an upper surface portion of adisk portion 38 a of a balancer fixingbottom plate 38 for fixing theupper balance weight 31 to the rotator upperend fixing substrate 33. Further, inEmbodiment 1, a stator inner peripheralpassage closing portion 38 b (closing member) is arranged to project from an outer peripheral portion of thedisk portion 38 a of the balancer fixingbottom plate 38. This stator inner peripheralpassage closing portion 38 b is arranged to close an upper part of a stator innerperipheral passage 27 formed between therotator 6 and the stator 7 (specifically,air gap 27 a between therotator 6 and thestator 7, and core inner peripheral portion cut-out passage 27 b formed by cutting out the inner peripheral side of the stator 7). - In the
hermetic compressor 100 configured as described above, the orbitingscroll 52 of thecompression mechanism 60 performs eccentric orbital operation along with rotation of thedrive shaft 3, causing sucked low-pressure refrigerant to enter thecompression chamber 4 through acompressor suction pipe 21. Then, the sucked pressure refrigerant is increased in pressure through a compression step of gradually decreasing a volume of thecompression chamber 4, and is discharged into a discharge space 10 ((1) inFIG. 1 ) in thehermetic container 1 through adischarge port 18 of the fixedscroll 51. - Further, along with the rotation of the
drive shaft 3, the lubricating oil stored in thelower oil reservoir 2 is sucked upward from a lower end of thedrive shaft 3, and flows into ahollow hole 3 a. Part of the lubricating oil is supplied, for example, to thesub bearing unit 54 and themain bearing unit 55 through oil supply holes (not shown). Further, part of the lubricating oil flows out from an upper end of thedrive shaft 3, and then is supplied into thecompression chamber 4 through, for example, a gap between theupper bearing member 11 and the orbitingscroll 52 and anoil supply hole 3 b, increasing effects of lubrication of thecompression mechanism 60 and sealing of the compressed gas. The lubricating oil that is supplied in thecompression chamber 4 is discharged into the discharge space 10 ((1) inFIG. 1 ) in thehermetic container 1 through thedischarge port 18 of the fixedscroll 51 together with the refrigerant compressed to have a high pressure in thecompression chamber 4. - <Flow of Refrigerant in Hermetic Container>
- The refrigerant that is discharged through the
discharge port 18 flows downward through therefrigerant passage 57 formed of a gap between an outer peripheral side of thecompression mechanism casing 50 and thehermetic container 1, and reaches the electric motor statorsuperjacent space 9 a ((2) inFIG. 1 ). Further, this refrigerant flows downward into an electric motor stator subjacent space ((3) inFIG. 1 ) in an electric motorsubjacent space 5 through the stator outerperipheral passages 25 formed between the core 7 c of thestator 7 and thehermetic container 1, and reaches thelower bearing member 12 including thesub bearing unit 54. During this process, the refrigerant and the lubricating oil mixed in an atomized form with the refrigerant are separated from each other, and the separated lubricating oil is refluxed to thelower oil reservoir 2 through anoil return hole 12 a formed through thelower bearing member 12. - Meanwhile, the refrigerant that flows in the electric motor stator subjacent space in the electric motor
subjacent space 5 flows up from an electric motor rotator subjacent space ((4) inFIG. 1 ) in the electric motorsubjacent space 5 through the rotator vents 26 into a vaneinner passage 46 of thecentrifugal impeller 40 attached on an upper portion of the rotator 6 (passage on an inner peripheral side of the innerperipheral flow guide 42, that is, space represented by (5) inFIG. 1 ). Then, the refrigerant that flows in the vaneinner passage 46 is sucked intointer-vane passages 47 formed between thevanes 41 of thecentrifugal impeller 40, flows to the outer peripheral side while being increased in pressure in accordance with a rotational speed of thecentrifugal impeller 40, and, on an outer peripheral side of thevanes 41, flows up through a vaneouter passage 48 formed in a region on an inner peripheral side of the cylindricallateral wall 37. Then, this refrigerant is once released into the electric motor rotatorsuperjacent space 9 b ((6) inFIG. 1 ) that is formed above the circular vanesuperjacent disk 43 covering upper surfaces of thevanes 41 of thecentrifugal impeller 40 and on the inner peripheral side of the cylindricallateral wall 37. With this, static pressure is increased. After that, the refrigerant that flows in the electric motor rotatorsuperjacent space 9 b ((6) inFIG. 1 ) flows into thedischarge cover 56 through an openingportion 56 a of thedischarge cover 56, and then is discharged into an external circuit on an outside of thehermetic container 1 through acompressor discharge pipe 22 that communicates to an inner space of thedischarge cover 56. - <Flow in
Short Circuit Passage 23 and Short-Circuit Prevention> - To prevent electrical short-circuiting between the electric motor upper coil-interconnecting
portions 7 a and thedischarge cover 56, a gap between the electric motor upper coil-interconnectingportions 7 a and thedischarge cover 56, that is, ashort circuit passage 23 needs to be formed. Thus, during the process from the discharge space 10 ((1) inFIG. 1 ) to the electric motor rotatorsuperjacent space 9 b ((6) inFIG. 1 ), the refrigerant may flow from the electric motor statorsuperjacent space 9 a ((2) inFIG. 1 ) directly into the electric motor rotatorsuperjacent space 9 b ((6) inFIG. 1 ) without flowing through the electric motor stator subjacent space ((3) inFIG. 1 ). As a result, a large number of droplets of unseparated oil may flow out from thehermetic container 1 to the external circuit, which may cause degradation in performance and reliability of thehermetic compressor 100, and degradation in performance of the vapor compression-type refrigeration cycle device (in particular, of the heat exchanger). - In view of the circumstances, to reduce an amount of the flow of the refrigerant that short-circuits to be directly discharged through the
short circuit passage 23, the following measures need to be taken. - (1) Set a passage resistance of the
short circuit passage 23 to the electric motor rotatorsuperjacent space 9 b ((6) inFIG. 1 ) to be sufficiently high. - (2) Increase a pressure in the electric motor rotator
superjacent space 9 b ((6) inFIG. 1 ) to be close to or higher than a pressure in the electric motor statorsuperjacent space 9 a. - Thus, in
Embodiment 1, the cylindricallateral wall 37 is arranged upright to the balancer fixingbottom plate 38 so that a passage area of theshort circuit passage 23 is reduced, and thus the passage resistance is increased. Further, a lower end portion of thedischarge cover 56 is bent so that a passage shape of theshort circuit passage 23 is made complicated, and thus the passage resistance of theshort circuit passage 23 is further increased. - In addition, in
Embodiment 1, the cylindricallateral wall 37 is interposed to separate thecentrifugal impeller 40 arranged on therotator 6 and the electric motor upper coil-interconnectingportions 7 a from each other. With this, the refrigerant gas that is increased in pressure by thecentrifugal impeller 40 can be suppressed from reversely flowing into the electric motor statorsuperjacent space 9 a ((2) inFIG. 1 ) throughradial passages 28 in the electric motor upper coil-interconnectingportions 7 a. As a result, the pressure in the electric motor rotatorsuperjacent space 9 b ((6) inFIG. 1 ) can be increased. - Note that, other than the rotator vents 26, the stator inner peripheral passage 27 (
air gap 27 a and core inner peripheral portion cut-out passage 27 b) is formed as an upward refrigerant passage from the electric motor subjacent space 5 ((3) or (4) inFIG. 1 ) to the electric motor superjacent space 9 ((2) or (5) inFIG. 1 ), and the pressure increasing effect by thecentrifugal impeller 40 cannot be exerted to the refrigerant gas that flows through the stator innerperipheral passage 27. Therefore, a greater pressure increasing effect can be obtained by thecentrifugal impeller 40 when the stator innerperipheral passage 27 is closed as much as possible. Thus, inEmbodiment 1, to slightly increase an outer diameter of the balancer fixing bottom plate 38 (for example, approximately 1 mm), the stator inner peripheralpassage closing portion 38 b is arranged to the outer peripheral portion of thedisk portion 38 a so that the upper part of the stator innerperipheral passage 27 is closed. With this, an amount of the refrigerant gas that flows through the stator innerperipheral passage 27 can be suppressed, and thus the pressure in the electric motor rotatorsuperjacent space 9 b ((6) inFIG. 1 ) can be further increased. - <Design of Centrifugal Impeller>
- To increase the pressure in the electric motor rotator
superjacent space 9 b ((6) inFIG. 1 ) with thecentrifugal impeller 40 such that approximately 100% of the refrigerant flows from the electric motor statorsuperjacent space 9 a ((2) inFIG. 1 ) to the electric motor stator subjacent space ((3) inFIG. 1 ), the shape of the vanes and the passages of thecentrifugal impeller 40 need to be designed such that a pressure (P6) in the electric motor rotatorsuperjacent space 9 b ((6) inFIG. 1 ) is higher than a pressure (P2) in the electric motor statorsuperjacent space 9 a ((2) inFIG. 1 ). Further, to increase a pressure in thecentrifugal impeller 40, input to the compressor (electric power consumption thereof) is increased. Thus, it is also important to design a highly-efficientcentrifugal impeller 40. - According to Non Patent Literature 2 (p. 132), of centrifugal fans, a turbofan (having vanes that are formed rearward with respect to a rotation direction) is advantageous in terms of efficiency. Thus, the shape of the
vanes 41 of thecentrifugal impeller 40 is determined to be rearward with respect to the rotation direction, and eightvanes 41 formed into this shape are arranged in axial symmetry with respect to thedrive shaft 3. Further, an inlet angle of each of thevanes 41 is determined such that thevanes 41 each form an angle within a range of ±5 degrees with respect to a circle formed by connecting end positions on the inner peripheral side of thevanes 41. This is because, according to Non Patent Literature 1 (p. 216), a collision loss occurs when an entry angle ib that is equal to a difference between a relative inflow angle 131 and a vane inlet angle β1 b at an inlet of the impeller ranges from 2 degrees to 5 degrees or more, causing losses in the compressor. Note that, to increase a percentage by which the refrigerant that flows through the rotator vents 26 flows into the inner peripheral side of thecentrifugal impeller 40, and then flows out to the outer peripheral side thereof (passage rate), the following configurations are devised. -
- The rotator vents 26 are arranged on an inner side with respect to the inner
peripheral flow guide 42 in plan view. - The vane
superjacent disk 43 and the vanesubjacent disk 44 for covering the upper and lower sides of thevanes 41 are configured to cover all over the inner peripheral side to the outer peripheral side of the plurality ofvanes 41.
- The rotator vents 26 are arranged on an inner side with respect to the inner
- With this, the pressure increasing effect by the
centrifugal impeller 40 can be further increased, and the pressure in the electric motor rotatorsuperjacent space 9 b ((6) inFIG. 1 ) can be further increased. - <Effects>
- In the
hermetic compressor 100 configured as inEmbodiment 1, the pressure in the electric motor rotatorsuperjacent space 9 b ((6) inFIG. 1 ) can be increased by using rotation of therotator 6 in thehermetic container 1. Specifically, when thehermetic compressor 100 that is configured to output three horsepower and operated at a constant speed (50 rps), is operated by using a refrigerant R22 under the condition of Ashrae standard, an effect of increasing the pressure in the electric motor rotatorsuperjacent space 9 b ((6) inFIG. 1 ) in units of several kPa can be obtained. As a result, the refrigerant is less liable to flow from the electric motor statorsuperjacent space 9 a ((2) inFIG. 1 ) directly into the electric motor rotatorsuperjacent space 9 b ((6) inFIG. 1 ) through theshort circuit passage 23, and the large number of droplets of the unseparated oil are less liable to flow out from thehermetic container 1 to the external circuit. Further, to effectively use the sealed lubricating oil, an effect of suppressing the degradation in performance of thehermetic compressor 100, and an effect of suppressing the degradation in reliability thereof due to insufficient lubrication that may be caused by a decrease in amount of the oil stored in thehermetic container 1 can be obtained. -
FIG. 4 is a vertical sectional view of a structure of a hermetic compressor according toEmbodiment 2 of the present invention.FIG. 5 is a horizontal sectional view of the structure of the hermetic compressor according toEmbodiment 2 of the present invention (sectional view taken along the line A-A inFIG. 4 ). Further,FIG. 6 is a perspective view of a rotary pressure increasing mechanism that is arranged on an upper portion of a rotator of the hermetic compressor according toEmbodiment 2 of the present invention. Note that, the solid arrow shown inFIG. 5 indicates a rotation direction of the rotary pressure increasing mechanism. Further, the rotary pressure increasing mechanism illustrated inFIG. 6 is viewed in a direction of the three-dimensional arrow shown inFIG. 5 . - Now, with reference to
FIGS. 4 to 6 , thehermetic compressor 100 according toEmbodiment 2 is described. Note that, the fundamental structure and the operation of thehermetic compressor 100 according toEmbodiment 2 are the same as those inEmbodiment 1, and hence description thereof is omitted. - (1)
Embodiment 2 is different fromEmbodiment 1 in that only four of the eightvanes 41 of thecentrifugal impeller 40 inEmbodiment 1 that are positioned on one side on which theupper balance weight 31 is absent are left, and that a height of each of the fourvanes 41 is designed to be equal to a height of theupper balance weight 31. InEmbodiment 1, to allow the refrigerant flowing through the rotator vents 26 to flow out from thecentrifugal impeller 40 through the vaneinner passage 46, the innerperipheral flow guide 42 and the vanesubjacent disk 44 are needed. In contrast, inEmbodiment 2, there is an advantage in that the innerperipheral flow guide 42 and the vanesubjacent disk 44 can be omitted, and hence thecentrifugal impeller 40 is easily processed. - Note that, in a case where the
centrifugal impeller 40 is configured as inEmbodiment 2, fan efficiency is lower than that of thecentrifugal impeller 40 according toEmbodiment 1, in which thevanes 41 are arranged in axial symmetry. Further, in the case where thecentrifugal impeller 40 is configured as inEmbodiment 2, pressure pulsation by thecentrifugal impeller 40 is increased in comparison with that by thecentrifugal impeller 40 according toEmbodiment 1, in which thevanes 41 are arranged in axial symmetry. As a result, vibration and noise may occur. Thus, in a case where the fan efficiency and prevention of the vibration and noise are regarded as important, it is preferred that thecentrifugal impeller 40 be configured as inEmbodiment 1. - (2) In
Embodiment 1, the cylindricallateral wall 37 for preventing short-circuit flow of the refrigerant through theshort circuit passage 23, and the balancer fixingbottom plate 38 for fixing the cylindricallateral wall 37 are formed as separate members. Meanwhile, inEmbodiment 2, the cylindricallateral wall 37 and the balancer fixingbottom plate 38 according toEmbodiment 1 are provided as anoil separating cup 36 obtained by a process of integrating a cylindricallateral wall 36 a and abottom plate 36 b with each other. Note that, similarly toEmbodiment 1, anoil drain hole 36 c is formed in theoil separating cup 36 on the rotation direction leadingend portion 31 a side of theupper balance weight 31. When theoil separating cup 36 obtained by the process of integrating the cylindricallateral wall 36 a and thebottom plate 36 b with each other is provided instead of the cylindricallateral wall 37 and the balancer fixingbottom plate 38 according toEmbodiment 1, there is an advantage in that a process of assembling thehermetic compressor 100 can be facilitated. - In this way, according to the
hermetic compressor 100 configured as inEmbodiment 2, the decrease in amount of the lubricating oil stored in thehermetic container 1 can be prevented. In addition, an effect of suppressing reliability degradation caused by insufficient lubrication and an effect of suppressing energy-saving performance degradation, which are comparably less than those inEmbodiment 1 but are equivalent thereto, can be obtained. Meanwhile, according to thehermetic compressor 100 configured as inEmbodiment 2, there is an advantage in that a manufacturing cost for thecentrifugal impeller 40 is lower than that inEmbodiment 1. - (3) Note that, other differences between the
hermetic compressor 100 according toEmbodiment 2 and thehermetic compressor 100 described inEmbodiment 1 are as follows. -
- In the
hermetic compressor 100 according toEmbodiment 2, the lower end portion of thedischarge cover 56 is not subjected to a bending process, and hence theshort circuit passage 23 has a simple shape. Thus, in thehermetic compressor 100 according toEmbodiment 2, the passage resistance in theshort circuit passage 23 is determined based on a size of a smallest gap that is formed between thedischarge cover 56 and the cylindricallateral wall 36 a. - Further, the
hermetic compressor 100 according toEmbodiment 2 does not include the closing member for closing the stator inner peripheral passage 27 (counterpart of the stator inner peripheralpassage closing portion 38 b in Embodiment 1).
- In the
-
FIG. 7 is a vertical sectional view of a structure of a hermetic compressor according toEmbodiment 3 of the present invention.FIG. 8 is a horizontal sectional view of the structure of the hermetic compressor according toEmbodiment 3 of the present invention (sectional view taken along the line A-A inFIG. 7 ). Note that, the solid arrow shown inFIG. 8 indicates a rotation direction of the rotary pressure increasing mechanism. - Now, with reference to
FIGS. 7 and 8 , thehermetic compressor 100 according toEmbodiment 3 is described. Note that, the fundamental structure and the operation of thehermetic compressor 100 according toEmbodiment 3 are the same as those inEmbodiment 1, and hence description thereof is omitted. - (1) Similarly to
Embodiment 2, in thecentrifugal impeller 40 according toEmbodiment 3, only four of the eightvanes 41 of thecentrifugal impeller 40 inEmbodiment 1 that are positioned on the one side on which theupper balance weight 31 is absent are left, and the height of each of the fourvanes 41 is designed to be equal to the height of theupper balance weight 31. However, thecentrifugal impeller 40 according toEmbodiment 3 is different from that according toEmbodiment 2 in that thevanes 41 are arranged in a radial direction (direction orthogonal to the rotation direction of the drive shaft 3). With this, although fan efficiency is lower than that of the turbofan, there is an advantage in that thecentrifugal impeller 40 can be easily manufactured. - (2) In
Embodiments lateral wall 37 or cylindricallateral wall 36 a) for preventing the short-circuit flow of the refrigerant through theshort circuit passage 23 is arranged on the upper portion of therotator 6 so that the cylindrical lateral wall is rotated together with therotator 6. In contrast, inEmbodiment 3, a closing cover 29 (more specifically,cylindrical portion 29 a) as a counterpart of the cylindrical lateral wall is arranged on an inner side of the electric motor upper coil-interconnectingportions 7 a of thestator 7 so that theradial passages 28 are closed. Further, in theclosing cover 29, on an inner peripheral side of thecylindrical portion 29 a, a projectingportion 29 b for closing the upper part of the stator innerperipheral passage 27 is formed. This projectingportion 29 b is a counterpart of the stator inner peripheralpassage closing portion 38 b inEmbodiment 1, and is designed such that asmallest gap 29 c between the projectingportion 29 b and thedisk portion 38 a of the balancer fixingbottom plate 38 is narrowed (for example, approximately 1 mm to 2 mm) within a range in which electrical short-circuiting does not occur. Note that, in a case where this design is employed, a pressure increasing effect by rotation of the cylindrical lateral wall about the drive shaft cannot be obtained. - In this way, according to the
hermetic compressor 100 configured as inEmbodiment 3, the decrease in amount of the lubricating oil stored in thehermetic container 1 can be prevented. In addition, the effect of suppressing reliability degradation caused by insufficient lubrication and the effect of suppressing energy-saving performance degradation, which are comparably less than those inEmbodiment 1 but are equivalent thereto, can be obtained. -
FIG. 9 is a vertical sectional view of a structure of a hermetic compressor according toEmbodiment 4 of the present invention.FIG. 10 is a horizontal sectional view of the structure of the hermetic compressor according toEmbodiment 4 of the present invention (sectional view taken along the line A-A inFIG. 9 ). Further,FIG. 11 is a perspective view of a rotary pressure increasing mechanism that is arranged on an upper portion of a rotator of the hermetic compressor according toEmbodiment 4 of the present invention. Note that, the solid arrow shown inFIG. 10 indicates a rotation direction of the rotary pressure increasing mechanism. Further, the rotary pressure increasing mechanism illustrated inFIG. 11 is viewed in a direction of the three-dimensional arrow shown inFIG. 10 . - Now, with reference to
FIGS. 9 to 11 , thehermetic compressor 100 according toEmbodiment 4 is described. Note that, the fundamental structure and the operation of thehermetic compressor 100 according toEmbodiment 4 are the same as those inEmbodiment 1, and hence description thereof is omitted. - (1) The configuration of the
hermetic compressor 100 according toEmbodiment 4 is the same as the configuration of thehermetic compressor 100 described inEmbodiment 2 except the configuration of the rotarypressure increasing mechanism 49. Specifically, the rotarypressure increasing mechanism 49 according toEmbodiment 4 is obtained by removing all thevanes 41 from thecentrifugal impeller 40 described inEmbodiment 1. In other words, the rotarypressure increasing mechanism 49 according toEmbodiment 4 includes an oil separatingrotary disk 35 as a counterpart of the vanesuperjacent disk 43 inEmbodiment 1, and abalancer cover 30 including arotary disk 30 b and an innerperipheral flow guide 30 c as respective counterparts of the vanesubjacent disk 44 and the innerperipheral flow guide 42 inEmbodiment 1. In the rotarypressure increasing mechanism 49 configured in this way, the refrigerant that flows out from the rotator vents 26 flows into aninner passage 30 a formed on an inner peripheral side of the innerperipheral flow guide 30 c, flows between therotary disk 30 b and the oil separatingrotary disk 35, and flows out into the electric motor rotatorsuperjacent space 9 b ((6) inFIG. 9 ) through a cupinner passage 36 d formed on an inner peripheral side of theoil separating cup 36. In the rotarypressure increasing mechanism 49 according toEmbodiment 4, although the great pressure increasing effect (for example, in units of several kPa) by the centrifugal impeller cannot be obtained, a pressure increasing effect (for example, 1 kPa or less) can be obtained by rotations of therotary disk 30 b of thebalancer cover 30, the oil separatingrotary disk 35, and the cylindricallateral wall 36 a of theoil separating cup 36. - In this way, according to the
hermetic compressor 100 configured as inEmbodiment 4, the decrease in amount of the lubricating oil stored in thehermetic container 1 can be prevented. In addition, the effect of suppressing reliability degradation caused by insufficient lubrication and the effect of suppressing energy-saving performance degradation, which are comparably less than (for example, less than half of) those inEmbodiment 1 but are equivalent thereto, can be obtained. Meanwhile, according to thehermetic compressor 100 configured as inEmbodiment 4, there is an advantage in that a manufacturing cost for the rotarypressure increasing mechanism 49 is lower than that inEmbodiment 1. - In
Embodiments 1 to 4, the present invention is described with an example of the high-pressure shell hermetic scroll compressor. In this context, also when other rotary compression types (such as sliding-vane type and swing type) are employed, the same effects as those inEmbodiments 1 to 4 can be obtained as long as the arrangement of therotator 6 and thestator 7 of theelectric motor 8, and the flow of the refrigerant from the electric motorsubjacent space 5 to the electric motorsuperjacent space 9 are unchanged. - In
Embodiment 5, an example of the vapor compression-type refrigeration cycle device including thehermetic compressor 100 described in any one ofEmbodiments 1 to 4 is described. -
FIG. 12 is a configuration diagram of a vapor compression-typerefrigeration cycle device 101 according toEmbodiment 5. The vapor compression-typerefrigeration cycle device 101 includes thehermetic compressor 100 described in any one ofEmbodiments 1 to 4, aradiator 102 for transferring heat of the refrigerant compressed by thehermetic compressor 100, anexpansion mechanism 103 for expanding the refrigerant that flows out from theradiator 102, and anevaporator 104 for causing the refrigerant that flows out from theexpansion mechanism 103 to receive heat. When thehermetic compressor 100 according to any one ofEmbodiments 1 to 4 is used in the vapor compression-typerefrigeration cycle device 101, the vapor compression-typerefrigeration cycle device 101 can be improved in energy saving efficiency, reduced in vibration and noise, and increased in reliability. -
-
- 1
hermetic container 2lower oil reservoir 3drive shaft 3 ahollow hole 3 boil supply hole 4compression chamber 5 electric motorsubjacent space 6rotator 7stator 7 a electric motor upper coil-interconnectingportion 7 b electric motor lower coil-interconnectingportion 7c core 8electric motor 9 electric motorsuperjacent space 9 a electric motor statorsuperjacent space 9 b electric motor rotatorsuperjacent space 10discharge space 11upper bearing member 12lower bearing member 12 aoil return hole 18discharge port 21compressor suction pipe 22compressor discharge pipe 23short circuit passage 25 stator outerperipheral passage 26rotator vent 27 stator innerperipheral passage 27 aair gap 27 b core inner peripheral portion cut-out passage 28radial passage 29 closing cover - 29 a
cylindrical portion 29 b projecting portion for closing stator innerperipheral passage 29 csmallest gap 30 balancer cover 30 ainner passage 30b rotary disk 30 c innerperipheral flow guide 31upper balance weight 31 a rotation direction leadingend portion 31 b rotation direction trailingend portion 32lower balance weight 33 rotator upperend fixing substrate 34 rotator lowerend fixing substrate 35 oil separating rotary disk (single member) 36oil separating cup 36 a cylindrical lateral wall - 36
b bottom plate 36 coil drain hole 36 d cupinner passage 37 cylindrical lateral wall (single member) 38 balancer fixingbottom plate 38 adisk portion 38 b stator inner peripheralpassage closing portion 39oil drain hole 40centrifugal impeller 41vane 42 innerperipheral flow guide 43 vanesuperjacent disk 44 vanesubjacent disk 46 vaneinner passage 47inter-vane passage 48 vaneouter passage 49 rotarypressure increasing mechanism 50compression mechanism casing 51 fixedscroll 52 orbitingscroll 54sub bearing unit 55main bearing unit 56 discharge cover - 56 a
opening portion 57refrigerant passage 60compression mechanism 100hermetic compressor 101 vapor compression-typerefrigeration cycle device 102radiator 103expansion mechanism 104 evaporator
- 1
Claims (10)
1: A hermetic compressor, comprising:
a hermetic container having a bottom portion for storing lubricating oil;
an electric motor arranged in the hermetic container, the electric motor including:
a stator; and
a rotator through which a rotator vent is formed in a vertical direction;
a drive shaft attached to the rotator;
a scroll-type compression mechanism arranged in the hermetic container, for compressing refrigerant by rotation of the drive shaft and discharging the compressed refrigerant into the hermetic container,
a rotary pressure increasing mechanism arranged on an upper portion of the rotator, for increasing a pressure of refrigerant gas flowing from a space below the electric motor through the rotator vent into the rotary pressure increasing mechanism by allowing the refrigerant gas to flow through the rotary pressure increasing mechanism while rotating about the drive shaft,
a cylindrical lateral wall for partitioning a space above the electric motor into an outer space on a stator side and an inner space on a rotator side in such a manner that the cylindrical lateral wall surrounds the rotary pressure increasing mechanism; and
a discharge pipe communicated to the inner space, for allowing the refrigerant to flow out from the inner space into an external circuit that is external to the hermetic container,
the rotary pressure increasing mechanism being configured to make a pressure in the inner space larger than a pressure in the outer space.
2: The hermetic compressor of claim 1 , wherein the rotary pressure increasing mechanism comprises a centrifugal impeller that is rotated about the drive shaft so that the refrigerant gas flows into the centrifugal impeller through an inlet on an inner peripheral side, and flows out through an outlet on an outer peripheral side while being increased in pressure.
3: The hermetic compressor of claim 2 , wherein the cylindrical lateral wall is arranged to surround the outlet on the outer peripheral side of the centrifugal impeller.
4: The hermetic compressor of claim 2 , wherein the centrifugal impeller comprises:
a lower surface plate for blocking inflow of the refrigerant gas from a region below vanes of the centrifugal impeller into the centrifugal impeller;
an upper surface plate for blocking inflow of the refrigerant gas from a region above the vanes of the centrifugal impeller into the centrifugal impeller; and
a partition plate for blocking inflow of the refrigerant gas into the inlet on the inner peripheral side of the centrifugal impeller through passages other than the rotator vents.
5: The hermetic compressor of claim 1 ,
wherein the stator comprises a plurality of electric motor upper coil-interconnecting portions formed of projecting parts of a coil wound around a core, the projecting parts projecting from an upper end of the stator, and
wherein the cylindrical lateral wall is interposed to separate the rotary pressure increasing mechanism and the electric motor upper coil-interconnecting portions from each other.
6: The hermetic compressor of claim 1 , further comprising a closing member for closing an upper part of a passage formed between the rotator and the stator.
7: The hermetic compressor of claim 1 , wherein the cylindrical lateral wall is arranged to an upper end of the rotator, and is rotated together with the rotator.
8: The hermetic compressor of claim 1 ,
wherein the compression mechanism is arranged above the electric motor, and
wherein the refrigerant gas that is compressed by the compression mechanism and discharged into the hermetic container flows from the outer space into the space below the electric motor through stator outer peripheral passages formed between the stator and the hermetic container, is moved from the space below the electric motor up to an upper end of the rotator through the rotator vents, flows into the rotary pressure increasing mechanism to be increased in pressure, flows into the inner space to increase the pressure in the inner space, and is discharged to an outside through the discharge pipe while suppressing inflow of the refrigerant gas from the outer space to the inner space.
9: The hermetic compressor of claim 8 , further comprising a discharge cover for partitioning a part of the space above the electric motor, which is positioned above the cylindrical lateral wall, into the outer space and the inner space, the discharge cover being arranged under the compression mechanism,
wherein the discharge cover and the cylindrical lateral wall are used to increase a passage resistance of a short circuit passage that communicates the outer space and the inner space to each other.
10: A vapor compression-type refrigeration cycle device, comprising:
the hermetic compressor of claim 1 ;
a radiator for transferring heat of refrigerant that is compressed by the hermetic compressor;
an expansion mechanism for expanding the refrigerant that flows out from the radiator; and
an evaporator for causing the refrigerant that flows out from the expansion mechanism to receive heat.
Applications Claiming Priority (1)
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PCT/JP2014/057464 WO2015140949A1 (en) | 2014-03-19 | 2014-03-19 | Hermetic compressor and vapor compression refrigeration cycle device with said hermetic compressor |
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US20170089624A1 true US20170089624A1 (en) | 2017-03-30 |
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US15/126,203 Abandoned US20170089624A1 (en) | 2014-03-19 | 2014-03-19 | Hermetic compressor and vapor compression-type refrigeration cycle device including the hermetic compressor |
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US (1) | US20170089624A1 (en) |
JP (1) | JPWO2015140949A1 (en) |
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US20170284706A1 (en) * | 2015-06-16 | 2017-10-05 | Guangdong Meizhi Compressor Co., Ltd. | Refrigeration cycle device |
EP3401543A1 (en) * | 2017-05-12 | 2018-11-14 | LG Electronics Inc. | Scroll compressor with oil separation |
EP3636926A1 (en) * | 2018-10-12 | 2020-04-15 | LG Electronics Inc. | Compressor |
CN111108333A (en) * | 2017-09-28 | 2020-05-05 | 三菱电机株式会社 | Oil separator and air conditioner provided with same |
US11193490B2 (en) * | 2018-03-30 | 2021-12-07 | Kabushiki Kaisha Toyota Jidoshokki | Scroll compressor including bushing mounted on eccentric shaft containing cylindrical and auxiliary weight portions and balancer disposed above annular rotor remote from back pressure chamber |
EP4053412A4 (en) * | 2019-12-17 | 2022-12-28 | Daikin Industries, Ltd. | Compressor |
US11668301B2 (en) | 2019-11-06 | 2023-06-06 | Danfoss Commercial Compressors | Scroll compressor having a press-fitted motor and a vertically central suction inlet |
US11686311B1 (en) * | 2022-06-07 | 2023-06-27 | Agilent Technologies, Inc | Drive shaft connector with counterweight and blades for cooling pump motor |
US20240200558A1 (en) * | 2022-12-15 | 2024-06-20 | Agilent Technologies, Inc. | Fluid pump and enclosure providing stator holder and cooling for motor and electronics |
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JP6696533B2 (en) * | 2018-06-22 | 2020-05-20 | ダイキン工業株式会社 | Refrigeration equipment |
JP7076583B2 (en) * | 2019-01-30 | 2022-05-27 | 三菱電機株式会社 | Compressor and refrigeration cycle equipment |
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US10605492B2 (en) * | 2015-06-16 | 2020-03-31 | Guangdong Meizhi Compressor Co., Ltd. | Refrigeration cycle device |
US20170284706A1 (en) * | 2015-06-16 | 2017-10-05 | Guangdong Meizhi Compressor Co., Ltd. | Refrigeration cycle device |
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US12000400B2 (en) | 2019-12-17 | 2024-06-04 | Daikin Industries, Ltd. | Compressor |
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US20240200558A1 (en) * | 2022-12-15 | 2024-06-20 | Agilent Technologies, Inc. | Fluid pump and enclosure providing stator holder and cooling for motor and electronics |
Also Published As
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JPWO2015140949A1 (en) | 2017-04-06 |
WO2015140949A1 (en) | 2015-09-24 |
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Owner name: MITSUBISHI ELECTRIC CORPORATION, JAPAN Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:YOKOYAMA, TETSUHIDE;NISHIKI, TERUHIKO;MOROE, SHOGO;AND OTHERS;SIGNING DATES FROM 20160722 TO 20160728;REEL/FRAME:039741/0713 |
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