WO2017081845A1 - Compresseur - Google Patents

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Publication number
WO2017081845A1
WO2017081845A1 PCT/JP2016/004676 JP2016004676W WO2017081845A1 WO 2017081845 A1 WO2017081845 A1 WO 2017081845A1 JP 2016004676 W JP2016004676 W JP 2016004676W WO 2017081845 A1 WO2017081845 A1 WO 2017081845A1
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WO
WIPO (PCT)
Prior art keywords
oil
suction
oil passage
compression
passage
Prior art date
Application number
PCT/JP2016/004676
Other languages
English (en)
Japanese (ja)
Inventor
壮宏 山田
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 US15/765,235 priority Critical patent/US20180298900A1/en
Priority to EP16863812.0A priority patent/EP3339647A1/fr
Priority to CN201680058627.XA priority patent/CN108138779A/zh
Publication of WO2017081845A1 publication Critical patent/WO2017081845A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F04C18/0246—Details concerning the involute wraps or their base, e.g. geometry
    • F04C18/0253—Details concerning the base
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/008—Hermetic pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/10—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by changing the positions of the inlet or outlet openings with respect to the working chamber
    • F04C28/16—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by changing the positions of the inlet or outlet openings with respect to the working chamber using lift valves
    • 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

Definitions

  • the present invention relates to a technique for eliminating insufficient lubrication of a compression mechanism in a compressor having a suction bypass mechanism that adjusts a suction volume by changing a suction closing position.
  • inverter machines have been widely used in order to cope with a wide range of operation, and have been used from high speed rotation to low speed rotation.
  • the refrigerant flow rate inside the compressor increases during high-speed rotation, the amount of refrigerating machine oil sucked together with the refrigerant supplied into the compressor compression mechanism increases, and the amount of refrigerating machine oil discharged together with the compressed refrigerant. Will increase. Therefore, a technique for reducing the amount of refrigerating machine oil supplied into the compression mechanism is required.
  • Patent Document 1 discloses a suction bypass mechanism that adjusts the suction volume by changing the suction closing position of the scroll compressor.
  • the suction bypass mechanism of Patent Document 1 includes a first compression chamber between the inner peripheral surface of the fixed scroll and the outer peripheral surface of the movable scroll, and a second compression chamber between the outer peripheral surface of the fixed scroll and the inner peripheral surface of the movable scroll. And a plunger (valve) as an opening and closing mechanism for switching between a communication state and a blocking state.
  • the suction closed position is changed from the shut-off position to a position where the suction volume is reduced.
  • the compression mechanism is rotated at a high speed when the suction volume is reduced, so that performance can be ensured.
  • the compressor is rotated at a high operating speed at a low operating capacity with a capacity control compared to when the capacity control is not performed, the performance deterioration can be suppressed as compared with a capacity operating without a capacity control, but a low operating capacity. Therefore, the oil supplied to the compression chamber is insufficient, and a sufficient performance cannot be ensured because the oil film inside the compression mechanism is not sufficiently formed.
  • the present invention has been made in view of such problems, and an object thereof is to improve the performance at the low operating capacity while suppressing the oil rising at the high operating capacity of the compressor.
  • a first aspect of the present disclosure includes a compression mechanism (20) and a casing (10) that houses the compression mechanism (20), and the compression mechanism (20) includes a compression chamber (25a, 25b) in a suction stroke.
  • a suction volume adjusting mechanism (30) capable of adjusting the suction volume by switching the suction closed position between the first position and the second position where the suction volume is smaller than the first position.
  • the mechanism (30) is premised on a compressor including a plunger (33) that can be switched between a closed position where the suction closed position is a first position and an open position where the suction closed position is a second position.
  • the compressor includes an oil passage (51) communicating with an oil reservoir (18, 50) formed in the casing (10) and a suction side space (25s) of the compression chamber (25a, 25b).
  • the plunger (33) is disposed in the middle of the oil passage (51), and closes the oil passage (51) in the closed position to close the oil reservoir (18, 50) and the compression chamber (25a, 25b) is cut off from the suction side space (25s), and the oil passage (51) is opened at the open position so that the oil sump (18, 50) and the suction side space (25s) of the compression chamber (25a, 25b) And a switching portion (65) that communicates with the other.
  • the compression mechanism (20) includes a fixed scroll (21) and a movable scroll (22) that meshes with the fixed scroll (21) and compresses the working fluid.
  • the scroll compression mechanism (20) is provided.
  • the oil passage (51) is blocked, so that the oil is stored in the oil reservoir (18 , 50) is not supplied to the suction side space (25s) of the compression chamber (25a, 25b), while the plunger (33) whose suction volume is reduced when the suction closed position is in the second position is in the open position.
  • the oil passage (51) is opened, so that oil is supplied from the oil reservoir (18, 50) to the suction side space (25s) of the compression chamber (25a, 25b) by the action of negative pressure.
  • the oil passage (51) is an oil sump formed in a space (crank chamber (23e)) in the housing (23) of the compression mechanism (20). One end communicates with (18, 50), and the other end communicates with the suction side space (25s) of the compression mechanism (20).
  • the plunger (33) when the suction volume is reduced when the suction closed position is the second position, the plunger (33) is in the open position and the oil passage (51) is opened, so that the compression mechanism (20 ) Oil is supplied to the suction side space (25s) of the compression chamber (25a, 25b) from the oil sump (18, 50) formed in the space (crank chamber (23e)) .
  • the oil passage (51) includes a movable scroll side oil passage (55) and a fixed scroll side oil passage (communication to the movable scroll side oil passage (55)). 52), and the movable scroll side oil passage (55) is connected to the oil reservoir (18, 50) at the end opposite to the communicating end with the fixed scroll side oil passage (52).
  • the oil passage (52) is characterized in that the end opposite to the communication end with the movable scroll (22) side communication passage communicates with the suction side space (25s) of the compression mechanism (20).
  • the plunger (33) when the suction volume is reduced when the suction closed position is the second position, the plunger (33) is in the open position, and the movable scroll side oil passage (55) and the fixed scroll side oil passage ( 52) is opened, so that oil is supplied from the oil reservoir (18, 50) to the suction side space (25s) of the compression chamber (25a, 25b) by the action of negative pressure.
  • the oil passage (51) has one end communicating with an oil reservoir (18, 50) formed in the casing (10), and the compression mechanism ( It is characterized by having an oil supply pipe (56) whose other end communicates with the suction side space (25s) of 20).
  • the plunger (33) when the suction closed position is the second position and the suction volume is small, the plunger (33) is in the open position and the oil passage (51) is opened, so the casing (10 ) Oil is supplied to the suction side space (25s) of the compression chambers (25a, 25b) from the oil reservoir (18, 50) formed in) by the action of negative pressure.
  • one end of the oil passage (51) communicates with an oil supply pump (43a) provided on a drive shaft of the compression mechanism (20). It has an oil supply pipe (57) whose other end communicates with the suction side space (25s) of (20).
  • the plunger (33) when the suction closed position is the second position and the suction volume is small, the plunger (33) is in the open position and the oil passage (51) is opened. Oil is supplied from 43a) to the suction side space (25s) of the compression chamber (25a, 25b).
  • the oil passage (51) passes through the inside of the fixed scroll (21) and the plunger (33) is compressed. It has a fixed scroll passage (53) communicating with the suction side space (25s) of the mechanism (20).
  • the oil passage (51) is formed outside the fixed scroll (21) in the casing (10). It has a fixed scroll outer passage (58) communicating with the plunger (33) and the suction side space (25s) of the compression mechanism (20) through the space.
  • the plunger (33) when the suction volume is reduced when the suction closed position is the second position, the plunger (33) is in the open position and the oil passage (51) is opened, so that the casing (10 The oil is supplied to the suction side space (25s) of the compression chamber (25a, 25b) through the space formed outside the fixed scroll (21).
  • the suction volume adjustment mechanism (30) is moved from the plunger (33) in the second position to the casing (10).
  • the oil passage (51) has an outflow passage (60) for discharging the working fluid to a space formed outside the fixed scroll (21), and one end of the oil passage (51) communicates with the plunger (33).
  • An oil merging passage (53a) whose other end communicates with the passage (60) is provided.
  • the plunger (33) when the suction volume is reduced when the suction closed position is the second position, the plunger (33) is in the open position, and the oil merge passage (53a) communicates with the outflow passage (60). Since the oil passage (51) provided with is opened, the suction side space (25s) of the compression chamber (25a, 25b) passes through the space formed outside the fixed scroll (21) in the casing (10). ) Is supplied.
  • the plunger (33) is a cylindrical valve body, and the oil passage ( 51), and has a circumferential groove (33d) that is disengaged from the oil passage (51) at the first position.
  • the eleventh aspect of the present disclosure is characterized in that, in the tenth aspect, the plunger (33) includes seal members (33e) on both sides of the circumferential groove (33d) on the outer peripheral surface.
  • the plunger (33) when the capacity control is not performed with the suction closed position being the first position, the plunger (33) is in the closed position and the oil passage (51) is blocked.
  • This operating state is a high operating capacity state, and the refrigerant flow rate inside the compressor increases, so that the amount of oil sucked into the compression chambers (25a, 25b) becomes sufficient, and the compression passage ( Since excess oil is not supplied to 25a and 25b), oil rise is suppressed and performance is maintained.
  • the plunger (33) when the capacity control is not performed when the suction closed position is the first position, the plunger (33) is closed and the oil passage (51) is closed. Blocked.
  • This operating state is a high operating capacity state, and the refrigerant flow rate inside the compressor increases, so that the amount of oil sucked into the compression chambers (25a, 25b) becomes sufficient, and the compression passage ( Since excess oil is not supplied to 25a and 25b), oil rise is suppressed and performance is maintained.
  • one end communicates with the oil sump (18, 50) formed in the space (crank chamber (23e)) in the housing of the compression mechanism (20), and the compression mechanism (20
  • the oil passage (51) with the other end communicating with the suction side space (25s) can be used to supply oil to the compression chambers (25a, 25b) when adjusting the suction volume. Therefore, the performance of the scroll compressor can be improved with a simple structure.
  • the movable scroll side oil passage (55) and the fixed scroll side oil passage (52) are configured such that one end communicates with the oil reservoir (18, 50) and the compression mechanism (
  • the oil passage (51) whose other end communicates with the suction side space (25s) of 20) can be used to supply oil to the compression chambers (25a, 25b) when adjusting the suction volume. Therefore, it is possible to realize the effect of suppressing the decrease in the performance of the scroll compressor and at the same time suppressing the oil rise with a simple structure.
  • one end communicates with the oil sump (18, 50) formed in the casing (10) of the compressor, and the suction side space (25s) of the compression mechanism (20).
  • Oil can be supplied to the compression chambers (25a, 25b) when adjusting the suction volume using the oil passage (51) with which the other end communicates. Therefore, the performance of the scroll compressor can be improved with a simple structure.
  • the oil passage (51) having one end communicating with the oil supply pump (43a) and the other end communicating with the suction side space (25s) of the compression mechanism (20) is used. Oil can be supplied to the compression chambers (25a, 25b) when adjusting the suction volume. Therefore, the performance of the scroll compressor can be improved with a simple structure.
  • a fixed scroll inner passage (communication path) that communicates with the plunger (33) and the suction side space (25s) of the compression mechanism (20) through the fixed scroll (21).
  • the oil passage (51) having 52) can be used to supply oil to the compression chambers (25a, 25b) when adjusting the suction volume. Therefore, the performance of the scroll compressor can be improved with a simple structure.
  • the plunger (33) and the suction side space of the compression mechanism (20) pass through the space formed outside the fixed scroll (21) in the casing (10). Oil can be supplied to the compression chambers (25a, 25b) when adjusting the suction volume using the oil passage (51) having the fixed scroll outer passage (58) communicating with (25s). Therefore, the performance of the scroll compressor can be improved with a simple structure.
  • the plunger (33) communicates with the outflow passage (60) for discharging the working fluid to the space formed outside the fixed scroll (21) in the casing (10).
  • Oil can be supplied to the compression chambers (25a, 25b) using the oil passage (51) provided with the oil joining passage (53a) to adjust the suction volume. Therefore, the performance of the scroll compressor can be improved with a simple structure.
  • the suction volume adjusting mechanism (30) can be realized with a simple structure using the plunger (33) which is a cylindrical valve body.
  • the plunger Oil leakage can be prevented by providing the seal member (33e) on (33).
  • FIG. 1 is a longitudinal sectional view of a compressor according to the first embodiment.
  • FIG. 2 is a diagram showing the shapes of the fixed scroll and the movable scroll in the section taken along the line II-II in FIG.
  • FIG. 3 is an enlarged cross-sectional view of the compression mechanism.
  • FIG. 4 is a cross-sectional structure diagram of the opening / closing mechanism.
  • FIG. 5 is an enlarged front view of the plunger.
  • FIG. 6 is a plan view showing the shape of the lateral passage of the oil passage.
  • FIG. 7 is a first operation state diagram of the compression mechanism.
  • FIG. 8 is a second operation state diagram of the compression mechanism.
  • FIG. 9 is a third operation state diagram of the compression mechanism.
  • FIG. 10 is a fourth operation state diagram of the compression mechanism.
  • FIG. 1 is a longitudinal sectional view of a compressor according to the first embodiment.
  • FIG. 2 is a diagram showing the shapes of the fixed scroll and the movable scroll in the section taken along the
  • FIG. 11 is a fifth operation state diagram of the compression mechanism.
  • FIG. 12 is a sixth operation state diagram of the compression mechanism.
  • FIG. 13 is a cross-sectional structure diagram of a compression mechanism according to a modification of the first embodiment.
  • FIG. 14 is a plan view of the fixed scroll of the compression mechanism of FIG.
  • FIG. 15 is a longitudinal sectional view of a compressor according to the second embodiment.
  • 16 is an enlarged cross-sectional view of the compression mechanism of FIG.
  • FIG. 17 is a longitudinal sectional view of a compressor according to the third embodiment.
  • FIG. 18 is a longitudinal sectional view of a compressor according to the fourth embodiment.
  • FIG. 19 is a plan view of the compression mechanism according to the fifth embodiment.
  • FIG. 20 is a cross-sectional view showing a first state of the plunger of the compression mechanism of FIG.
  • FIG. 21 is a cross-sectional view showing a second state of the plunger of the compression mechanism of FIG.
  • FIG. 22 is a plan view of a compression mechanism according to the sixth embodiment.
  • FIG. 23 is a cross-sectional view showing the structure of the plunger of the compression mechanism of FIG.
  • FIG. 24 is an enlarged view showing a modified example of the plunger.
  • Embodiment 1 of the Invention A first embodiment of the present invention will be described.
  • the scroll compressor of the present embodiment is provided, for example, in a refrigerant circuit of an air conditioner that performs a vapor compression refrigeration cycle, and compresses low-pressure refrigerant sucked from an evaporator and discharges it to a condenser.
  • the scroll compressor (1) is configured as a so-called totally sealed type.
  • the scroll compressor (1) includes a casing (10) formed in a vertically long cylindrical sealed container shape.
  • the casing (10) includes a body (11) which is a vertically long cylindrical member, an upper end plate (12) fixed to the upper end of the body (11), and a lower part fixed to the lower end of the body (11). End plate (13).
  • a compression mechanism (20) for compressing the refrigerant and an electric motor (45) for driving the compression mechanism (20) are accommodated.
  • the electric motor (45) is disposed below the compression mechanism (20), and is connected to the compression mechanism (20) via a drive shaft (40) that is a rotating shaft.
  • the electric motor (45) uses a brushless DC motor capable of variably adjusting the rotation speed by inverter control.
  • the discharge pipe (15) is attached to the upper end plate (12) which is the top of the casing (10).
  • the discharge pipe (15) has a terminal end (lower end in the figure) connected to the compression mechanism (20).
  • a suction pipe (14) is attached through the body (11) of the casing (10).
  • the suction pipe (14) has an end (right end in the figure) opened between the compression mechanism (20) and the electric motor (45) in the casing (10).
  • the drive shaft (40) is disposed on the vertical center line of the casing (10).
  • the drive shaft (40) is a crankshaft including a main shaft portion (41) and an eccentric portion (42).
  • the eccentric part (42) is formed with a smaller diameter than the main shaft part (41), and is formed on the upper end surface of the main shaft part (41).
  • this eccentric part (42) is eccentric by the predetermined dimension with respect to the axial center of a main-shaft part (41), and comprises the eccentric pin.
  • 1 and 2 show a state in which the main shaft portion (41) and the eccentric portion (42) are located concentrically, this is illustrated in FIGS. 1 and 2 with respect to the main shaft portion (41). This is because the center of the shaft and the center of the eccentric portion (42) are cross-sectional views as viewed from a direction in a straight line. For example, when viewing FIGS. The part (42) is in a state shifted from the center.
  • a lower bearing member (48) is fixed near its lower end.
  • the lower bearing member (48) rotatably supports the lower end portion of the main shaft portion (41) of the drive shaft (40) via the sliding bearing (48a).
  • an oil supply passage (44) extending in the vertical direction is formed inside the drive shaft (40).
  • An oil supply pump (43) is provided at the lower end of the main shaft (41). The oil supply pump (43) sucks refrigeration oil from the bottom of the casing (10), and the refrigeration oil passes through the oil supply passage (44) of the drive shaft (40) to drive the sliding part and the drive of the compression mechanism (20). Supplied to the bearing part of the shaft (40).
  • the electric motor (45) includes a stator (46) and a rotor (47).
  • the stator (46) is fixed to the body (11) of the casing (10).
  • the rotor (47) is connected to the main shaft portion (41) of the drive shaft (40) and rotationally drives the drive shaft (40).
  • the compression mechanism (20) includes a fixed scroll (21) and a movable scroll (22), and also includes a housing (23) that fixedly supports the fixed scroll (21).
  • the fixed scroll (21) and the movable scroll (22) include spiral wraps (21b, 22b) that mesh with each other on the end plate (21a, 22a).
  • the compression mechanism (20) is configured such that the movable scroll (22) performs an eccentric rotational motion with respect to the fixed scroll (21).
  • the housing (23) is composed of a main body part (23a) and a bearing part (23b).
  • the main body portion (23a) and the bearing portion (23b) are formed continuously in the vertical direction, and the main body portion (23a) is fitted and joined to the body portion (11) of the casing (10).
  • the bearing portion (23b) is formed with a smaller diameter than the main body portion (23a), and protrudes downward from the main body portion (23a).
  • the bearing portion (23b) rotatably supports the main shaft portion (41) of the drive shaft (40) via the sliding bearing (23c).
  • the fixed scroll (21) includes a fixed side end plate (21a), a fixed side wrap (21b), and an edge (21c).
  • the fixed side end plate (21a) is formed in a substantially disc shape.
  • the fixed side wrap (21b) is erected near the central portion of the lower surface of the fixed side end plate (21a), and is integrally formed with the fixed side end plate (21a).
  • the fixed side wrap (21b) is formed in a spiral wall shape having a constant height.
  • the edge portion (21c) is a wall-shaped portion extending downward from the outer peripheral edge portion of the fixed side end plate (21a), and the lower surface overlaps the upper surface of the main body portion (23a) of the housing (23). It is fixed to the housing (23).
  • the movable scroll (22) includes a movable side end plate (22a), a movable side wrap (22b), and a boss portion (22c).
  • the movable side end plate (22a) is formed in a substantially disc shape.
  • the movable side wrap (22b) is erected on the upper surface of the movable side end plate (22a), and is integrally formed with the movable side end plate (22a).
  • the movable wrap (22b) is formed in a spiral wall shape having a constant height, and is configured to mesh with the fixed wrap (21b) of the fixed scroll (21).
  • the boss portion (22c) extends downward from the lower surface of the movable side end plate (22a) and is integrally formed with the movable side end plate (22a).
  • the eccentric part (42) of the drive shaft (40) is inserted into the boss part (22c) via a sliding bearing (22d). For this reason, when the drive shaft (40) rotates, the movable scroll (22) revolves around the axis of the main shaft portion (41).
  • the revolution radius of the movable scroll (22) is the same as the eccentric amount of the eccentric part (42), that is, the dimension from the axis of the main shaft part (41) to the axis of the eccentric part (42).
  • the movable side end plate (22a) is located in a first recess (23d) provided at the upper end of the housing (23), and the boss portion (22c) is provided in the main body (23a) of the housing (23).
  • the second recess (crank chamber) (23e) is located.
  • an Oldham coupling for preventing the rotation of the movable scroll (22) is disposed between the movable side end plate (22a) and the housing (23).
  • the first recess (23d) is formed to have a size that allows the eccentric rotational motion of the movable side end plate (22a), and the second recess (23e) has a size that allows the eccentric rotational motion of the boss portion (22c). (In the drawing, the magnitude relationship between these parts is not considered).
  • FIG. 2 is a diagram showing the shapes of the fixed scroll and the movable scroll in the section taken along the line II-II in FIG.
  • a so-called asymmetric spiral structure is adopted, and the number of spirals (the number of spirals between the fixed side wrap (21b) and the movable side wrap (22b) ( The length of the spiral is different. Specifically, the number of spirals of the fixed side wrap (21b) is longer than that of the movable side wrap (22b) by about 1/2 turn.
  • the outer circumferential surface is not formed on the outermost winding of the fixed side wrap (21b), and the fixed side wrap (21b) is connected to the edge (21c) of the fixed scroll (21) within that range. Yes. And, the winding end of the fixed side wrap (21b) is terminated in such a manner that the outer peripheral side end and the inner peripheral side end located where it is wound longer by one turn face each other, The outer peripheral side end (winding end) of the movable wrap (22b) is located in the vicinity thereof.
  • the compression mechanism (20) includes a plurality of compression chambers formed by partitioning the fixed side wrap (21b) and the movable side wrap (22b) between the fixed side end plate (21a) and the movable side end plate (22a). 25a, 25b).
  • the plurality of compression chambers (25a, 25b) includes a first compression chamber (25a) configured between an inner peripheral surface of the fixed side wrap (21b) and an outer peripheral surface of the movable side wrap (22b), and a fixed side It is comprised from the 2nd compression chamber (25b) comprised between the outer peripheral surface of a lap
  • the maximum volume of the first compression chamber (25a) is the maximum of the second compression chamber (25b). Greater than volume.
  • a suction port (29) is formed on the outer peripheral side of the fixed scroll (21).
  • the suction port (29) opens into a space above the compression mechanism (20).
  • the suction port (29) intermittently communicates with each of the first compression chamber (25a) and the second compression chamber (25b) as the movable scroll (22) revolves.
  • a concave portion (21g) is formed at the upper end of the fixed side end plate (21a), and a discharge cover (27) covering the concave portion (21g) is attached to the upper surface of the fixed side end plate (21a).
  • a space in which the recessed portion (21g) is covered with the discharge cover (27) is configured as a discharge chamber (28) communicating with the discharge pipe (15).
  • a discharge port (26) communicating with the discharge chamber (28) is formed at the lower center of the fixed side end plate (21a).
  • the discharge port (26) intermittently communicates with each of the first compression chamber (25a) and the second compression chamber (25b) as the movable scroll (22) revolves.
  • the inside of the casing (10) is a low-pressure space where both the space (16) below the housing (23) and the space (17) above are filled with low-pressure refrigerant.
  • the suction volume is adjusted by adjusting the suction closing position of the compression chamber (25a, 25b) in the suction stroke of the compression mechanism (20).
  • An intake volume adjusting mechanism (30) capable of adjusting the intake is provided.
  • the suction volume adjusting mechanism (30) can adjust the suction closing position (position where the suction stroke is completed and the compression stroke is started) in both the first compression chamber (25a) and the second compression chamber (25b). As shown in FIG. 2, it is provided only at one location in the outer circumferential side of the spiral.
  • the suction volume adjusting mechanism (30) switches the suction closed position of the compression chamber (25a, 25b) in the suction stroke between the first position and the second position where the suction volume is smaller than the first position. It is a mechanism that enables adjustment.
  • the suction volume adjusting mechanism (30) includes an opening / closing mechanism (31) that can switch the first compression chamber (25a) and the second compression chamber (25b) between a communication state and a cutoff state.
  • the plunger (33) is a cylindrical valve body, and is located on the outer peripheral surface of the oil passage (44) at the second position and at the first position. It has a circumferential groove (33d) that deviates from the path of the passage (44).
  • the communication path (32) is composed of a stepped hole (32) formed in the fixed side end plate (21a). As shown in FIG. 2, the stepped hole (32) is formed at a position obliquely below the left side of the center of the spiral in the drawing within a range of the outer periphery of the spiral. As shown in FIG. 3, the stepped hole (32) is composed of a large diameter portion (32a) opened on the upper surface of the fixed side end plate (21a) and a small diameter portion (32b) having a smaller diameter. The small-diameter portion (32b) constitutes the communication path (32). The stepped hole (32) is formed such that the small diameter portion (32b) is positioned between the teeth of the fixed side wrap (21b). The small diameter portion (32b) is a circular hole having a diameter larger than the thickness of the teeth of the movable side wrap (22b).
  • the stepped hole (32) is loaded with a compression coil spring (biasing member) (35) and the plunger (33) (see FIG. 5) for opening and closing the small diameter portion (32b) at the tip.
  • the plunger (33) includes a plug portion (33a) having a size to be fitted to the small diameter portion (32b) and a larger diameter than the plug portion (33a) and the compression coil spring (35).
  • the spring receiving part (33b) to which the is attached and the seal part (33c) larger in diameter than the spring receiving part (33b) are integrally formed so as to be continuous from the tip (lower end in the figure) side Is.
  • the circumferential groove (33d) is formed in the seal portion (33c).
  • the opening / closing drive mechanism (34) applies a low pressure to the compression coil spring (35) that urges the plunger (33) toward the open position and the plunger (33).
  • a switching valve (switching member) (36) for switching a state in which a high pressure is applied against the urging force of the compression coil spring (35) to the plunger (33).
  • the suction volume adjusting mechanism (30) opening / closing mechanism (31)
  • the plunger (33) When the plunger (33) is operated in the closed position, the first compression chamber (25a) and the second compression chamber are operated. Since (25b) is in a cut-off state, a normal operation is performed in which the refrigerant is compressed with a suction volume as designed.
  • the operation when the operation is performed with the plunger (33) in the open position, the first compression chamber (25a) and the second compression chamber (25b) are in communication with each other.
  • the adjustment operation compresses the refrigerant.
  • the rotational speed of the electric motor (45) is made faster than that during normal operation.
  • an oil sump (50) is formed at the bottom of the second recess (crank chamber) (23e) so that the oil after lubricating the bearing portion of the drive shaft (41) and the like is retained. It has become.
  • an oil passage (51) communicating with the oil reservoir (50) and the suction side space (25s) of the compression chamber (25a, 25b) is formed.
  • the oil passage (51) has one end communicating with an oil sump (50) formed in a crank chamber (23e) in the housing (23) of the compression mechanism (20), and the suction side of the compression mechanism (20). The other end communicates with the space (25s).
  • the oil passage (51) includes a vertical passage (52) on the oil reservoir side and a lateral passage (arc-shaped) on the suction side space (25s) side of the compression mechanism (20). Passage) (53).
  • the plunger (33) is disposed in the middle of the lateral passage (53) of the oil passage (51).
  • the plunger (33) closes the oil passage (51) in the closed position to shut off the oil reservoir (50) and the suction side space (25s) of the compression chambers (25a, 25b).
  • the switching part (55) is constituted by a circumferential groove (33d) formed in the seal part (33c). That is, in the open position of FIG.
  • the oil passage (51) communicates with the oil reservoir (50) and the suction side space (25s) of the compression chamber (25a, 25b) via the circumferential groove (33d).
  • the oil passage (51) is blocked by the seal portion (33c) in the closed position (not shown), the oil reservoir (50) and the suction side space (25s) of the compression chambers (25a, 25b) There is no communication, and no oil is supplied from the oil reservoir (50) to the suction side space (25s) of the compression chamber (25a, 25b).
  • the volume of the compression chambers (25a, 25b) repeats increasing and decreasing periodically with the revolving motion of the movable scroll (22).
  • the compression chambers (25a, 25b) when the volume of the portion communicating with the suction port (29) increases, the refrigerant in the refrigerant circuit flows from the suction pipe (14) to the suction path (not shown) and the suction port (29 )
  • the compression chamber (25a, 25b) the refrigerant is compressed when the volume of the part where the suction side is closed is reduced, and then discharged from the discharge port (26) to the discharge chamber (28)
  • the refrigerant in the discharge chamber (28) is supplied from the discharge pipe (15) to the condenser of the refrigerant circuit.
  • FIGS. 7 to 12 are sectional views showing the operation state of the compression mechanism (20) divided into six stages.
  • the movable scroll (22) revolves at a predetermined angular interval in the clockwise direction of the drawing. It shows how it is.
  • the winding end of the movable wrap (22b) is located between the teeth of the fixed wrap (21b), and the outermost first compression chamber is located.
  • Both the compression chambers (25a-0, 25b-0) communicate with the suction port (29) with both the (25a-0) and the second compression chamber (25b-0) open to the low pressure side.
  • the outer peripheral surface of the movable wrap (22b) and the inner peripheral surface of the fixed wrap (21b) are substantially in contact at a point P1 on the center line Y in the figure.
  • contact means a state in which there is a micron-order gap but an oil film is formed so that leakage of the refrigerant does not cause a problem.
  • the contact position (seal point) P1 is on the inner peripheral side.
  • the part (25a-1) of (the spiral start side) is already in the compression stroke.
  • the volume of the second compression chamber (25b-1) is reduced and the compression stroke of the refrigerant starts, and the outermost first compression In the chamber (25a-0), the volume further expands and the refrigerant suction process proceeds.
  • the compression stroke in the second compression chamber (25b-1) and the suction stroke in the outermost first compression chamber (25a-0) are further advanced.
  • a new second compression chamber (25b-0) is formed at the end of the vortex with respect to the second compression chamber (25b-1) already compressed. The inhalation stroke has started.
  • the suction stroke in the second outermost compression chamber (25b-0) further proceeds, while the outer peripheral surface of the end of winding of the movable wrap (22b) is fixed wrap.
  • the inner peripheral surface of (21b) is contacted, and the contact position (seal point) P1 is the suction closed position of the first compression chamber (25a-1).
  • the compression stroke in the first compression chamber (25a-1) formed in the state of FIG. 11 proceeds and the outermost second compression chamber (25b-0)
  • the inhalation process proceeds.
  • a new first compression chamber (25a-0) is provided on the outer peripheral side (the end of the spiral) of the first compression chamber (25a-1) during compression. It is formed.
  • FIGS. 7 to 12 Thereafter, the operations of FIGS. 7 to 12 are repeated, and the first compression chamber (25a-1) and the second compression chamber (25b-1) in the middle of compression move toward the inner peripheral side of the spiral while reducing the volume.
  • the first compression chamber (25a-2) and the second compression chamber (25b-2) immediately before discharge are changed.
  • the first compression chamber (25a-2) and the second compression chamber (25b-2) communicate with the discharge port (26) when the volume is minimized by moving to the innermost side, It is discharged from the compression mechanism (20).
  • the plunger (33) is closed, the oil passage (51) is shut off, and the oil reservoir (50) and the suction side space (25s) of the compression chamber (25a, 25b) Does not communicate. Therefore, oil is not supplied from the oil reservoir (50) to the compression chamber (25a, 25b) in response to the fact that the amount of oil discharged is not large during high capacity normal operation. There will be no excess.
  • the opening / closing mechanism (31), which is the suction volume adjustment mechanism (30), has the plunger (33) in the open position and opens the small diameter portion (32b), which is the communication path (32).
  • the first compression chamber (25a) and the second compression chamber (25b) are in a communication state (a state in which communication is possible).
  • both compressions are performed in a state where both the outermost first compression chamber (25a-0) and the second compression chamber (25b-0) are opened to the low pressure side.
  • the point that the chamber (25a-0, 25b-0) communicates with the suction port (29) is the same as in normal operation.
  • the outer peripheral surface of the movable wrap (22b) and the inner peripheral surface of the fixed wrap (21b) are in contact with each other at a point P1 on the center line Y in the figure, and the inner periphery is more than this point (seal point) P1
  • the first compression chamber (25a-1) on the side (the spiral start side) has already been closed
  • the first compression chamber (25a-1) is connected via the communication path (32), It communicates with the second outermost compression chamber (25b-0) in the middle of the suction stroke. Therefore, the first compression chamber (25a-1) is still in a state before the suction closed position, and is in the middle of the suction stroke, like the second compression chamber (25b).
  • the contact point P1 between the inner peripheral surface of the fixed side wrap (21b) and the outer peripheral surface of the movable side wrap (22b) passes through the communication path (32) of the opening / closing mechanism (31). It is displaced to the position immediately after. Therefore, the contact position (seal point) P1 at this time becomes the suction closed position of the first compression chamber (25a-1).
  • the outermost second compression chamber (25b-1) closed during normal operation in this state is formed on the spiral outer periphery side of the first compression chamber (25a-1) that has entered the compression stroke.
  • the outermost first compression chamber (25a-0) communicates with the communication path (32). Since the outermost first compression chamber (25a-0) is in the middle of the suction stroke, the second compression chamber (25b) is before the suction closing.
  • This state is the same in the third operation state shown in FIG. 9 and the fourth operation state shown in FIG. 10, and the second compression chamber (25b-1) is in the state before the intake closing and is still on the winding end side. Seal points are not formed. At this time, the outermost first compression chamber (25a-0) is also in the middle of the suction stroke. In the fourth operation state shown in FIG. 10, a new second compression chamber (25b-0) is starting to be formed on the spiral outer peripheral side of the second compression chamber (25b-1).
  • the contact point P2 between the outer peripheral surface of the fixed side wrap (21b) and the inner peripheral surface of the movable side wrap (22b) passes through the communication path (32) of the opening / closing mechanism (31). pass. Therefore, the contact point P2 at this time becomes the seal point of the second compression chamber (25b-1), and the compression stroke in the second compression chamber (25b-1) is started.
  • the first outermost compression chamber (25a-1) was closed during normal operation, but the outermost first compression chamber (25a-1) was closed during the adjustment operation. Since it communicates with the low pressure side through the second compression chamber (25b-0), it is still in the middle of the suction stroke. This is the same in the sixth operating state of FIG. 12, and the same is true when returning to the first operating state of FIG.
  • the suction volumes of both the first compression chamber (25a) and the second compression chamber (25b) are smaller than those during normal operation. Become. As a result, the compression ratio becomes smaller than that during normal operation, and the discharge pressure decreases if the suction pressure is the same as during normal operation.
  • the rotation speed of the electric motor (45) is set to be higher than that in the normal operation, so that the capacity of the scroll compressor (1) is kept equal to that in the normal operation. be able to.
  • the plunger (33) is opened, the oil passage (51) is opened, and the oil reservoir (50) and the suction side space (25s) of the compression chamber (25a, 25b) Communicate. Therefore, during the low capacity adjustment operation, the capacity is adjusted to the same capacity as when no adjustment operation is performed, so the engine rotates at a higher speed than when adjustment is not performed, so oil supply to the compression chamber (25a, 25b) In addition to the increase in amount, oil is supplied from the oil reservoir (18, 50) to the compression chamber (25a, 25b), so that supply of oil to the compression chamber is not insufficient.
  • a sufficient amount of oil is not supplied to the compression chambers (25a, 25b) only during the adjustment operation (at the time of low capacity operation), and a sufficient oil film is not formed on the compression mechanism portion, so that performance is improved.
  • the oil passage (51) is opened and the oil sump (50) communicates with the suction side space (25s) of the compression chamber (25a, 25b), the compression chamber (25a, 25b) is sufficiently connected. The correct amount of oil is supplied. Therefore, the performance during the adjustment operation can be improved.
  • the oil passage (51) is configured such that the whole passage passes through the inside of the fixed scroll (21), and the plunger (33) and the suction side of the compression mechanism (20). You may comprise by the channel
  • the suction pipe (14) is connected to the suction port (29), and the lateral passage (53) of the oil passage (51) communicates with the suction port (29). With this configuration, the oil in the oil sump (50) joins the suction refrigerant and is supplied to the compression chamber (25).
  • Embodiment 2 of the Invention will be described.
  • the oil passage (51) is communicated with the movable scroll side oil passage (55) and the movable scroll side oil passage (55).
  • (Fixed scroll passage) (52) The movable scroll side oil passage (55) communicates with the oil reservoir (18) at the end opposite to the communicating end with the fixed scroll side oil passage (51).
  • the movable scroll side oil passage (55) has an oil supply passage (44) whose end opposite to the communicating end with the fixed scroll side oil passage (52) is formed inside the drive shaft (41).
  • the fixed scroll side oil passage (52) communicates with the suction side space (25s) of the compression mechanism (20) at the end opposite to the communicating end with the movable scroll side communication passage (55).
  • the oil passage (51) is opened as shown in FIG. 16, and the oil reservoir (18) communicates with the suction side space (25s) of the compression chamber (25a, 25b).
  • the oil reservoir (18) communicates with the suction side space (25s) of the compression chamber (25a, 25b).
  • Embodiment 3 of the Invention will be described.
  • the oil passage (51) has one end communicating with an oil reservoir (18) formed in the casing (10), and the suction of the compression mechanism (20). The other end communicates with the side space (25s).
  • the oil passage (51) has an oil supply pipe (56) extending upward from an oil reservoir (18) in the casing (10) and communicating with the plunger (33). ) Communicates with the lateral passage (53).
  • the portion between the plunger (33) and the suction side of the compression chamber (25) (the transverse passage (53)) is configured in the same manner as the modification of the first embodiment and the second embodiment. Has been.
  • the oil passage (51) is opened as shown in FIG. 17, and the oil reservoir (18) communicates with the suction side space (25s) of the compression chamber (25a, 25b).
  • the oil reservoir (18) communicates with the suction side space (25s) of the compression chamber (25a, 25b).
  • Embodiment 4 of the Invention will be described.
  • the oil passage (51) has one end communicating with an oil supply pump (43a) provided on the drive shaft (41), and the suction of the compression mechanism (20). The other end communicates with the side space (25s).
  • the oil passage (51) has an oil supply pipe (57) extending upward from an oil supply pump (43a) provided at the lower end of the drive shaft (41) and communicating with the plunger (33).
  • the oil supply pipe (56) communicates with the lateral passage (53).
  • the portion between the plunger (33) and the suction side of the compression chamber (25) (the transverse passage (53)) is configured in the same manner as the modification of the first embodiment and the second embodiment. Has been.
  • the oil passage (51) is opened as shown in FIG. 18, and the oil reservoir (18) communicates with the suction side space (25s) of the compression chamber (25a, 25b).
  • the oil reservoir (18) communicates with the suction side space (25s) of the compression chamber (25a, 25b).
  • Embodiment 5 of the Invention will be described.
  • the oil passage (51) passes through a space (17) formed outside the fixed scroll (21) in the casing (10). It has a fixed scroll outer passage (58) communicating with the plunger (33) and the suction side space (25s) of the compression mechanism (20). Further, in the fifth embodiment, the fixed scroll (21) is formed with a gas outflow path (60) through which the refrigerant gas flows out from the compression chamber (25a, 25b) into the space (17).
  • the oil passage (51) is opened as shown in FIG. 20, and the oil reservoir (18) communicates with the suction side space (25s) of the compression chamber (25a, 25b).
  • the oil reservoir (18) communicates with the suction side space (25s) of the compression chamber (25a, 25b).
  • Embodiment 6 of the Invention is an example in which the structure of the oil passage (51) is different from that of the fifth embodiment. Specifically, as shown in FIGS. 22 and 23, the oil passage (51) passes through a space (17) formed outside the fixed scroll (21) in the casing (10). There is a fixed scroll outer passage (58) communicating with the plunger (33) and the suction side space (25s) of the compression mechanism (20). Further, in the fifth embodiment, the fixed scroll (21) is formed with a gas outflow path (60) through which the refrigerant gas flows out from the compression chamber (25a, 25b) into the space (17). In the sixth embodiment, the end portion of the lateral passage (53) is closed, and the lateral passage (53) and the gas outflow passage (60) are communicated with each other through the oil merge passage (53a).
  • the oil passage (51) is opened as shown in FIG. 23, and the oil reservoir (18) communicates with the suction side space (25s) of the compression chamber (25a, 25b).
  • the oil reservoir (18) communicates with the suction side space (25s) of the compression chamber (25a, 25b).
  • the present invention may be applied to a scroll compressor having a target spiral structure.
  • the suction volume adjusting mechanism (30) may be provided with a structure similar to that of the above-described embodiment one by one at a position symmetrical with respect to the center of the spiral.
  • the suction closing position is adjusted for each of the first compression chamber (25a) and the second compression chamber (25b) that exist symmetrically with respect to the spiral center. Since the oil flow can be controlled at the same time, the same effect as the above embodiment can be obtained.
  • the present invention is not limited to the scroll compressor, and may be applied to, for example, a rolling piston type compressor or a swing piston type compressor. Also good.
  • seal members (33e) may be provided on both sides of the circumferential groove (33d) on the outer peripheral surface of the plunger (33).
  • the seal portion (33c) of the plunger (33) is formed with seal mounting grooves (33f) along the circumferential direction on both sides of the circumferential groove (33d). ) Is attached with a ring-shaped sealing member (33e).
  • the present invention is useful for a technique for eliminating insufficient lubrication of a compression mechanism in a compressor having a suction bypass mechanism that adjusts the suction volume by changing the suction closing position.

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

Abstract

Selon la présente invention, un passage d'huile (51) est formé de façon à communiquer avec un réservoir d'huile (50) et un espace côté aspiration de chambre de compression (25s) formé à l'intérieur d'un boîtier (10), et un piston (33) d'un mécanisme de réglage de volume d'aspiration (30) est disposé à mi-chemin le long du passage d'huile (51), et comporte une unité de commutation (65) qui ferme le passage d'huile (51) et déconnecte le réservoir d'huile (50) et l'espace côté aspiration (25s) quand la position de commutation de fermeture d'aspiration est dans une première position, et qui ouvre le passage d'huile (51) et permet au réservoir d'huile (50) et à l'espace côté aspiration (25s) de communiquer quand la position de commutation de fermeture d'aspiration est une seconde position pour laquelle le volume d'aspiration est inférieur à celui de la première position. Par conséquent, une diminution des performances du compresseur peut être éliminée, et l'écoulement de sortie d'huile peut être éliminé.
PCT/JP2016/004676 2015-11-11 2016-10-24 Compresseur WO2017081845A1 (fr)

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US15/765,235 US20180298900A1 (en) 2015-11-11 2016-10-24 Compressor
EP16863812.0A EP3339647A1 (fr) 2015-11-11 2016-10-24 Compresseur
CN201680058627.XA CN108138779A (zh) 2015-11-11 2016-10-24 压缩机

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JP2015220912A JP6206468B2 (ja) 2015-11-11 2015-11-11 スクロール圧縮機

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EP3992461B1 (fr) * 2019-08-30 2023-10-11 Daikin Industries, Ltd. Compresseur à spirale
JP6809582B1 (ja) * 2019-08-30 2021-01-06 ダイキン工業株式会社 スクロール圧縮機

Citations (2)

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Publication number Priority date Publication date Assignee Title
JPH0392581U (fr) * 1990-01-10 1991-09-20
JP2007154761A (ja) * 2005-12-05 2007-06-21 Daikin Ind Ltd スクロール圧縮機

Family Cites Families (7)

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Publication number Priority date Publication date Assignee Title
US5586876A (en) * 1995-11-03 1996-12-24 Carrier Corporation Rotary compressor having oil pumped through a vertical drive shaft
JP2002257063A (ja) * 2001-02-28 2002-09-11 Sanden Corp スクロール型圧縮機
CN1751183A (zh) * 2002-09-24 2006-03-22 松下电器产业株式会社 涡旋式压缩机
EP2527655B1 (fr) * 2010-01-22 2017-12-06 Daikin Industries, Ltd. Compresseur à spirale
EP2633306B1 (fr) * 2010-10-27 2016-03-23 GE Healthcare Bio-Sciences AB Système de chromatographie comportant des colonnes de garde
CN103189653B (zh) * 2010-12-24 2015-09-23 东芝开利株式会社 多汽缸旋转式压缩机及制冷循环装置
JP5724706B2 (ja) * 2011-07-15 2015-05-27 ダイキン工業株式会社 回転式圧縮機

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0392581U (fr) * 1990-01-10 1991-09-20
JP2007154761A (ja) * 2005-12-05 2007-06-21 Daikin Ind Ltd スクロール圧縮機

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CN108138779A (zh) 2018-06-08
JP2017089504A (ja) 2017-05-25
EP3339647A1 (fr) 2018-06-27
JP6206468B2 (ja) 2017-10-04

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