WO2014103204A1 - Compresseur à spirale - Google Patents

Compresseur à spirale Download PDF

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Publication number
WO2014103204A1
WO2014103204A1 PCT/JP2013/007242 JP2013007242W WO2014103204A1 WO 2014103204 A1 WO2014103204 A1 WO 2014103204A1 JP 2013007242 W JP2013007242 W JP 2013007242W WO 2014103204 A1 WO2014103204 A1 WO 2014103204A1
Authority
WO
WIPO (PCT)
Prior art keywords
oil
passage
housing
scroll
drive shaft
Prior art date
Application number
PCT/JP2013/007242
Other languages
English (en)
Japanese (ja)
Inventor
義友 塚
Original Assignee
ダイキン工業株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by ダイキン工業株式会社 filed Critical ダイキン工業株式会社
Priority to RU2015131143/06A priority Critical patent/RU2600206C1/ru
Priority to BR112015013435-1A priority patent/BR112015013435B1/pt
Priority to US14/758,174 priority patent/US20150330390A1/en
Priority to EP13869762.8A priority patent/EP2940302B1/fr
Priority to CN201380067868.7A priority patent/CN104903583B/zh
Priority to KR1020157020116A priority patent/KR101728261B1/ko
Priority to ES13869762T priority patent/ES2747231T3/es
Publication of WO2014103204A1 publication Critical patent/WO2014103204A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/02—Lubrication; Lubricant separation
    • F04C29/023—Lubricant distribution through a hollow driving shaft
    • 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
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/0042—Driving elements, brakes, couplings, transmissions specially adapted for pumps
    • F04C29/0085—Prime movers
    • 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
    • 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

Definitions

  • the present invention relates to a scroll type compressor, and particularly relates to a countermeasure against oil supply to a sliding portion of a compression mechanism.
  • a scroll type compressor having a fixed scroll and a movable scroll and compressing fluid between both scrolls is known and widely used in a refrigeration apparatus and the like.
  • Patent Document 1 discloses this type of scroll compressor.
  • the scroll compressor has an electric motor housed in a casing and a drive shaft that is rotationally driven by the electric motor.
  • the end of the drive shaft is engaged with the engaging portion of the end plate of the movable scroll.
  • the movable scroll rotates eccentrically with respect to the fixed scroll. Thereby, the compression chamber between both scrolls becomes small gradually, and fluid is compressed in this compression chamber.
  • a housing that rotatably accommodates the drive shaft is fixed to the inner peripheral surface of the casing.
  • An accommodation chamber is formed in the upper center portion of the housing so as to accommodate the engaging portion of the drive shaft and the movable scroll.
  • An oil pump that sucks up oil in the oil reservoir at the bottom of the casing is provided at the lower end of the drive shaft. The oil sucked up by the oil pump along with the rotation of the drive shaft flows upward through the oil flow path in the drive shaft, to the bearing portion of the drive shaft and the sliding portion between the engagement portion of the drive shaft and the movable scroll. After that, it flows out into the storage chamber.
  • the oil accumulated in the storage chamber sequentially flows in an oil flow path 44a extending radially outward from the storage chamber and an oil flow path 44b extending upward from the outflow side of the oil flow path 44a to slide the compression mechanism.
  • the thrust sliding surface of a compression mechanism is also used using the oil after utilized for lubrication of the sliding part between a drive shaft and the engaging part of a movable scroll. Lubricated.
  • the present invention has been made in view of such a point, and an object thereof is to provide a scroll type compressor that can reduce oil agitation loss in a storage chamber.
  • a casing (15), an electric motor (50) accommodated in the casing (15), a drive shaft (60) driven by the electric motor (50), and the drive shaft (60).
  • a compression mechanism (20) having an engaging portion (43) with which an end portion is engaged, a movable scroll (40) rotating eccentrically with respect to the drive shaft (60), and a fixed scroll (30);
  • a housing (25) having a bearing part (28) for supporting the drive shaft (60) and a housing part (26) for housing the engaging part (43), and an oil reservoir (18) of the casing (15) )
  • an oil conveying mechanism (75) for conveying the oil
  • the drive shaft (60) receives the oil conveyed by the oil conveying mechanism (75) on the sliding portion ( 44)
  • Scroll-type compressors with an oil supply passage (70) to be supplied to are targeted.
  • the scroll compressor is formed on the housing (25) at the bottom (26a) of the accommodating portion (26) and lubricates the sliding portion (44) of the engaging portion (43).
  • a recess (78) in which the oil is stored and an oil supply passage (70) for sending the oil in the recess (78) to the sliding portions (35, 45) of the compression mechanism (20) are formed.
  • the drive shaft (60) and the movable scroll (40) are connected by the end of the drive shaft (60) engaging with the engaging portion (43) of the movable scroll (40).
  • the electric motor (50) rotationally drives the drive shaft (60)
  • the movable scroll (40) rotates eccentrically with respect to the fixed scroll (30).
  • the volume of the compression chamber between the fixed scroll (30) and the movable scroll (40) is expanded and contracted, and the fluid is compressed in the compression chamber.
  • the oil transfer mechanism (75) is configured to slide the oil in the oil reservoir (18) of the casing (15) through the oil supply passage (70) between the drive shaft (60) and the engaging portion (43) ( 44). Thereby, a sliding part (44) is lubricated with oil, and sliding resistance becomes small.
  • the oil used for lubrication of the sliding part (44) of the engaging part (43) flows out into the housing part (26) that houses the engaging part (43).
  • the recess (78) is formed at the bottom of the accommodating portion (26), the oil that has flowed out flows down into the recess (78). Therefore, in the accommodating part (26), it is suppressed that oil accumulates to the circumference
  • the oil that has flowed down into the recess (78) is sent to the sliding portion (35, 45) of the compression mechanism (20) through the oil supply passage (90). Since the recess (78) is located at a position lower than the bottom of the storage portion (26), the oil in the storage portion (26) is sequentially supplied into the recess (78). For this reason, the oil in the recessed part (78) can be reliably supplied to the sliding parts (35, 45) of the compression mechanism (20).
  • the second invention is characterized in that, in the first invention, the recess (78) is constituted by an annular groove (78) surrounding the entire circumference of the bearing portion (28).
  • the concave portion of the second invention is constituted by an annular groove (78) surrounding the entire circumference of the bearing portion (28) of the drive shaft (60). If an annular groove is formed on the entire circumference of the bearing portion (28), the elastic coefficient of the portion of the housing (25) between the annular groove (78) and the bearing portion (28) becomes small. For this reason, even if the axis of the drive shaft (60) is inclined when the drive shaft (60) is rotated, this portion is easily deformed so as to be along the outer peripheral surface of the drive shaft (60). As a result, the outer peripheral surface of the drive shaft (60) can be prevented from coming into contact with the bearing portion (28), and the bearing load on the bearing portion (28) can be reduced.
  • the housing (25) is formed with an oil drainage path (80) for sending the oil in the housing part (26) to the oil reservoir (18). It is characterized by.
  • a part of the oil that has flowed down into the accommodating portion (26) is passed through the oil drainage passage (80). 18) Returned to.
  • the raise of the oil level height of a accommodating part (26) can be suppressed by returning the oil of a accommodating part (26) to an oil reservoir part (18) through an oil drainage path (80). Therefore, the engagement portion (43) can be prevented from being immersed in oil, and the oil stirring loss in the rotating engagement portion (43) is reduced.
  • the inflow port (80a) of the oil drainage passage (80) is arranged inside the housing part (26) so as to be along the bottom part (26a) of the housing part (26). It is characterized by having an opening.
  • the inlet (80a) of the oil drainage passage (80) is formed at a position along the bottom (26a) of the housing (26), the oil overflowing from the recess (78) is quickly drained. Can be led to the oil passage (80). Therefore, an increase in the oil level height of the accommodating portion (26) can be reliably suppressed.
  • the fifth invention is characterized in that, in the third invention, the inflow port (80a) of the oil drainage passage (80) opens into the recess (78).
  • part of the oil that has flowed down from the containing portion (26) to the recess (78) is returned to the oil reservoir (18) through the oil drainage passage (80). For this reason, it can prevent that the oil of a recessed part (78) overflows to an accommodating part (26), and can suppress the raise of the oil surface height of an accommodating part (26) reliably.
  • the recess (78) has a first chamber (S1) communicating with the inlet (90a) of the oil supply passage (90) and the oil discharge passage (
  • a partition member (100) for partitioning the second chamber (S2) communicating with the inflow port (80a) of 80) is formed from the bottom of the recess (78) to the opening surface, and the first chamber (S1 ) Is larger than the volume of the second chamber (S2).
  • the interior of the recess (78) is partitioned into a first chamber (S1) and a second chamber (S2) by a partition member (100).
  • the volume of the first chamber (S1) connected to the oil supply passage (90) is larger than the volume of the second chamber (S2) connected to the oil discharge passage (80).
  • the amount of oil that flows into the recess (78) after being used for lubricating the sliding portion (44) of the engaging portion (43) is also greater in the first chamber (S1) than in the second chamber (S2). Will increase. Therefore, in the present invention, sufficient oil can be secured to be supplied to the sliding portions (35, 45) of the compression mechanism (20) through the oil supply passage (90).
  • the height of the inflow port (90a) of the oil supply passage (90) is equal to that of the inflow port (80a) of the oil discharge passage (80). It is in a position lower than the height.
  • the height of the inlet (90a) of the oil supply passage (90) is lower than the height of the inlet (80a) of the oil passage (80). For this reason, if the oil level is between the inlet (90a) of the oil supply passage (90) and the inlet (80a) of the oil discharge passage (80), this oil will only enter the oil supply passage (90). Sent. On the other hand, when the oil level is higher than the inlet (80a) of the oil discharge passage (80), the oil is sent to both the oil supply passage (90) and the oil discharge passage (80).
  • the oil that has flowed into the housing part (26) is preferentially supplied to the oil supply path (90) rather than the oil discharge path (80), so the sliding part (35 of the compression mechanism (20) , 45) can be reliably lubricated.
  • the concave portion (78) is formed in the bottom portion (26a) of the accommodating portion (26), the oil used for lubrication of the sliding portion (44) of the engaging portion (43) is supplied to the concave portion (78 ) Can be sent in.
  • an accommodating part (26) it can suppress that an engaging part (43) is immersed in oil, and the stirring loss of the oil of the engaging part (43) in rotation can be reduced.
  • the engaging portion (43) can be prevented from being immersed in oil as described above, the compressed fluid may be mixed in the oil or the oil may be in a mist shape. Can be prevented. Therefore, the oil used for lubricating the sliding portion (44) can be quickly returned to the oil reservoir (18), and so-called oil rising can be prevented.
  • the second invention it is possible to prevent the drive shaft (60) and the bearing portion (28) from coming into contact with each other by configuring the concave portion with an annular groove (78). That is, in the present invention, since the annular groove (78) serves as a recess (78) for storing oil and a so-called elastic groove, the structure of the apparatus can be simplified.
  • the engagement part (43) is prevented from being immersed in the oil. It is possible to suppress oil agitation by the engaging portion (43).
  • the inflow port (80a) of the oil discharge passage (80) since the height of the inflow port (80a) of the oil discharge passage (80) is located along the bottom (26a) of the storage portion (26), the oil in the storage portion (26) is discharged. It can be discharged quickly.
  • the inflow port (80a) of the oil discharge passage (80) opens into the recess (78), so that the oil in the recess (78) is prevented from overflowing into the storage portion (26). it can.
  • the fourth and fifth inventions it is possible to effectively suppress an increase in the height of the oil level of the accommodating portion (26), and it is possible to reliably suppress oil agitation by the engaging portion (43).
  • the interior of the recess (78) is partitioned into a first chamber (S1) and a second chamber (S2) by a partition member (100), and the first chamber (S1) communicates with the oil supply passage (90). Since the volume of the second chamber (S2) is larger than that of the second chamber (S2), it is possible to prevent the amount of oil supplied from the oil supply passage (90) to the sliding portions (35, 45) of the compression mechanism (20) from being insufficient. Accordingly, the sliding portions (35, 45) of the compression mechanism (20) can be reliably lubricated, and as a result, the reliability of the scroll compressor can be improved.
  • the oil supply passage (90) is connected to the compression mechanism (20). It is possible to prevent the amount of oil supplied to the sliding portions (35, 45) from being insufficient. Accordingly, the sliding portions (35, 45) of the compression mechanism (20) can be reliably lubricated, and as a result, the reliability of the scroll compressor can be improved.
  • FIG. 1 is a longitudinal section showing the whole scroll compressor composition concerning an embodiment.
  • FIG. 2 is an enlarged vertical cross-sectional view of a main part of the compression mechanism and the housing according to the embodiment.
  • FIG. 3 is a horizontal sectional view showing the internal structure of the compression mechanism.
  • 4 is a sectional view taken along line XX of FIG.
  • FIG. 5 is a view corresponding to FIG. 2 of the scroll compressor according to the first modification.
  • FIG. 6 is a perspective view showing the internal structure of the central recess of the scroll compressor according to the second modification.
  • FIG. 7 is a horizontal sectional view showing the internal structure of the central recess of the scroll compressor according to the second modification.
  • the scroll compressor (10) of this embodiment is a hermetic compressor.
  • the scroll compressor (10) is connected to a refrigerant circuit that performs a refrigeration cycle, and sucks and compresses refrigerant in the refrigerant circuit.
  • a compression mechanism (20), an electric motor (50), a lower bearing member (55), and a drive shaft (60) are provided in the internal space of the casing (15). ) And is housed.
  • the casing (15) is a sealed container formed in a vertically long cylindrical shape.
  • a compression mechanism (20), an electric motor (50), and a lower bearing member (55) are arranged in order from the top to the bottom.
  • the drive shaft (60) is arranged in such a posture that its axial direction is along the height direction of the casing (15). The detailed structure of the compression mechanism (20) will be described later.
  • the casing (15) is provided with a suction pipe (16) and a discharge pipe (17).
  • the suction pipe (16) and the discharge pipe (17) both penetrate the casing (15).
  • the suction pipe (16) is connected to the compression mechanism (20).
  • the discharge pipe (17) opens in a portion between the electric motor (50) and the compression mechanism (20) in the internal space of the casing (15).
  • the lower bearing member (55) includes a central cylindrical portion (56) and an arm portion (57). Although only one is shown in FIG. 1, the lower bearing member (55) is provided with three arms (57).
  • the central cylindrical portion (56) is formed in a substantially cylindrical shape. Each arm portion (57) extends outward from the outer peripheral surface of the central cylindrical portion (56). In the lower bearing member (55), the three arm portions (57) are arranged at substantially equal angular intervals. The protruding end portion of each arm portion (57) is fixed to the casing (15). Near the upper end of the central cylindrical portion (56), a bearing metal (58) is inserted. A sub journal portion (67) of a drive shaft (60), which will be described later, is inserted through the bearing metal (58).
  • the central cylindrical portion (56) constitutes a journal bearing that supports the sub journal portion (67).
  • the electric motor (50) includes a stator (51) and a rotor (52).
  • the stator (51) is fixed to the casing (15).
  • the rotor (52) is arranged coaxially with the stator (51).
  • a main shaft portion (61) of a drive shaft (60), which will be described later, is inserted through the rotor (52).
  • a plurality of core cuts (51a) through which refrigerant and oil flow are formed on both ends of the stator (51) in the axial direction on the outer peripheral surface of the stator (51).
  • the drive shaft (60) is formed with a main shaft portion (61), a balance weight portion (62), and an eccentric portion (63).
  • the balance weight part (62) is disposed in the middle of the main shaft part (61) in the axial direction.
  • the main shaft portion (61) has a lower portion than the balance weight portion (62) passing through the rotor (52) of the electric motor (50).
  • the portion above the balance weight portion (62) constitutes the main journal portion (64), and the sub journal portion (67) below the portion penetrating the rotor (52). ) Is formed.
  • the main journal portion (64) is inserted through a bearing metal (28) provided in the central bulge portion (27) of the housing (25).
  • the sub-journal part (67) is inserted through a bearing metal (58) provided in the central cylindrical part (56) of the lower bearing member (55).
  • the eccentric part (63) is formed at the upper end of the drive shaft (60).
  • the eccentric part (63) is formed in a cylindrical shape having a smaller diameter than the main journal part (64), and projects from the upper end surface of the main journal part (64).
  • the shaft center of the eccentric portion (63) is parallel to the shaft center of the main journal portion (64) (that is, the shaft center of the main shaft portion (61)) and is eccentric to the shaft center of the main journal portion (64). Yes.
  • the eccentric part (63) is inserted into a bearing metal (44) provided in the cylindrical part (43) of the movable scroll (40).
  • the cylindrical portion (43) of the movable scroll (40) constitutes an engaging portion with which the eccentric portion (63) is rotatably engaged.
  • An oil supply passage (70) is formed in the drive shaft (60).
  • the oil supply passage (70) includes one main passage (74) and three branch passages (71 to 73).
  • the main passage (74) extends along the axis of the drive shaft (60), and one end thereof opens to the lower end of the main shaft portion (61) and the other end opens to the upper end surface of the eccentric portion (63). ing.
  • the first branch passage (71) is formed in the eccentric part (63).
  • the first branch passage (71) extends from the main passage (74) to the outer side in the radial direction of the eccentric portion (63), and opens to the outer peripheral surface of the eccentric portion (63).
  • the second branch passage (72) is formed in the main journal portion (64).
  • the second branch passage (72) extends from the main passage (74) to the outer side in the radial direction of the main journal portion (64), and opens on the outer peripheral surface of the main journal portion (64).
  • the third branch passage (73) is formed in the secondary journal section (67).
  • the third branch passage (73) extends from the main passage (74) to the outer side in the radial direction of the sub journal portion (67), and is open to the outer peripheral surface of the sub journal portion (67).
  • An oil supply pump (75) as an oil transfer mechanism is attached to the lower end of the drive shaft (60).
  • the oil supply pump (75) is a trochoid pump driven by the drive shaft (60).
  • the oil supply pump (75) is disposed near the start end of the main passage (74) of the oil supply passage (70).
  • the oil supply pump (75) has a suction port (76) that opens downward at the lower end and sucks refrigeration oil, which is lubricating oil.
  • the oil supply pump (75) is not limited to the trochoid pump, and may be a positive displacement pump driven by the drive shaft (60). Therefore, the oil supply pump (75) may be a gear pump, for example.
  • Refrigerator oil which is lubricating oil, is stored at the bottom of the casing (15). That is, the oil reservoir (18) is formed at the bottom of the casing (15).
  • the oil supply pump (75) sucks and discharges refrigeration oil from the oil reservoir (18), and the refrigeration oil discharged from the oil supply pump (75) flows through the main passage (74).
  • the refrigeration oil flowing through the main passage (74) is supplied to the lower bearing member (55), the compression mechanism (20), and the sliding portion of the drive shaft (60). Since the oil supply pump (75) is a positive displacement pump, the flow rate of the refrigeration oil in the main passage (74) is proportional to the rotational speed of the drive shaft (60).
  • a housing (25) is provided inside the casing (15) above the electric motor (50).
  • the housing (25) is formed in a thick disk shape, and its outer peripheral edge is fixed to the casing (15).
  • a central concave portion (26) and an annular convex portion (29) are formed in the central portion of the housing (25).
  • the central recess (26) is a cylindrical recess that opens on the upper surface of the housing (25).
  • the central recess (26) constitutes a housing portion that houses the cylindrical portion (43) of the movable scroll (40) and the eccentric portion (63) of the drive shaft (60).
  • the annular convex portion (29) is formed along the outer periphery of the central concave portion (26) and protrudes from the upper surface of the housing (25).
  • the protruding end surface of the annular convex portion (29) is a flat surface.
  • a ring-shaped concave groove is formed along the circumferential direction of the projecting end surface of the annular convex portion (29), and a seal member (29a) is fitted into the concave groove.
  • the central bulge portion (27) is formed in the housing (25).
  • the central bulging portion (27) is located below the central concave portion (26) and bulges downward.
  • a through-hole penetrating the central bulge portion (27) vertically is formed in the central bulge portion (27), and a bearing metal (28) is inserted into the through-hole.
  • the main journal portion (64) of the drive shaft (60) is inserted through the bearing metal (28) of the central bulge portion (27).
  • the central bulge portion (27) constitutes a journal bearing that supports the main journal portion (64).
  • the compression mechanism (20) includes a fixed scroll (30) and a movable scroll (40).
  • the compression mechanism (20) is provided with an Oldham coupling (24) for restricting the rotation of the movable scroll (40).
  • a fixed scroll (30) and a movable scroll (40) are placed on the housing (25).
  • the fixed scroll (30) is fixed to the housing (25) with bolts or the like.
  • the movable scroll (40) is engaged with the housing (25) via the Oldham coupling (24), and is movable relative to the housing (25).
  • the movable scroll (40) engages with the drive shaft (60) to perform eccentric rotational movement.
  • the movable scroll (40) is a member in which a movable side end plate portion (41), a movable side wrap (42), and a cylindrical portion (43) are integrally formed.
  • the movable side end plate portion (41) is formed in a disc shape.
  • the movable side wrap (42) is formed in a spiral wall shape, and protrudes from the front surface (upper surface in FIGS. 1 and 2) of the movable side end plate portion (41).
  • the cylindrical portion (43) is formed in a cylindrical shape, and protrudes from the back surface (the lower surface in FIGS. 1 and 2) of the movable side end plate portion (41).
  • the rear surface of the movable side end plate portion (41) of the movable scroll (40) is in sliding contact with the seal member (29a) provided on the annular convex portion (29) of the housing (25).
  • the cylindrical portion (43) of the movable scroll (40) is inserted from above into the central recess (26) of the housing (25).
  • a bearing metal (44) is inserted into the cylindrical part (43) as a sliding part with which the eccentric part (63) comes into sliding contact.
  • An eccentric portion (63) of the drive shaft (60) described later is inserted into the bearing metal (44) of the cylindrical portion (43) from below.
  • the cylindrical portion (43) constitutes a journal bearing that slides with the eccentric portion (63).
  • the fixed scroll (30) is a member in which a fixed side end plate part (31), a fixed side wrap (32), and an outer peripheral part (33) are integrally formed.
  • the fixed side end plate portion (31) is formed in a disc shape.
  • the fixed side wrap (32) is formed in a spiral wall shape, and protrudes from the front surface (the lower surface in FIGS. 1 and 2) of the fixed side end plate portion (31).
  • the outer peripheral portion (33) is formed in a thick ring shape extending downward from the outer peripheral portion (33) of the fixed-side end plate portion (31) and surrounds the fixed-side wrap (32).
  • the discharge port (22) is formed in the fixed side end plate part (31).
  • the discharge port (22) is a through hole formed in the vicinity of the center of the fixed-side end plate portion (31), and passes through the fixed-side end plate portion (31) in the thickness direction.
  • a suction pipe (16) is inserted in the vicinity of the outer periphery of the fixed-side end plate part (31).
  • a discharge gas passage (23) is formed in the compression mechanism (20).
  • the start end of the discharge gas passage (23) communicates with the discharge port (22).
  • the discharge gas passage (23) is formed from the fixed scroll (30) to the housing (25), and the other end opens to the lower surface of the housing (25).
  • the fixed scroll (30) and the movable scroll (40) have the front surface of the fixed side end plate portion (31) and the front surface of the movable side end plate portion (41) facing each other, and the fixed side wrap (32)
  • the movable wraps (42) are arranged so as to mesh with each other.
  • the fixed wrap (32) and the movable wrap (42) mesh with each other to form a plurality of compression chambers (21).
  • the movable side end plate portion (41) of the movable scroll (40) and the outer peripheral portion (33) of the fixed scroll (30) are in sliding contact with each other.
  • a portion of the front surface (upper surface in FIGS. 1 and 2) on the outer peripheral side of the movable side wrap (42) is in sliding contact with the fixed scroll (30).
  • the outer peripheral portion (33) of the fixed scroll (30) has its protruding end surface (the lower surface in FIGS. 1 and 2) in sliding contact with the movable thrust sliding surface (45) of the movable scroll (40).
  • a portion of the protruding end surface that is in sliding contact with the movable side thrust sliding surface (45) is a fixed side thrust sliding surface (35). That is, the fixed-side thrust sliding surface (35) and the movable-side thrust sliding surface (45) constitute a sliding portion of the compression mechanism (20).
  • annular groove (78) is formed in the bottom (26a) of the central recess (26) described above.
  • the annular groove (78) is constituted by a recess opened upward.
  • the center of the annular groove (78) substantially coincides with the axis of the main journal portion (64) and surrounds the entire circumference of the bearing metal (28) that is the bearing portion.
  • the annular groove (78) constitutes a so-called elastic groove. That is, in the housing (25), a cylindrical convex portion (79) protruding upward is formed between the annular groove (78) and the bearing metal (28).
  • the main journal portion (64) When the main journal portion (64) is bent radially outward during the rotation of the drive shaft (60), the cylindrical convex portion (79) is elastically deformed along the main journal portion (64). . As a result, the main journal portion (64) can be prevented from being in line contact with the bearing metal (28), so-called one-side contact, and the bearing load of the bearing metal (28) can be reduced.
  • ⁇ Oil used to lubricate the bearing metal (28) of the main journal part (64) flows out into the central recess (26) of the housing (25) through the oil supply passage (70).
  • the housing (25) has an oil drainage path (80) for sending the oil that has flowed into the central recess (26) to the oil reservoir (18), and the sliding part (fixed side) of the compression mechanism (20).
  • An oil supply passage (90) for feeding the thrust sliding surface (35) and the movable-side thrust sliding surface (45) is formed.
  • the oil drainage passage (80) of the present embodiment is formed on the annular convex portion (29) of the housing (25).
  • the oil drainage path (80) includes a horizontal hole (81) that penetrates the lower end of the annular convex part (29) in the radial direction and a vertical hole (82) that extends downward from the outflow end of the horizontal hole (81). Composed.
  • the inflow port (80a) of the oil drainage passage (80) opens into the center recess (26).
  • the height of the lower end of the inflow port (80a) of the oil drainage passage (80) is substantially the same as the height (26a) of the central recess (26). That is, the inflow port (80a) of the oil drainage passage (80) is disposed along the bottom (26a) of the central recess (26).
  • An oil catch plate (83) is provided below the vertical hole (82) of the oil drainage passage (80).
  • the oil catching plate (83) has a diameter-expanded portion (83a) whose diameter is increased upward, and a lower nozzle portion (83b) that is extended downward from the diameter-expanded portion (83a).
  • the outflow end (lower end) of the lower nozzle part (83b) is located inside the core cut (51a) of the stator (51).
  • the oil supply passage (90) is formed from the central bulging portion (27) of the housing (25) to the annular convex portion (29).
  • the oil supply passage (90) includes a first oil supply hole (91) and a second oil supply hole (92).
  • the first oil supply hole (91) extends obliquely upward from the annular groove (78) outward in the radial direction inside the housing (25).
  • the inlet (91a) of the first oil supply hole (91) opens into the annular groove (78).
  • the height of the inlet (91a) of the first oil supply hole (91) is lower than the height of the inlet (80a) of the oil discharge passage (80).
  • the height of the inlet (91a) of the first oil supply hole (91) is higher than the bottom surface of the annular groove (78).
  • the second oil supply hole (92) is formed through the annular protrusion (29) of the housing (25) in the axial direction so as to communicate with the outflow end of the first oil supply hole (91).
  • the screw member (93) is inserted through the second oil supply hole (92).
  • the head (93a) of the screw member (93) closes the lower end of the second oil supply hole (92).
  • the screw member (93) constitutes a pressure reducing mechanism (throttle mechanism) for reducing the pressure of the oil flowing through the second oil supply hole (92).
  • an oil communication passage (94) communicating with the second oil supply hole (92), and the oil communication passage (94).
  • a communicating oil groove (95) is formed.
  • the inflow end of the oil communication passage (94) is connected to the second oil supply hole (92) inside the housing (25).
  • the outflow end of the oil communication passage (94) opens toward the movable thrust sliding surface (45) of the movable scroll (40).
  • the oil groove (95) is a concave groove formed in the fixed-side thrust sliding surface (35) of the outer peripheral portion (33), and is formed in a ring shape surrounding the periphery of the fixed-side wrap (32).
  • the oil groove (95) communicates with the outflow end of the oil communication passage (94).
  • the compression chamber (21) is closed from the suction pipe (16), and then the compression chamber (21) is separated from the fixed wrap (32) and the movable wrap ( 42) and move toward the inner circumferential edge. In the process, the volume of the compression chamber (21) gradually decreases, and the gas refrigerant in the compression chamber (21) is compressed.
  • the compression chamber (21) When the volume of the compression chamber (21) gradually decreases as the movable scroll (40) moves, the compression chamber (21) eventually communicates with the discharge port (22). Then, the refrigerant compressed in the compression chamber (21) (that is, high-pressure gas refrigerant) flows into the discharge gas passage (23) through the discharge port (22), and then the internal space of the casing (15). Is discharged. In the internal space of the casing (15), the high-pressure gas refrigerant discharged from the compression mechanism (20) is once guided below the stator (51) of the electric motor (50), and then the rotor (52) And flows through the gap between the stator (51) and the like, and flows out of the casing (15) through the discharge pipe (17).
  • the high pressure gas refrigerant discharged from the compression mechanism (20) circulates in the inner space of the casing (15) below the housing (25), and the pressure is substantially equal to the pressure of the high pressure gas refrigerant. Are equal. Therefore, the pressure of the refrigerating machine oil stored in the oil reservoir (18) in the casing (15) is also substantially equal to the pressure of the high-pressure gas refrigerant.
  • the portion of the internal space of the casing (15) above the housing (25) communicates with the suction pipe (16) (not shown), and the low pressure gas whose pressure is sucked into the compression mechanism (20) It is about the same as the pressure of the refrigerant. Therefore, in the compression mechanism (20), the pressure in the space near the outer periphery of the movable side end plate portion (41) of the movable scroll (40) is approximately the same as the pressure of the low-pressure gas refrigerant.
  • the oil flowing into the first branch passage (71) is supplied to the gap between the eccentric portion (63) and the bearing metal (44), and is used for lubrication and cooling of the eccentric portion (63) and the bearing metal (44).
  • the oil used for lubricating the bearing metal (44) flows out into the central recess (26).
  • the cylindrical portion (43) of the movable scroll (40) may be immersed in the oil.
  • the oil in the central recess (26) becomes the resistance of the cylindrical portion (43), so-called stirring loss increases, and the power of the electric motor (50) is increased. Incurs an increase.
  • the high-pressure gas refrigerant in the casing (15) may be mixed into the oil, or the oil may be refined in a mist shape. There is.
  • an annular groove (78) is formed in the bottom (26a) of the central recess (26) in order to prevent oil from being stirred by the cylindrical portion (43) in the central recess (26).
  • the refrigerant that has been used to lubricate the bearing metal (44) and has flowed into the central recess (26) flows down from the bottom (26a) of the central recess (26) into the annular groove (78).
  • the oil level in the annular groove (78) exceeds the height position of the inlet (90a) of the first oil supply hole (91)
  • the oil in the annular groove (78) becomes the first oil supply hole (91).
  • This oil passes through the first oil supply hole (91) and flows upward through the second oil supply hole (92).
  • the second oil supply hole (92) the high pressure oil is decompressed by the screw member (93).
  • the oil that has passed through the second oil supply hole (92) flows into the oil groove (95) via the oil communication passage (94) inside the fixed scroll (30).
  • the sliding portion between the fixed-side thrust sliding surface (35) and the movable-side thrust sliding surface (45) is lubricated with oil.
  • the oil that has flowed into the central recess (26) is appropriately supplied to the sliding portion of the compression mechanism (20) through the annular groove (78) and the oil supply passage (90).
  • the oil level height in the central recess (26) is suppressed from increasing, and the area where the cylindrical portion (43) of the movable scroll (40) is immersed in oil can be suppressed.
  • annular groove (78) is formed around the bearing metal (28) of the main journal portion (64), so that a cylindrical shape is formed between the annular groove (78) and the bearing metal (28).
  • a convex part (79) can be formed.
  • the inflow port (90a) of the oil supply path (90) is opened inside the annular groove (78), and the inflow port (80a) of the oil discharge path (80) is formed inside the central recess (26). Is open. That is, the height of the inlet (90a) of the oil supply passage (90) is lower than the height of the inlet (80a) of the oil discharge passage (80). For this reason, the oil that has flowed into the central recess (26) is preferentially introduced into the oil supply passage (90) rather than the oil discharge passage (80), so the sliding portions (35, 45) oil can be supplied reliably, and the reliability of the scroll compressor (10) can be improved.
  • the scroll compressor (10) according to the first modification shown in FIG. 5 is different from the above embodiment in the configuration of the oil discharge passage (80).
  • the oil drainage passage (80) of Modification 1 has an inflow port (80a) that opens into the annular groove (78).
  • the oil drainage passage (80) extends downward from the lateral hole (81) extending radially outward from the annular groove (78) and from the radially outer end of the lateral hole (81).
  • a vertical hole (82) Inside the annular groove (78), the height of the inlet (90a) of the oil supply passage (90) is lower than the height of the inlet (80a) of the oil discharge passage (80).
  • the oil that has flowed into the central recess (26) is preferentially introduced into the oil supply passage (90) rather than the oil discharge passage (80), so that the compression mechanism (20) Oil can be reliably supplied to the sliding parts (35, 45), and the reliability of the scroll compressor (10) can be improved.
  • Modification 2 shown in FIGS. 6 and 7 has the same configuration of the housing (25) as that of Modification 1, and a partition member (100) is provided inside the annular groove (78).
  • the partition member (100) extends in the axial direction of the annular groove (78) from the bottom part on the lower side of the annular groove (78) to the opening end on the upper side of the annular groove (78).
  • the partition member (100) has a cross-sectional shape perpendicular to the axial direction of the annular groove (78) formed in a substantially U-shape (U-shape), and is fitted into the annular groove (78).
  • the partition member (100) is formed on each of the vertical wall portion (100a) curved in an arc shape along the inner peripheral surface of the annular groove (78) and both ends in the circumferential direction of the vertical wall portion (100a). And a pair of side wall portions (100b).
  • the vertical wall (100a) is disposed at a position facing the inlet (80a) of the oil drainage passage (80).
  • Each vertical wall portion (100a) extends in the radial direction from the inner inner peripheral surface of the annular groove (78) to the outer outer peripheral surface.
  • the opening area at the upper end of the first chamber (S1) is larger than the opening area at the upper end of the second chamber (S2). That is, in the annular groove (78), the volume of the first chamber (S1) is larger than the volume of the second chamber (S2). For this reason, in Modification 2, much of the oil that has flowed into the central recess (26) flows down to the first chamber (S1) rather than the second chamber (S2), and is sufficient for the first chamber (S1). You can store oil. Therefore, the oil can be reliably supplied to the sliding portions (35, 45) of the compression mechanism (20) through the first chamber (S1) and the oil supply passage (90), and the reliability of the scroll compressor (10) is improved. Can be improved.
  • the annular recess (78) is formed at the bottom (26a) of the central recess (26) so as to surround the main journal portion (64).
  • the recess (78) is not necessarily annular.
  • the cross-sectional shape perpendicular to the axis may be a rectangle, a straight line, or a dot. That is, the concave portion (78) may have any shape as long as it can capture the oil that has flowed into the central concave portion (26).
  • the present invention relates to a scroll compressor, and is particularly useful as a countermeasure against oil supply to the sliding portion of the compression mechanism.

Abstract

Selon l'invention, un creux (78), qui est formé dans la partie inférieure (26a) d'une partie de réception (26), et dans lequel de l'huile s'accumule après la lubrification d'une partie de glissement (44) d'une partie de prise (43), et un passage d'alimentation en huile (70), qui introduit l'huile dans le creux (78) vers des parties de glissement (35, 45) du compresseur (20), sont formés dans le boîtier (25) d'un compresseur à spirale.
PCT/JP2013/007242 2012-12-28 2013-12-10 Compresseur à spirale WO2014103204A1 (fr)

Priority Applications (7)

Application Number Priority Date Filing Date Title
RU2015131143/06A RU2600206C1 (ru) 2012-12-28 2013-12-10 Спиральный компрессор
BR112015013435-1A BR112015013435B1 (pt) 2012-12-28 2013-12-10 Compressor do tipo scroll
US14/758,174 US20150330390A1 (en) 2012-12-28 2013-12-10 Scroll compressor
EP13869762.8A EP2940302B1 (fr) 2012-12-28 2013-12-10 Compresseur à spirale
CN201380067868.7A CN104903583B (zh) 2012-12-28 2013-12-10 涡旋式压缩机
KR1020157020116A KR101728261B1 (ko) 2012-12-28 2013-12-10 스크롤형 압축기
ES13869762T ES2747231T3 (es) 2012-12-28 2013-12-10 Compresor de espiral

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2012-288807 2012-12-28
JP2012288807A JP5655850B2 (ja) 2012-12-28 2012-12-28 スクロール型圧縮機

Publications (1)

Publication Number Publication Date
WO2014103204A1 true WO2014103204A1 (fr) 2014-07-03

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Application Number Title Priority Date Filing Date
PCT/JP2013/007242 WO2014103204A1 (fr) 2012-12-28 2013-12-10 Compresseur à spirale

Country Status (9)

Country Link
US (1) US20150330390A1 (fr)
EP (1) EP2940302B1 (fr)
JP (1) JP5655850B2 (fr)
KR (1) KR101728261B1 (fr)
CN (1) CN104903583B (fr)
BR (1) BR112015013435B1 (fr)
ES (1) ES2747231T3 (fr)
RU (1) RU2600206C1 (fr)
WO (1) WO2014103204A1 (fr)

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WO2017015456A1 (fr) 2015-07-22 2017-01-26 Trane International Inc. Drain de boîtier de palier de compresseur
RU2629049C1 (ru) * 2016-05-24 2017-08-24 Леонид Михайлович Курин Спиральный компрессор и способ его работы
CN107289115A (zh) * 2016-04-01 2017-10-24 舍弗勒技术股份两合公司 轮内驱动总成
WO2019027342A1 (fr) * 2017-08-04 2019-02-07 Леонид Михайлович КУРИН Compresseur à spirales et procédé de fonctionnement
JP2021025502A (ja) * 2019-08-08 2021-02-22 日立ジョンソンコントロールズ空調株式会社 スクロール圧縮機

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CN105332913B (zh) * 2015-11-23 2017-09-22 珠海格力节能环保制冷技术研究中心有限公司 一种涡旋压缩机及包括该压缩机的电器产品
US10132317B2 (en) * 2015-12-15 2018-11-20 Bitzer Kuehlmaschinenbau Gmbh Oil return with non-circular tube
KR102405400B1 (ko) 2017-02-13 2022-06-07 엘지전자 주식회사 스크롤 압축기
DE102017209553A1 (de) * 2017-06-07 2018-12-13 Robert Bosch Gmbh Zahnradpumpe für ein Abwärmerückgewinnungssystem
KR102515119B1 (ko) 2019-01-18 2023-03-29 한온시스템 주식회사 스크롤 압축기
KR20240008722A (ko) * 2022-07-12 2024-01-19 삼성전자주식회사 배유 통로를 구비한 스크롤 압축기

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WO2017015456A1 (fr) 2015-07-22 2017-01-26 Trane International Inc. Drain de boîtier de palier de compresseur
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US10851787B2 (en) 2015-07-22 2020-12-01 Trane International Inc. Compressor bearing housing drain
CN107289115A (zh) * 2016-04-01 2017-10-24 舍弗勒技术股份两合公司 轮内驱动总成
CN107289115B (zh) * 2016-04-01 2021-08-17 舍弗勒技术股份两合公司 轮内驱动总成
RU2629049C1 (ru) * 2016-05-24 2017-08-24 Леонид Михайлович Курин Спиральный компрессор и способ его работы
WO2019027342A1 (fr) * 2017-08-04 2019-02-07 Леонид Михайлович КУРИН Compresseur à spirales et procédé de fonctionnement
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JP7373939B2 (ja) 2019-08-08 2023-11-06 日立ジョンソンコントロールズ空調株式会社 スクロール圧縮機

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KR20150099849A (ko) 2015-09-01
BR112015013435A2 (pt) 2017-07-11
CN104903583A (zh) 2015-09-09
BR112015013435B1 (pt) 2021-11-30
KR101728261B1 (ko) 2017-04-18
EP2940302A4 (fr) 2016-08-24
CN104903583B (zh) 2017-10-10
ES2747231T3 (es) 2020-03-10
US20150330390A1 (en) 2015-11-19
JP2014129793A (ja) 2014-07-10
RU2600206C1 (ru) 2016-10-20
JP5655850B2 (ja) 2015-01-21
EP2940302A1 (fr) 2015-11-04
EP2940302B1 (fr) 2019-07-10

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