WO2013118514A1 - 圧縮機 - Google Patents
圧縮機 Download PDFInfo
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- WO2013118514A1 WO2013118514A1 PCT/JP2013/000714 JP2013000714W WO2013118514A1 WO 2013118514 A1 WO2013118514 A1 WO 2013118514A1 JP 2013000714 W JP2013000714 W JP 2013000714W WO 2013118514 A1 WO2013118514 A1 WO 2013118514A1
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- WIPO (PCT)
- Prior art keywords
- oil
- pump
- shaft
- passage
- drive shaft
- Prior art date
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- 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
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- 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
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- 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
- F04B39/0261—Hermetic compressors with an auxiliary oil pump
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
- F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
- F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/02—Lubrication; Lubricant separation
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- 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
- F04C29/025—Lubrication; Lubricant separation using a lubricant pump
Definitions
- the present invention relates to a compressor that compresses a refrigerant, and particularly relates to a measure for avoiding a reduction in motor efficiency.
- Patent Document 1 discloses this type of scroll compressor.
- an electric motor is fixed to the inner surface of a casing, and a drive shaft is coupled to the electric motor.
- a scroll-type compression mechanism is connected to the upper portion of the drive shaft. In this compression mechanism, the refrigerant in the compression chamber is compressed by rotating the movable scroll eccentrically with respect to the fixed scroll.
- the oil in the oil reservoir in the bottom of the casing is supplied to the pin bearing and the upper main bearing above the motor via the oil supply passage in the drive shaft, and lubricates these sliding portions. .
- the oil return guide guides the oil to the gap between the core cut formed on the outer peripheral surface of the stator of the motor and the casing. It falls from the lower end and is discharged into the oil sump.
- This invention is made
- the first invention includes a casing (20), an electric motor (30) fixed to the casing (20), a drive shaft (40) connected to the electric motor (30) and extending in the vertical direction, and the drive shaft. (40) driven by the compression mechanism (50) for compressing the fluid, and formed in the drive shaft (40), the oil at the bottom of the casing (20) is above the electric motor (30).
- the compressor is provided with an in-shaft oil supply passage (45) supplied to the sliding portion of the drive shaft (40).
- the compressor is formed inside the drive shaft (40) and is connected to an in-shaft oil drain passage (46) extending from above to below the electric motor (30) and a lower end of the drive shaft (40).
- An oil discharge pump (81b) for discharging the oil after being supplied to the sliding portion of the drive shaft (40) to the bottom of the casing (20) via the in-shaft oil discharge passage (46); It is characterized by having.
- the oil supplied to the sliding portion above the electric motor (30) is sucked into the in-shaft oil drain passage (46) by the oil drain pump (81b), and the in-shaft oil drain passage. After being conveyed to the lower part of the electric motor (30) via (46), it is discharged to the bottom of the casing (20). For this reason, it is not necessary to return the oil to the bottom of the casing (20) through the gap between the core cut (34) of the electric motor (30) and the casing (20) as in the prior art.
- the oil at the bottom of the casing (20) is supplied to the in-shaft oil supply passage (45), and the oil supply constituting the drain oil pump (81b) and the dual pump is provided.
- a pump (81a) is provided.
- an oil supply pump (81a) is provided, and the oil supply pump (81a) constitutes an oil discharge pump (81b) and a dual pump. For this reason, the oil at the bottom of the casing (20) is reliably supplied to the sliding portion via the in-shaft oil supply passage (45), and the system for supplying and discharging oil is formed small.
- the third invention is characterized in that, in the second invention, the oil supply pump (81a) has a capacity larger than that of the oil discharge pump (81b).
- a lower bearing member (70) for rotatably supporting a lower portion of the drive shaft (40) than the electric motor (30);
- An off-shaft oil passage (72, 73) formed in the lower bearing member (70) and communicating with the outflow end of the in-shaft oil passage (46) and the suction port of the oil discharge pump (81b); It is characterized by having.
- oil supply is performed in the in-shaft oil supply passage (45) in the drive shaft (40) below the electric motor (30), while the oil is discharged from the shaft outside the drive shaft (40). It takes place on the road (72,73). Therefore, it becomes easy to route each flow path (45, 72, 73) around the oil discharge pump (81b).
- the oil that has been supplied to the sliding portion above the electric motor (30) is sucked into the in-shaft oil passage (46) by the oil discharge pump (81b), and then discharged into the shaft. It was conveyed to the lower part of the electric motor (30) through the oil passage (46) and discharged to the bottom of the casing (20). For this reason, it is not necessary to return the oil to the bottom of the casing (20) through the gap between the core cut (34) of the electric motor (30) and the casing (20) as in the prior art. Therefore, it is not necessary to increase the core cut (34) to reduce the cross-sectional area of the stator in order to secure the oil return passage, and it is possible to avoid a decrease in motor efficiency.
- the oil supply pump (81a) for supplying oil from the bottom portion of the casing (20) to the in-shaft oil supply passage (45) is provided, and the oil pump (81a) and the oil discharge pump (81b) are connected in series.
- the pump was configured. As a result, it is possible to reliably supply oil to the sliding portion and to reduce the size of the system that supplies and discharges oil.
- the capacity of the oil supply pump (81a) is made larger than the capacity of the oil discharge pump (81b).
- the amount of oil supply can be made larger than the amount of oil discharged, and the sliding parts of each bearing part (the pin bearing part (58), the main bearing part (37), and the lower bearing part (71)) can be normally operated. It is possible to prevent the refrigerant gas from entering without being refueled, and as a result, to reduce the lubricity of the sliding portion.
- the off-axis oil drain passage (72, 73) is formed in the lower bearing member (70).
- oil is supplied through the in-shaft oil passage (45) in the drive shaft (40), while oil is drained from the off-shaft oil passage (72, 73) outside the drive shaft (40). ), And it is possible to facilitate the handling of each flow path (45, 72, 73) around the oil discharge pump (81b).
- FIG. 1 is a longitudinal sectional view of the compressor according to the first embodiment, in which the flow of oil is represented by white arrows.
- FIG. 2 is an enlarged view around the oil pump of the compressor according to the first embodiment.
- FIG. 3 is an exploded perspective view of the oil pump according to the first embodiment.
- FIG. 4 is an enlarged view around the oil pump of the compressor according to the first modification of the first embodiment.
- FIG. 5 is an enlarged view around the oil pump of the compressor according to the third modification of the first embodiment.
- FIG. 6 is an enlarged view around the oil pump of the compressor according to the second embodiment.
- FIG. 7 is an enlarged view around the oil pump of the compressor according to the first modification of the second embodiment.
- FIG. 8 is a longitudinal sectional view of the compressor according to the third embodiment.
- FIG. 9 is an enlarged view around the oil pump of the compressor according to the third embodiment.
- the compressor (10) according to Embodiment 1 of the present invention is a scroll type compressor.
- the compressor (10) is connected to a refrigerant circuit of a refrigeration apparatus (not shown).
- the refrigerant compressed by the compressor (10) dissipates heat by the condenser (heat radiator) and is decompressed by the decompression mechanism.
- the decompressed refrigerant is evaporated by the evaporator and sucked into the compressor (10). That is, in the refrigerant circuit of the refrigeration apparatus, the refrigerant circulates to perform a vapor compression refrigeration cycle.
- the compressor (10) includes a casing (20), an electric motor (30), a drive shaft (40), and a compression mechanism (50).
- the casing (20) is composed of a vertically long cylindrical sealed container.
- the casing (20) includes a cylindrical body part (21) whose both ends in the axial direction are open, a first end plate part (22) that closes one end (upper end) of the body part (21) in the axial direction, A second end plate portion (23) that closes the other end (lower end) of the portion (21) in the axial direction.
- a leg portion (24) for supporting the casing (20) is formed below the second end plate portion (23).
- the electric motor (30) has a stator (31) fixed to the inner peripheral wall of the casing (20) and a rotor (33) inserted into the stator (31).
- the stator (31) has a substantially cylindrical stator core (32) and windings (not shown) wound around the stator core (32).
- the outer surface of the stator core (32) is fixed to the inner surface of the casing (20).
- a core cut (34) penetrating the stator core (32) in the axial direction is formed on the outer peripheral surface of the stator core (32).
- the rotor (33) is formed in a substantially cylindrical shape, and the drive shaft (40) is inserted into and connected to the rotor (33).
- the drive shaft (40) extends in the axial direction (vertical direction) of the casing (20) from the upper end of the body (21) of the casing (20) to the bottom of the casing (20).
- An oil pump (81) is fixed to the lower end of the drive shaft (40).
- An in-shaft oil supply passage (45) and an in-shaft oil discharge passage (46) are formed inside the drive shaft (40).
- the oil pump (81), the in-shaft oil supply passage (45), and the in-shaft oil discharge passage (46) will be described in detail later.
- the compression mechanism (50) is driven by the drive shaft (40) and compresses the refrigerant (low-pressure gas refrigerant) in the refrigerant circuit.
- the compression mechanism (50) includes a housing (35), a movable scroll (55), a fixed scroll (60), and a rotation prevention member (39).
- the housing (35) is a substantially cylindrical member extending vertically, and the outer peripheral surface thereof is joined to the inner peripheral surface of the body (21) of the casing (20).
- a drive shaft (40) is inserted into the housing (35), and a main bearing portion (37) is formed in a lower portion thereof.
- the main bearing portion (37) is fitted with a sliding bearing (37a), and the main shaft portion (41) of the drive shaft (40) is rotatably supported by the sliding bearing (37a).
- a substantially circular recess (36) in the axial direction formed by recessing the upper end surface of the housing (35) is formed in the upper portion of the housing (35).
- the pin shaft portion (42) of the drive shaft (40) is accommodated so as to protrude upward from the upper end surface of the main shaft portion (41).
- the pin shaft portion (42) has a smaller diameter than the main shaft portion (41) of the drive shaft (40).
- the shaft center of the pin shaft portion (42) is eccentric with respect to the shaft center of the main shaft portion (41) of the drive shaft (40).
- a rotation preventing member (39) of the movable scroll (55) is provided on the upper surface of the housing (35).
- the rotation prevention member (39) is made of, for example, an Oldham joint.
- the rotation prevention member (39) is slidably fitted into the movable side end plate portion (56) and the housing (35) of the movable scroll (55).
- the movable scroll (55) has a movable side end plate portion (56), a movable side wrap (57), and a pin bearing portion (58).
- the movable side end plate portion (56) is formed in a disc shape.
- a movable side wrap (57) is erected on one end side (upper end side) in the thickness direction of the movable side end plate portion (56).
- the movable wrap (57) is formed in a spiral shape.
- a sliding bearing (58a) is fitted into the pin bearing portion (58), and the pin shaft portion (42) is rotatably supported.
- the fixed scroll (60) has a fixed side end plate part (61), an outer edge part (62), and a fixed side wrap (63).
- the fixed side end plate portion (61) is formed in a disc shape.
- an outer edge portion (62) and a fixed side wrap (63) are erected on the surface of the movable scroll (55).
- the outer edge portion (62) is formed at the outer peripheral end portion of the fixed scroll (60) and is formed in a cylindrical shape.
- the axial end surface (upper end surface in FIG. 1) of the movable side end plate portion (56) of the movable scroll (55) is in sliding contact with the axial end surface (lower end surface in FIG. 1) of the outer edge portion (62).
- a surface is formed.
- the stationary side wrap (63) is disposed inside the outer edge (62) and is formed in a spiral shape.
- the fixed wrap (63) meshes with the movable wrap (57).
- a compression chamber (C) for compressing the refrigerant is defined between the movable scroll (55) and the fixed scroll (60).
- a discharge port (64) and a discharge chamber (65) are formed in the fixed side end plate portion (61) of the fixed scroll (60).
- the discharge port (64) is formed at the central portion in the radial direction of the fixed side end plate portion (61) and communicates with the compression chamber (C).
- the discharge chamber (65) is connected to the outflow end of the discharge port (64).
- the discharge chamber (65) communicates with a space below the housing (35) in the casing (20) through a discharge channel (not shown). That is, the space below the housing (35) constitutes a high-pressure space (25) that is filled with high-pressure discharged refrigerant.
- the suction pipe (27) and the discharge pipe (28) are connected to the casing (20) of the compressor (10).
- the suction pipe (27) is connected to a low-pressure gas line of the refrigerant circuit, and communicates with the compression chamber (C) through an auxiliary suction hole (not shown).
- the discharge pipe (28) penetrates the trunk part (21) of the casing (20) in the radial direction.
- the outflow end of the discharge pipe (28) is connected to the high-pressure gas line of the refrigerant circuit.
- the inflow end of the discharge pipe (28) opens between the housing (35) and the electric motor (30) in the high-pressure space (25). In the high-pressure space (25), the oil contained in the high-pressure refrigerant is collected at the bottom of the casing (20). That is, an oil sump (26) in which oil for lubricating each sliding part inside the compressor (10) is formed at the bottom of the casing (20).
- a lower bearing member (70) is provided in the vicinity of the oil sump (26) at the bottom of the casing (20).
- the lower bearing member (70) is a substantially cylindrical member extending up and down, and its outer peripheral surface protrudes outward and is fixed to the inner peripheral surface of the casing (20).
- the drive shaft (40) is inserted into the lower bearing member (70), and the lower bearing portion (71) is formed in the upper portion.
- a sliding bearing (71a) is fitted into the lower bearing portion (71), and the drive shaft (40) is rotatably supported by the sliding bearing (71a).
- the lower bearing member (70) has a substantially circular recess (72) as viewed in the axial direction formed by recessing the lower end surface of the lower bearing member (70).
- An oil pump (81) is attached to the lower end surface of the lower bearing member (70) so as to close the recess (72).
- the compressor (10) of this embodiment supplies the oil in the oil reservoir (26) to each sliding portion of the drive shaft (40), and the oil after being supplied to each sliding portion is stored in the oil reservoir (26).
- An oil supply / discharge mechanism (80) is provided.
- the oil supply / discharge mechanism (80) includes an oil pump (81), an in-shaft oil supply passage (45), and an oil discharge passage (90).
- the oil pump (81) is a so-called double trochoidal volumetric pump. As shown in FIGS. 2 and 3, the oil pump (81) is fixed to the lower end surface of the lower bearing member (70) with a bolt (84), and includes a thrust plate (75), a pump case (82), A pump cover (83), a pump shaft (85), a lower outer rotor (86), a lower inner rotor (87), an upper outer rotor (88) and an upper inner rotor (89) are provided.
- the thrust plate (75) is formed in a substantially disc shape and is in sliding contact with the drive shaft (40) to receive the thrust force of the drive shaft (40).
- An insertion hole (76) for inserting the pump shaft (85) is formed at the radial center of the thrust plate (75).
- a discharge port (77) for discharging oil is formed in the outer peripheral portion of the thrust plate (75).
- the pump case (82) is a substantially cylindrical member extending in the vertical direction, and an outer peripheral edge (82a) protruding upward is formed on the upper surface.
- the pump case (82) is fixed to the lower surface of the thrust plate (75) with the thrust plate (75) fitted inside the outer peripheral edge (82a).
- the pump case (82) has an upper case flow passage (82b) that is recessed in a substantially circular shape at a substantially central portion of the upper surface, and a lower side that is recessed in a substantially circular shape at a substantially central portion of the lower surface.
- An in-case flow path (82c) is formed.
- the pump cover (83) is formed in a substantially disc shape.
- a pump shaft (85) extending upward is rotatably supported at the center of the pump cover (83).
- the pump shaft (85) is inserted from below into the inner peripheral hole (82d) of the pump case (82) and the insertion hole (76) of the thrust plate (75), and the pump cover (83) is inserted in the inserted state. It is fixed to the lower surface of the pump case (82).
- the pump shaft (85) is connected to an inlet (45a) formed at the lower end of the drive shaft (40) via a cylindrical holding member (49). As a result, the pump shaft (85) rotates integrally with the drive shaft (40).
- the lower outer rotor (86) is fitted in the flow path (82c) in the lower case.
- the lower outer rotor (86) is formed in a substantially annular shape, and a plurality of substantially arcuate (more precisely, trochoidal curve) outer teeth (86a) are formed on the inner peripheral surface thereof.
- the plurality of outer teeth (86a) are arranged at equal intervals in the circumferential direction and bulge toward the lower inner rotor (87).
- the lower inner rotor (87) is formed in a substantially annular shape and is fitted to the outside of the pump shaft (85). Specifically, a holding hole (87a) having a substantially D-shaped cross section perpendicular to the axis is formed inside the lower inner rotor (87). When the flat wall (85a) of the pump shaft (85) is engaged with the flat surface (87b) of the holding hole (87a), the lower inner rotor (87) rotates integrally with the pump shaft (85). .
- a plurality of inner teeth (87c) are formed on the outer peripheral surface of the lower inner rotor (87) so as to correspond to the outer teeth (86a) of the lower outer rotor (86).
- the pump cover (83) has a substantially crescent shaped inlet (83a) formed on the outer peripheral side of the pump shaft (85).
- the inflow end of the suction port (83a) opens to the oil sump (26), and the outflow end of the suction port (83a) opens to the lower case internal channel (82c) of the pump case (82). .
- a radial relay path (85b) and an axial relay path (85c) are formed inside the pump shaft (85).
- the radial relay path (85b) penetrates the pump shaft (85) in the radial direction, and the inflow end opens into the lower case flow path (82c) of the pump case (82).
- the axial relay path (85c) penetrates the upper part of the pump shaft (85) in the axial direction.
- the inflow end of the axial relay path (85c) communicates with the radial relay path (85b), and the outflow end of the axial relay path (85c) opens to the upper end surface of the pump shaft (85) for driving. It communicates with the oil supply passage (45) in the shaft (40).
- the lower part of the oil pump (81) constitutes the oil supply pump part (81a).
- the oil in the oil reservoir (26) flows in from the suction port (83a) of the pump cover (83), and both rotors (86, 87) in the lower case flow path (82c) After passing through the volume chamber (V1) therebetween, it passes through the radial relay path (85b) and the axial relay path (85c) and is supplied to the in-shaft oil supply path (45).
- This oil pump part (81a) constitutes the oil pump of the present invention.
- the upper outer rotor (88) is fitted in the upper case flow path (82b).
- the upper outer rotor (88) has substantially the same shape as the lower outer rotor (86).
- the upper inner rotor (89) is fitted to the outside of the pump shaft (85).
- the upper inner rotor (89) has substantially the same shape as the lower inner rotor (87).
- the inner teeth (89a) of the upper inner rotor (89) and the outer teeth (88a) of the upper outer rotor (88) mesh with each other, whereby the inner teeth (89a) and the outer teeth
- a volume chamber (V2) for conveying oil is formed between the portion (88a).
- the volume chamber (V1) between the lower two rotors (86, 87) is larger than the volume chamber (V2) between the upper two rotors (88, 89).
- the discharge port (77) of the thrust plate (75) has an upper end (inflow end) that opens into the recess (72) of the lower bearing member (70), and a lower end (outflow end) that flows in the upper case of the pump case (82). Open to the road (82b).
- the pump case (82) has a discharge passage (82e) extending in the lateral direction and penetrating the inside and the outside.
- the inner end (inflow end) of the discharge passage (82e) is an upper case inner passage. (82b) and the outer end (outflow end) of the discharge passage (82e) is open to the outer peripheral surface of the pump case (82).
- the upper part of the oil pump (81) constitutes the oil discharge pump part (81b).
- the oil flows upward from the recess (72) of the lower bearing member (70) that constitutes a part of the oil discharge path (90) through the discharge port (77) of the thrust plate (75).
- the case internal flow path (82b) After flowing into the case internal flow path (82b), passing through the volume chamber (V2) between both rotors (88, 89) in the upper case internal flow path (82b), passing through the discharge passage (82e), Drained into the oil sump (26) at the bottom of the casing (20).
- This oil discharge pump part (81b) constitutes the oil discharge pump of the present invention.
- the in-shaft oil supply passage (45) guides the oil in the oil reservoir (26) to each sliding portion of the drive shaft (40) through the oil pump portion (81a) of the oil pump (81). As shown in FIG. 1, the in-shaft oil supply passage (45) has an inlet (45a), a main oil supply passage (45b), an upper outlet (45c), and a lower outlet (45d).
- the inlet (45a) communicates with the axial relay passage (85c) of the oil pump (81).
- the main oil supply passage (45b) communicates with the inlet (45a), extends in the axial direction of the drive shaft (40), and opens to the upper end surface of the drive shaft (40) (the upper end surface of the pin shaft portion (42)). ing.
- the upper outlet (45c) extends radially outward from the main oil supply passage (45b) and opens to the main bearing portion (37) of the housing (35).
- the oil flowing out from the upper outlet (45c) to the main bearing portion (37) is supplied to the sliding portion between the sliding bearing (37a) of the main bearing portion (37) and the drive shaft (40).
- the lower outlet (45d) extends radially outward from the main oil supply passage (45b) and opens to the lower bearing portion (71) of the lower bearing member (70).
- the oil flowing out from the lower outlet (45d) to the lower bearing portion (71) is supplied to the sliding portion between the sliding bearing (71a) of the lower bearing portion (71) and the drive shaft (40).
- an oil communication chamber (48) is formed between the upper end surface of the drive shaft (40) and the lower surface of the movable side end plate portion (56).
- the oil communication chamber (48) communicates with the main oil supply passage (45b) and the pin shaft passage (not shown) on the drive shaft (40) side, and communicates with the oil passage (56a) on the movable end plate portion (56) side.
- the pin shaft channel is formed in the vertical direction between the pin shaft portion (42) and the sliding bearing (58a) of the pin bearing portion (58), the upper end opens to the oil communication chamber (48), and the lower end is the housing. Opened in the recess (36) of (35).
- the oil flowing into the pin shaft channel is supplied to the sliding portion between the sliding bearing (58a) of the pin bearing portion (58) and the drive shaft (40).
- the oil passage (56a) is formed in the movable side end plate part (56), and the upper end opens to the upper surface of the movable side end plate part (56) and the lower end opens to the lower surface of the movable side end plate part (56). It communicates with the communication room (48).
- the oil drain passage (90) guides the oil after being supplied to the sliding portions of the drive shaft (40) to the oil drain pump portion (81b) of the oil pump (81).
- the oil drain passage (90) includes a main bearing oil drain passage (35a), an in-shaft oil drain passage (46), and a recess (72) of the lower bearing member (70).
- the main bearing oil drain passage (35a) guides the oil after being supplied to the sliding portion of the sliding bearing (37a) of the main bearing portion (37) to the concave portion (36) of the housing (35). (35) is formed in the vertical direction along the sliding bearing (37a).
- the inflow end (lower end) of the main bearing oil drain passage (35a) communicates with the outer peripheral groove (47) of the drive shaft (40) located at the lower end of the sliding bearing (37a).
- the outflow end (upper end) of the main bearing oil drain passage (35a) opens into the recess (36).
- the in-shaft oil drain passage (46) guides oil in the recess (36) of the housing (35) to the recess (72) of the lower bearing member (70) below the electric motor (30). Specifically, the oil in the recess (36) of the housing (35) is oil that has flowed out of the main bearing drain oil passage (35a) and oil that has flowed out of the pin shaft flow path.
- the in-shaft oil drain passage (46) has an inflow port (46a), a main oil drain passage (46b), and a discharge port (46c).
- the inlet (46a) has an inflow end that opens into the recess (36) of the housing (35), and an outflow end that communicates with the main oil drain passage (46b).
- the main oil drainage passage (46b) extends in the axial direction from the upper end surface of the drive shaft (40) (the upper end surface of the pin shaft portion (42)), and communicates with the inflow port (46a) on the way.
- the upper end of the main oil drain passage (46b) is plugged.
- the discharge port (46c) extends in the lateral direction from the lower end of the main oil discharge passage (46b) and opens into the recess (72) of the lower bearing member (70).
- the concave portion (72) of the lower bearing member (70) guides the oil flowing in from the in-shaft oil passage (46) to the discharge port (77) of the thrust plate (75).
- This recessed part (72) comprises the off-axis oil drainage path of this invention.
- the movable scroll (55) revolves without rotating. Then, the refrigerant (low pressure gas refrigerant) in the refrigerant circuit is sucked into the compression mechanism (50) from the suction pipe (27) via the low pressure space and the auxiliary suction hole. In the compression mechanism (50), the refrigerant is sucked from the outer peripheral side of the fixed side wrap (63).
- a compression chamber (C) that is a closed space is defined between the fixed wrap (63) and the movable wrap (57).
- the compression chamber (C) approaches the center of the fixed scroll (60) while gradually reducing its volume. As a result, the refrigerant is compressed in the compression chamber (C).
- the compression chamber (C) communicates with the discharge port (64), the refrigerant in the compression chamber (C) is discharged to the discharge chamber (65) through the discharge port (64).
- the refrigerant (high-pressure gas refrigerant) discharged to the discharge chamber (65) is sent to the high-pressure space (25) through a discharge channel (not shown).
- the refrigerant in the high-pressure space (25) is sent to the refrigerant circuit outside the casing (20) through the discharge pipe (28).
- the oil in the oil reservoir (26) is sucked into the volume chamber (V1) in the lower case flow path (82c) through the suction port (83a) of the pump cover (83).
- the oil in the volume chamber (V1) flows in the order from the lower case flow path (82c) to the radial relay path (85b) and the axial relay path (85c), and the inlet (45a ).
- a part of the oil is supplied to the lower bearing portion (71) through the lower outlet (45d), and the sliding portion between the sliding bearing (71a) and the drive shaft (40) is lubricated.
- the remaining oil further rises in the main oil supply passage (45b)
- a part of the oil is supplied to the main bearing portion (37) through the upper outlet (45c), and the sliding bearing (37a) and the drive shaft (40 )
- the oil flows out through the main bearing oil drainage passage (35a) into the recess (36) of the housing (35).
- the remaining oil further rises in the main oil supply passage (45b), it flows out to the oil communication chamber (48).
- the upper inner rotor (89) shown in FIG. 2 rotates inside the upper outer rotor (88).
- the volume of the volume chamber (V2) expands and contracts, so that the oil that has flowed into the recess (36) is sucked into the in-shaft oil passage (46) from the inlet (46a).
- the oil flowing into the in-shaft oil discharge passage (46) flows out into the recess (72) of the lower bearing member (70) below the electric motor (30), and the oil discharge pump section (81b) of the oil pump (81) Flow into.
- the oil that has flowed into the oil discharge pump part (81b) is sucked into the volume chamber (V2) in the upper case flow path (82b) and then passes through the discharge passage (82e) of the pump case (82). Drained into the oil sump (26) at the bottom of the casing (20).
- the oil after being supplied to the sliding part of the pin bearing part (58) and the main bearing part (37) above the electric motor (30) is supplied to the oil pump part ( 81a), the oil was sucked into the in-shaft oil drain passage (46), then conveyed to the lower part of the electric motor (30) through the in-shaft oil drain passage (46), and discharged to the oil sump (26). Therefore, it is necessary to convey oil to the lower part of the electric motor (30) through the gap between the core cut of the electric motor (30) and the casing (20) and return it to the bottom of the casing (20) as in the past. Disappear. Therefore, it is not necessary to increase the core cut to secure the oil return passage and to reduce the cross-sectional area of the stator (31), thereby avoiding a reduction in motor efficiency.
- oil is supplied from the oil reservoir (26) to the in-shaft oil supply passage (45) by the two oil pumps (81), and from the oil discharge passage (90) to the oil reservoir (26). I tried to drain the oil. As a result, the oil can be reliably supplied and discharged, and the system for supplying and discharging the oil can be downsized.
- the pump capacity (volume of the volume chamber (V1)) of the oil supply pump section (81a) is changed to the pump capacity (volume chamber (V2) of the oil discharge pump section (81b). ) Volume)).
- the amount of oil supply can be made larger than the amount of oil discharged, and the sliding parts of each bearing part (the pin bearing part (58), the main bearing part (37), and the lower bearing part (71)) can be normally operated. It is possible to prevent the refrigerant gas from entering without being refueled, and as a result, to reduce the lubricity of the sliding portion.
- the recess (72) of the lower bearing member (70) is used as an off-axis oil drain passage communicating with the in-shaft oil drain passage (46).
- the compressor (10) according to Modification 1 is obtained by changing the configuration of the oil supply pump part (81a) of the oil pump (81) in the first embodiment. That is, although the oil pump part (81a) of the said Embodiment 1 was comprised with the volumetric pump, the oil pump part (81a) of the modification 1 is comprised with a differential pressure pump, as shown in FIG. I made it.
- the lower case internal flow path (82c) is not formed in the pump case (82), and only the upper case internal flow path (82b) is formed. Yes.
- the pump shaft (85) is formed with a suction passage (85d) penetrating in the vertical direction.
- the oil in the oil reservoir (26) flows directly into the suction passage (85d) of the pump shaft (85).
- the oil in the oil sump (26) is caused by the pressure acting on the oil sump (26), that is, the difference between the pressure in the high pressure space (25) and the pressure in the oil supply passage (45) in the pump shaft ( 85) is sucked into the shaft and supplied to the in-shaft oil supply passage (45).
- the oil in the oil drainage passage (90) is passed through the discharge port (77) of the thrust plate (75) in the upper case flow path (82b) of the oil discharge pump part (81b) as in the first embodiment. And then sucked into the volume chamber (V2) in the upper case flow path (82b), then passes through the discharge passage (82e) of the pump case (82) and flows out to the oil reservoir (26).
- the oil pump (81) of the first embodiment may be configured such that the oil supply pump part (81a) is a centrifugal pump.
- the in-shaft oil drain passage (46) is opened in the recess (72) of the lower bearing member (70), and the oil in the in-shaft oil passage (46) is thrust through the recess (72). It flows into the discharge port (77) of (75). That is, the off-axis oil drainage path is constituted by the recess (72) of the lower bearing member (70). However, the off-axis oil drainage path only needs to be formed in the lower bearing member (70). For example, as shown in FIG. A discharge passage (73) that opens to the lower surface of the lower bearing member (70) and communicates with the discharge port (77) of the thrust plate (75) while communicating with the oil passage (46) may be used as an off-axis oil discharge passage. Absent.
- Embodiment 2 of the Invention The compressor (10) according to Embodiment 2 is obtained by changing the method of introducing oil from the oil discharge passage (90) to the oil discharge pump portion (81b) of the oil pump (81) in Embodiment 1 described above. . That is, in the first embodiment, oil is introduced through the discharge port (77) on the outer peripheral portion of the thrust plate (75). However, in the second embodiment, as shown in FIG. 6, the thrust plate (75) The oil was introduced through the insertion hole (76) in the center of each.
- the thrust plate (75) of the second embodiment has a slit groove (75a) formed on the upper surface, extending in the radial direction and communicating with the insertion hole (76) at the inner end, and the insertion hole (76).
- a lateral path (75b) extending radially outward from the middle, and a discharge port (75c) extending downward from the middle of the lateral path (75b) and opening in the lower surface of the thrust plate (75) are formed.
- Other configurations, operations, and effects are the same as those in the first embodiment.
- the compressor (10) according to Modification 1 is obtained by changing the configuration of the oil supply pump part (81a) of the oil pump (81) in the second embodiment. That is, although the oil pump part (81a) of the said Embodiment 2 was comprised with the positive displacement pump, the oil pump part (81a) of the modification 1 is comprised with a differential pressure pump, as shown in FIG. I made it.
- the lower case internal flow path (82c) is not formed in the pump case (82), and only the upper case internal flow path (82b) is formed. Yes.
- the pump shaft (85) is formed with a suction passage (85d) penetrating in the vertical direction.
- the oil in the oil reservoir (26) flows directly into the suction passage (85d) of the pump shaft (85).
- the oil in the oil sump (26) is caused by the pressure acting on the oil sump (26), that is, the difference between the pressure in the high pressure space (25) and the pressure in the oil supply passage (45) in the pump shaft ( 85) is sucked into the shaft and supplied to the in-shaft oil supply passage (45).
- the oil in the oil discharge passage (90) flows in the order of the insertion hole (76), the side passage (75b), and the discharge port (75c) of the thrust plate (75) in the same manner as in the second embodiment. After being sucked into the volume chamber (V2) in the upper case flow path (82b) of the section (81b), it passes through the discharge passage (82e) of the pump case (82) and flows out to the oil sump (26) .
- the oil supply pump part (81a) may be constituted by a centrifugal pump.
- Embodiment 3 of the Invention In the compressor (10) according to the third embodiment, the type of bearing of the lower bearing portion (71) and the three bearing portions (pin bearing portion (58), main bearing portion (37), and The oil supply sequence for the lower bearing portion (71) is changed. That is, in the first embodiment, the sliding bearing (71a) is fitted into the lower bearing portion (71), and the lower bearing portion (71), the main bearing portion (37), and the pin bearing portion (58) are lubricated in this order. In Embodiment 3, as shown in FIGS. 8 and 9, the rolling bearing (71b) is fitted into the lower bearing portion (71), and the main bearing portion (37), the pin bearing portion (58), the lower bearing portion (71 ) In order of refueling.
- the rolling bearing (71b) of Embodiment 3 is a single-seal ball bearing, and includes an inner ring part (71c), an outer ring part (71d), a plurality of balls (71e), and a seal part (71f). have.
- the inner ring portion (71c) is fixed to the outer peripheral surface of the drive shaft (40).
- the outer ring portion (71d) is disposed to face the radially outer side of the inner ring portion (71c).
- the ball (71e) is rotatably held between the inner ring portion (71c) and the outer ring portion (71d).
- a sliding portion is formed between the inner ring portion (71c) and the ball (71e) or between the ball (71e) and the outer ring portion (71d).
- the seal portion (71f) is a plate material extending from the outer ring portion (71d) to the inner ring portion (71c) below the ball (71e), and blocks the gap between the outer ring portion (71d) and the inner ring portion (71c). Yes.
- the lower outlet (45d) is not formed. Therefore, the oil flowing from the oil pump part (81a) of the oil pump (81) into the inlet (45a) of the in-shaft oil supply path (45) is supplied to the rolling bearing (71b) of the lower bearing part (71). Without going up the main oilway (45b).
- the oil discharge passage (90) of Embodiment 3 includes a discharge passage (73) as an off-axis oil discharge passage.
- the discharge passage (73) is formed inside the lower bearing member (70), and has an upper flow path (73a) and a lower flow path (73b).
- the upper flow path (73a) is formed in the radial direction above the rolling bearing (71b) inside the lower bearing member (70).
- the upper flow path (73a) has an inner peripheral end that opens to the inner peripheral surface of the lower bearing portion (71) and communicates with the in-shaft oil discharge path (46). Further, the upper flow path (73a) communicates with the gap between the inner ring portion (71c) and the outer ring portion (71d) of the rolling bearing (71b) located on the lower side.
- the lower flow path (73b) is formed in the vertical direction on the outer peripheral portion of the lower bearing member (70).
- the lower flow path (73b) has an upper end communicating with an outer peripheral end of the upper flow path (73a), and a lower end opened on the lower surface of the lower bearing member (70), thereby discharging the thrust plate (75). Communicate with (77).
- the oil that has flowed from the oil pump part (81a) of the oil pump (81) into the in-shaft oil path (45) is not supplied to the lower bearing part (71), but rises in the main oil path (45b). And supplied to the main bearing portion (37) and the pin bearing portion (58). In the main bearing portion (37) and the pin bearing portion (58), the sliding portion is lubricated by the supplied oil.
- the oil supplied to the main bearing portion (37) and the pin bearing portion (58) flows into the in-shaft oil passage (46) and descends in the in-shaft oil passage (46).
- the discharge passage (73) a part of the oil is supplied to the rolling bearing (71b) of the lower bearing portion (71).
- the rolling bearing (71b) oil enters the gap between the inner ring portion (71c) and the outer ring portion (71d), and the sliding portion is lubricated.
- the remaining oil flows into the oil discharge pump part (81b) of the oil pump (81) and is discharged to the oil reservoir (26) at the bottom of the casing (20).
- the main bearing portion (37), the pin bearing portion (58), and the lower bearing portion (71) are refueled in this order. That is, oil supply to the main bearing portion (37) and the pin bearing portion (58) is performed on the upstream side of the lower bearing portion (71). Therefore, the upstream main bearing portion (37) and the pin bearing portion (58) can make it easy to ensure a sufficient amount of oil supply. As a result, the amount of oil supply is insufficient and wear and seizure occur. Can be prevented.
- the lower bearing portion (71) on the downstream side the amount of oil can be easily reduced, and the amount of oil supplied to the rolling bearing (71b), which requires less oil than the sliding bearing, is prevented from becoming excessive. be able to. That is, it is possible to increase the reliability of the compressor (10) by supplying an appropriate amount of oil to the three bearing portions (37, 58, 71).
- Other configurations, operations, and effects are the same as those in the first embodiment.
- the present invention relates to a compressor that compresses a refrigerant, and is particularly useful for a compressor in which an oil supply passage for supplying oil in an oil reservoir to a sliding portion above an electric motor is formed in a drive shaft. It is.
Abstract
Description
以下、本発明の実施形態1について図1~図3を参照しながら詳細に説明する。本発明の実施形態1に係る圧縮機(10)は、スクロール式の圧縮機である。圧縮機(10)は、図示しない冷凍装置の冷媒回路に接続されている。この冷凍装置では、圧縮機(10)で圧縮された冷媒が、凝縮器(放熱器)で放熱し、減圧機構で減圧される。減圧された冷媒は、蒸発器で蒸発して圧縮機(10)に吸入される。即ち、冷凍装置の冷媒回路では、冷媒が循環して蒸気圧縮式の冷凍サイクルが行われる。
本実施形態の圧縮機(10)は、油溜まり(26)の油を駆動軸(40)の各摺動部へ供給し、各摺動部へ供給された後の油を油溜まり(26)へ排出する油給排機構(80)を備えている。この油給排機構(80)は、油ポンプ(81)、軸内給油路(45)及び排油路(90)を備えている。
油ポンプ(81)は、いわゆる2連のトロコイド式の容積ポンプで構成されている。図2及び図3に示すように、この油ポンプ(81)は、下部軸受け部材(70)の下端面にボルト(84)で固定されており、スラストプレート(75)、ポンプケース(82)、ポンプカバー(83)、ポンプシャフト(85)、下側アウターロータ(86)、下側インナーロータ(87)、上側アウターロータ(88)及び上側インナーロータ(89)を備えている。
軸内給油路(45)は、油溜まり(26)の油を、油ポンプ(81)の給油ポンプ部(81a)を介して、駆動軸(40)の各摺動部へ導くものである。この軸内給油路(45)は、図1に示すように、流入口(45a)、主給油路(45b)、上側流出口(45c)及び下側流出口(45d)を有している。
排油路(90)は、駆動軸(40)の各摺動部へ供給された後の油を、油ポンプ(81)の排油ポンプ部(81b)へ導くものである。この排油路(90)は、主軸受け排油路(35a)と、軸内排油路(46)と、下部軸受け部材(70)の凹部(72)とを有している。
圧縮機(10)の基本的な運転動作について、図1を参照しながら説明する。圧縮機(10)の運転時には、電動機(30)が通電されて回転子(33)が回転する。これに伴い駆動軸(40)が回転し、ピン軸部(42)が主軸部(41)に対して偏心回転する。その結果、圧縮機構(50)で圧縮動作が行われる。
次いで、圧縮機(10)における油の給排動作について、図1及び図2を参照しながら説明する。上記のように圧縮機(10)が運転されると、駆動軸(40)の回転に伴い油ポンプ(81)も駆動される。油ポンプ(81)では、図2に示す下側インナーロータ(87)が、下側アウターロータ(86)の内部を回転する。これにより、容積室(V1)の容積が拡縮し、油溜まり(26)の油が油ポンプ(81)の給油ポンプ部(81a)内に吸い込まれる。
本実施形態によれば、電動機(30)より上方のピン軸受部(58)や主軸受部(37)の摺動部に供給された後の油を、油ポンプ(81)の給油ポンプ部(81a)によって軸内排油路(46)内に吸い込んだ後、この軸内排油路(46)を通して電動機(30)の下方まで搬送し、油溜まり(26)へ排出するようにした。そのため、従来のように、油を電動機(30)のコアカットとケーシング(20)との間の隙間を介して電動機(30)の下方まで搬送して、ケーシング(20)の底部に戻す必要がなくなる。よって、油戻し通路の確保のためにコアカットを大きくして、固定子(31)の断面積を小さくする必要がなくなり、モータ効率の低下を回避することができる。
上記実施形態に係る油給排機構(80)を以下のような各変形例の構成としてもよい。
変形例1に係る圧縮機(10)は、上記実施形態1において、油ポンプ(81)の給油ポンプ部(81a)の構成を変更したものである。つまり、上記実施形態1の給油ポンプ部(81a)は、容積ポンプで構成されていたが、変形例1の給油ポンプ部(81a)は、図4に示すように、差圧ポンプで構成するようにした。
上記実施形態1の油ポンプ(81)は、給油ポンプ部(81a)を遠心ポンプで構成するようにしても構わない。
上記実施形態1では、軸内排油路(46)を下部軸受け部材(70)の凹部(72)に開口し、軸内排油路(46)の油を凹部(72)を介してスラストプレート(75)の排出口(77)へ流入するようにしている。つまり、軸外排油路を下部軸受け部材(70)の凹部(72)によって構成している。しかし、軸外排油路は、下部軸受け部材(70)に形成されていれば良く、例えば、図5に示すように、下部軸受部(71)の内周面に開口して、軸内排油路(46)に連通する一方、下部軸受け部材(70)の下面に開口してスラストプレート(75)の排出口(77)に連通する排出通路(73)を軸外排油路としても構わない。
実施形態2に係る圧縮機(10)は、上記実施形態1において、排油路(90)から油ポンプ(81)の排油ポンプ部(81b)への油の導入方法を変更したものである。つまり、上記実施形態1では、スラストプレート(75)の外周部の排出口(77)を介して油を導入していたが、実施形態2では、図6に示すように、スラストプレート(75)の中央部の挿入孔(76)を介して油を導入するようにした。
上記実施形態に係る油給排機構(80)を以下のような各変形例の構成としてもよい。
変形例1に係る圧縮機(10)は、上記実施形態2において、油ポンプ(81)の給油ポンプ部(81a)の構成を変更したものである。つまり、上記実施形態2の給油ポンプ部(81a)は、容積ポンプで構成されていたが、変形例1の給油ポンプ部(81a)は、図7に示すように、差圧ポンプで構成するようにした。
上記実施形態2の油ポンプ(81)は、給油ポンプ部(81a)を遠心ポンプで構成するようにしても構わない。
実施形態3に係る圧縮機(10)は、上記実施形態1において、下部軸受部(71)の軸受けの種類と、3つの軸受部(ピン軸受部(58)、主軸受部(37)、及び下部軸受部(71))に対する給油順序を変更したものである。つまり、上記実施形態1では、下部軸受部(71)に滑り軸受け(71a)を嵌め込み、下部軸受部(71)、主軸受部(37)、ピン軸受部(58)の順に給油していたが、実施形態3では、図8及び図9に示すように、下部軸受部(71)に転がり軸受け(71b)を嵌め込み、主軸受部(37)、ピン軸受部(58)、下部軸受部(71)の順に給油するようにした。
30 電動機
40 駆動軸
45 軸内給油路
46 軸内排油路
50 圧縮機構
70 下部軸受け部材
72 凹部(軸外排油路)
73 排出通路(軸外排油路)
81a 給油ポンプ部(給油ポンプ)
81b 排油ポンプ部(排油ポンプ)
Claims (4)
- ケーシング(20)と、
上記ケーシング(20)に固定された電動機(30)と、
上記電動機(30)に連結され、上下方向に延びる駆動軸(40)と、
上記駆動軸(40)によって駆動され、流体を圧縮する圧縮機構(50)と、
上記駆動軸(40)の内部に形成され、上記ケーシング(20)の底部の油が上記電動機(30)よりも上方の上記駆動軸(40)の摺動部へ供給される軸内給油路(45)とを備えた圧縮機であって、
上記駆動軸(40)の内部に形成され、上記電動機(30)の上方から下方まで延びる軸内排油路(46)と、
上記駆動軸(40)の下端に連結され、上記駆動軸(40)の摺動部へ供給された後の油を、上記軸内排油路(46)を介して上記ケーシング(20)の底部へ排出する排油ポンプ(81b)とを備えている
ことを特徴とする圧縮機。 - 請求項1において、
上記ケーシング(20)の底部の油を上記軸内給油路(45)へ供給すると共に、上記排油ポンプ(81b)と2連ポンプを構成する給油ポンプ(81a)を備えている
ことを特徴とする圧縮機。 - 請求項2において、
上記給油ポンプ(81a)は、容量が上記排油ポンプ(81b)の容量よりも大きい
ことを特徴とする圧縮機。 - 請求項1乃至3の何れか一項において、
上記駆動軸(40)の上記電動機(30)よりも下側部分を回転可能に支持する下部軸受け部材(70)と、
上記下部軸受け部材(70)に形成され、上記軸内排油路(46)の流出端と上記排油ポンプ(81b)の吸入口とに連通する軸外排油路(72,73)とを備えている
ことを特徴とする圧縮機。
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CN201380008492.2A CN104105878B (zh) | 2012-02-09 | 2013-02-08 | 压缩机 |
US14/377,124 US9617996B2 (en) | 2012-02-09 | 2013-02-08 | Compressor |
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2012026179 | 2012-02-09 | ||
JP2012-026179 | 2012-02-09 | ||
JP2012-130671 | 2012-06-08 | ||
JP2012130671A JP5488644B2 (ja) | 2012-02-09 | 2012-06-08 | 圧縮機 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2013118514A1 true WO2013118514A1 (ja) | 2013-08-15 |
Family
ID=48947284
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Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2013/000714 WO2013118514A1 (ja) | 2012-02-09 | 2013-02-08 | 圧縮機 |
Country Status (4)
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US (1) | US9617996B2 (ja) |
JP (1) | JP5488644B2 (ja) |
CN (1) | CN104105878B (ja) |
WO (1) | WO2013118514A1 (ja) |
Families Citing this family (19)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US10036388B2 (en) * | 2013-06-27 | 2018-07-31 | Emerson Climate Technologies, Inc. | Scroll compressor with oil management system |
US10294942B2 (en) | 2014-12-12 | 2019-05-21 | Daikin Industries, Ltd. | Compressor |
WO2016092688A1 (ja) * | 2014-12-12 | 2016-06-16 | 三菱電機株式会社 | 圧縮機 |
US9938977B2 (en) * | 2015-02-03 | 2018-04-10 | Emerson Climate Technologies, Inc. | Compressor with oil pump assembly |
CN106151047B (zh) * | 2015-04-24 | 2019-11-15 | 艾默生环境优化技术(苏州)有限公司 | 涡旋压缩机和用于涡旋压缩机的驱动轴 |
US10641269B2 (en) | 2015-04-30 | 2020-05-05 | Emerson Climate Technologies (Suzhou) Co., Ltd. | Lubrication of scroll compressor |
CN106555757B (zh) * | 2015-09-25 | 2019-03-26 | 珠海格力节能环保制冷技术研究中心有限公司 | 一种压缩机 |
CN105351203B (zh) * | 2015-11-09 | 2017-11-24 | 珠海格力节能环保制冷技术研究中心有限公司 | 一种压缩机 |
US10890187B2 (en) * | 2016-03-31 | 2021-01-12 | Mitsubishi Electric Corporation | Scroll compressor witha lubricant supply system and refrigeration cycle apparatus having the scroll compressor |
WO2018012016A1 (ja) * | 2016-07-13 | 2018-01-18 | 三菱電機株式会社 | 圧縮機 |
CN106949049B (zh) * | 2017-04-28 | 2020-06-02 | 上海海立新能源技术有限公司 | 一种立式压缩机 |
CN106930941B (zh) * | 2017-04-28 | 2020-06-02 | 上海海立新能源技术有限公司 | 一种压缩机 |
KR101973677B1 (ko) * | 2017-09-28 | 2019-08-26 | 엘지전자 주식회사 | 윤활유 공급장치 및 이를 적용한 압축기 |
KR102116681B1 (ko) * | 2018-09-18 | 2020-05-29 | 엘지전자 주식회사 | 압축기 |
CN109386463A (zh) * | 2018-12-06 | 2019-02-26 | 珠海格力节能环保制冷技术研究中心有限公司 | 压缩机 |
EP3770430B1 (en) * | 2019-07-26 | 2023-09-06 | Arçelik Anonim Sirketi | A compressor with improved lubrication performance |
KR102309304B1 (ko) | 2019-11-05 | 2021-10-07 | 엘지전자 주식회사 | 압축기 |
FR3120661B1 (fr) * | 2021-03-10 | 2023-03-10 | Danfoss Commercial Compressors | Compresseur à spirales ayant une pompe à huile centrifuge |
FR3120662B1 (fr) * | 2021-03-10 | 2023-03-03 | Danfoss Commercial Compressors | Compresseur à spirales pourvu d'un agencement de palier inférieur hydrostatique |
Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS60116086U (ja) * | 1984-01-17 | 1985-08-06 | 三菱重工業株式会社 | 密閉型電動圧縮機 |
JPH04143489A (ja) * | 1990-10-04 | 1992-05-18 | Daikin Ind Ltd | スクロール形流体機械 |
JP2002349460A (ja) * | 2001-05-18 | 2002-12-04 | Fujitsu General Ltd | スクロール型圧縮機 |
JP2005048689A (ja) * | 2003-07-30 | 2005-02-24 | Matsushita Electric Ind Co Ltd | スクロール圧縮機 |
JP2009127614A (ja) * | 2007-11-28 | 2009-06-11 | Hitachi Appliances Inc | スクロール流体機械及びその製造方法 |
Family Cites Families (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3162129A (en) * | 1962-07-13 | 1964-12-22 | Sundstrand Corp | Two-stage fuel unit |
JPH109160A (ja) * | 1996-06-24 | 1998-01-13 | Daikin Ind Ltd | スクロール圧縮機 |
CN1782426A (zh) * | 2004-11-30 | 2006-06-07 | 乐金电子(天津)电器有限公司 | 卷轴式压缩机 |
JP2010285930A (ja) | 2009-06-11 | 2010-12-24 | Daikin Ind Ltd | スクロール圧縮機 |
-
2012
- 2012-06-08 JP JP2012130671A patent/JP5488644B2/ja not_active Expired - Fee Related
-
2013
- 2013-02-08 US US14/377,124 patent/US9617996B2/en not_active Expired - Fee Related
- 2013-02-08 WO PCT/JP2013/000714 patent/WO2013118514A1/ja active Application Filing
- 2013-02-08 CN CN201380008492.2A patent/CN104105878B/zh not_active Expired - Fee Related
Patent Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS60116086U (ja) * | 1984-01-17 | 1985-08-06 | 三菱重工業株式会社 | 密閉型電動圧縮機 |
JPH04143489A (ja) * | 1990-10-04 | 1992-05-18 | Daikin Ind Ltd | スクロール形流体機械 |
JP2002349460A (ja) * | 2001-05-18 | 2002-12-04 | Fujitsu General Ltd | スクロール型圧縮機 |
JP2005048689A (ja) * | 2003-07-30 | 2005-02-24 | Matsushita Electric Ind Co Ltd | スクロール圧縮機 |
JP2009127614A (ja) * | 2007-11-28 | 2009-06-11 | Hitachi Appliances Inc | スクロール流体機械及びその製造方法 |
Also Published As
Publication number | Publication date |
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JP2013177877A (ja) | 2013-09-09 |
JP5488644B2 (ja) | 2014-05-14 |
US9617996B2 (en) | 2017-04-11 |
CN104105878A (zh) | 2014-10-15 |
US20150030487A1 (en) | 2015-01-29 |
CN104105878B (zh) | 2016-04-27 |
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