EP3034878A1 - Scroll compressor - Google Patents

Scroll compressor Download PDF

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Publication number
EP3034878A1
EP3034878A1 EP14836075.3A EP14836075A EP3034878A1 EP 3034878 A1 EP3034878 A1 EP 3034878A1 EP 14836075 A EP14836075 A EP 14836075A EP 3034878 A1 EP3034878 A1 EP 3034878A1
Authority
EP
European Patent Office
Prior art keywords
oil
crankshaft
passage
scroll compressor
retention space
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP14836075.3A
Other languages
German (de)
English (en)
French (fr)
Inventor
Takashi Uekawa
Eri Watanabe
Masaaki FUWA
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Daikin Industries Ltd
Original Assignee
Daikin Industries Ltd
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 Daikin Industries Ltd filed Critical Daikin Industries Ltd
Publication of EP3034878A1 publication Critical patent/EP3034878A1/en
Withdrawn legal-status Critical Current

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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
    • 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
    • F04C29/005—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
    • F04C29/0057—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions for eccentric movement
    • 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
    • F04C29/025—Lubrication; Lubricant separation using a lubricant pump
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/50—Bearings
    • F04C2240/56—Bearing bushings or details thereof
    • 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 compressor.
  • a scroll compressor that has a crankshaft extending in a vertical direction, and that is designed to retain a lubricating oil (freezer oil) in a bottom section inside a casing, such as the compressor disclosed in Patent Document 1 ( Japanese Laid-open Patent Application 2011-137523 ) for example, has been described in the prior art.
  • lubricating oil is suctioned up through an opening provided at a bottom end of the crankshaft, and flows into an oil feed passage that extends vertically inside the crankshaft.
  • the flow of lubricating oil fed into the oil feed passage inside the crankshaft then branches into each of three branch passages, whereby oil is supplied to sliding members, such as the periphery of bearing metal of a bottom bearing, the periphery of bearing metal provided in a central expanded portion of the housing, the periphery of bearing metal provided to the cylindrical part of a rotating scroll, and the like.
  • a scroll compressor such as the one disclosed in the aforementioned Patent Document 1 ( Japanese Laid-open Patent Application 2011-137523 ) is configured so that lubricating oil retained in the bottom section of the housing is suctioned up; however, depending on the state of operation of a refrigeration device, there may be cases in which the lubricant in the bottom section becomes temporarily depleted.
  • the scroll compressor according to a first aspect of the present invention is provided with a casing, a compression mechanism part, a crankshaft, a motor, an oil feed pump, a lower oil reservoir part, an oil feed passage, and an oil retention space.
  • the compression mechanism part is accommodated within the casing, and has a stationary scroll, and a moveable scroll forming a compression chamber in relation to the stationary scroll.
  • the crankshaft is linked to the moveable scroll.
  • the motor rotatably drives the crankshaft.
  • the oil feed pump feeds lubricating oil upward.
  • the lower oil reservoir part is disposed in a space below the oil feed pump, and holds the lubricating oil.
  • the oil feed passage is formed so as to extend in the axial direction within the interior of the crankshaft, and communicates at a lower end with a discharge side of the oil feed pump.
  • the oil retention space is formed so as to extend in an axial direction within the crankshaft interior separately from the oil feed passage, and communicates with the oil feed passage.
  • the bottom end of the oil feed passage communicates with the discharge side of the oil feed pump, whereby under conditions in which the oil feed pump is being driven and lubricating oil is present in the lower oil reservoir part, the lubricating oil will be fed upward in the axial direction through the crankshaft interior.
  • the lubricating oil fed upwardly through the oil feed passage is fed as far as the outer periphery of the crankshaft, and oil can be supplied to the sliding sections. In contrast to this, it is possible for the oil retention space to retain lubricating oil within the internal space thereof.
  • a scroll compressor according to a second aspect of the present invention is the scroll compressor according to the first aspect of the present invention, wherein the oil feed passage and the oil retention space communicate via a communicating passage disposed in the interior of the crankshaft.
  • lubricating oil can be easily fed to the oil feed passage from the oil retention space via the communicating passage provided to the interior of the crankshaft.
  • a scroll compressor according to a third aspect of the present invention is the scroll compressor according to the first or second aspect of the present invention, wherein the oil retention space communicates with the discharge side of the oil feed pump via a space within the oil feed passage, without communicating directly with the discharge side of the oil feed pump.
  • the lubricating oil being fed upwardly by the oil feed pump is first fed preferentially into the oil feed passage. A portion of the rising lubricating oil fed into the oil feed passage is then fed towards the oil retention space side. Then, in cases in which oil can no longer be fed to the oil feed passage via the oil feed pump, as may occur under abnormal circumstances such as when the lubricating oil in the lower oil reservoir part has been depleted, rather than lubricating oil being fed into the oil retention space, the lubricating oil retained within the oil retention space flows down and is fed into the oil feed passage via the section thereof that communicates with the oil feed passage. In so doing, the lubricating oil held within the oil retention space can be fed to into the oil feed passage in a more reliable fashion, even under abnormal circumstances such as when the lubricating oil in the lower oil reservoir part has been depleted.
  • a scroll compressor according to a fourth aspect of the present invention is the scroll compressor according to any of the first to third aspects of the present invention, wherein the oil feed passage, the crankshaft, and the oil retention space are each cylindrical in shape.
  • the axial center of the oil retention space is disposed at a location closer to the axial center of the crankshaft with respect to the outer periphery thereof, than is the location of the axial center of the oil feed passage.
  • the axial center of the oil retention space is arranged closer to the axial center of the outer periphery of the crankshaft, than is the axial center of the oil feed passage. For this reason, even at times of rotational driving of the crankshaft, the lubricating oil retained in the oil retention space is less susceptible to the action of centrifugal force, as compared with the lubricating oil inside the oil feed passage. It is therefore possible for the lubricating oil to be retained more easily in the interior.
  • a scroll compressor according to a fifth aspect of the present invention is the scroll compressor according to the fourth aspect of the present invention, wherein the axial center of the oil retention space is disposed at an identical location to the location of the axial center of the crankshaft with respect to the outer periphery thereof.
  • a scroll compressor according to a sixth aspect of the present invention is the scroll compressor according to any of the first to fifth aspects of the present invention, further provided with a supply path disposed such that it is possible to supply lubricating oil towards the outer periphery of the crankshaft from the interior of the oil feed passage.
  • the supply passage which may be configured, for example, by a hole shape penetrating between the interior of the oil feed passage and the outer periphery of the crankshaft, or configured by a shape produced by partial cutting of the outer peripheral surface of the crankshaft so that lubricating oil may be supplied from the oil feed passage to the vicinity of an upper end of the crankshaft via the upper end section of the crankshaft.
  • a scroll compressor according to a seventh aspect of the present invention is the scroll compressor according to the sixth aspect of the present invention, wherein the supply passage is a horizontal oil-feed hole disposed so as to pass between the interior of the oil feed passage and the outer periphery of the crankshaft in the crankshaft interior.
  • This scroll compressor has a horizontal oil-feed hole disposed so as to pass through the crankshaft interior, between the interior of the oil feed passage and the outer periphery of the crankshaft. It is therefore possible for lubricating oil to be supplied to the outer peripheral section of the crankshaft by branching off the flow thereof midway along the oil feed passage, even without the oil being fed as far as the upper end of the oil feed passage.
  • a scroll compressor according to an eighth aspect of the present invention is the scroll compressor according to the seventh aspect of the present invention, wherein the oil retention space either lacks an opening that penetrates as far as the outer periphery of the crankshaft, or is provided with a hole that extends so as to penetrate from the interior to the outer periphery of the crankshaft and has a smaller passage cross-sectional area than that of the horizontal oil-feed hole.
  • the oil retention space either is not provided with an opening that penetrates as far as the outer periphery of the crankshaft, or the provided hole has a smaller passage cross-sectional area than the horizontal oil-feed hole. Therefore, leakage of lubricating oil to the outside from inside the oil retention space can be minimized, making it possible for the lubricating oil to be easily retained in a space in the interior of the oil retention space.
  • a scroll compressor according to a ninth aspect of the present invention is the scroll compressor according to the seventh or eighth aspect of the present invention, further provided with an upper bearing part and a lower bearing part.
  • the upper bearing part supports the crankshaft from a circumferential direction.
  • the lower bearing part supports the crankshaft from a circumferential direction, at a point below the upper bearing part.
  • the horizontal oil-feed hole has a lower bearing horizontal oil-feed hole that extends towards the lower bearing part from within the oil feed passage.
  • the oil retention space and the oil feed passage communicate at a location below the location at which the lower bearing horizontal oil-feed hole branches from the oil feed passage.
  • This scroll compressor is configured such that the location at which the oil retention space and the oil feed passage communicate is a location below the location at which the lower bearing horizontal oil-feed hole branches off from the oil feed passage. Therefore, even under abnormal circumstances such as when the lubricating oil in the lower oil reservoir part has been depleted, the lubricating oil retained within the oil retention space can be fed, via the communicating section, to the oil feed passage interior and move to a location at which centrifugal force acts more readily, and to thereby ascend due to centrifugal force and be fed as far as the section where the lower bearing horizontal oil-feed hole branches off from the oil feed passage. In so doing, it is possible to minimize friction in the sliding section between the lower bearing part and the crankshaft, even under abnormal circumstances such as when the lubricating oil in the lower oil reservoir part has been depleted.
  • a scroll compressor according to a tenth aspect of the present invention is the scroll compressor according to the ninth aspect of the present invention, further provided with an upper communicating passage.
  • the upper communicating passage provides communication between the interior of the oil feed passage and the interior of the oil retention space.
  • the oil retention space and the oil feed passage communicate at a location below the upper communicating passage.
  • the upper communicating passage causes the interior of the oil feed passage and the interior of the oil retention space to communicate, at a location above the location at which the oil retention space and the oil feed passage communicate. Therefore, a portion of the lubricating oil retained in the interior of the oil retention space is fed into the oil feed passage via the upper communicating passage, not via the location at which the oil retention space and the oil feed passage communicate. Therefore, it is possible to shorten the interval from the point in time that the lubricating oil in the lower oil reservoir part is depleted, until lubricating oil can be supplied to sliding sections in the upper part of the crankshaft.
  • a scroll compressor according to an eleventh aspect of the present invention is the scroll compressor according to the seventh aspect of the present invention, further provided with an upper bearing part and a lower bearing part.
  • the upper bearing part supports the crankshaft from a circumferential direction.
  • the lower bearing part supports the crankshaft from a circumferential direction, at a point below the upper bearing part.
  • the horizontal oil-feed hole has an upper bearing horizontal oil-feed hole that extends towards the inner peripheral surface of the upper bearing part from within the oil feed passage.
  • a scroll compressor according to a twelfth aspect of the present invention is the scroll compressor according to the seventh aspect of the present invention, wherein the moveable scroll has a cylindrical part for covering the upper end of the crankshaft from the circumferential direction.
  • the horizontal oil-feed hole has an upper horizontal oil-feed hole that extends towards the inner peripheral surface of the cylindrical part from within the oil feed passage.
  • a scroll compressor according to a thirteenth aspect of the present invention is the scroll compressor according to the fourth or fifth aspect of the present invention, wherein the inside diameter of the oil retention space is 0.5-2.0 times the inside diameter of the oil feed passage.
  • a scroll compressor according to a fourteenth aspect of the present invention is the scroll compressor according to any of the first to thirteenth aspects of the present invention, wherein the oil retention space is open at the upper end.
  • a scroll compressor according to a fifteenth aspect of the present invention is the scroll compressor according to any of the first to fourteenth aspects of the present invention, further provided with a member arranged in the interior of the oil retention space, for limiting the descent speed of the lubricating oil within the oil retention space.
  • the oil feed passage can be easily fed lubricating oil from the oil retention space.
  • the scroll compressor according to the third aspect of the present invention even under abnormal circumstances such as when the lubricating oil in the lower oil reservoir part has been depleted, the lubricating oil retained in the oil retention space can be fed into the oil feed passage in a more reliable manner.
  • the lubricating oil can be easily fed to the oil feed passage even when the crankshaft is rotating, and decline in the strength of the crankshaft can be minimized.
  • FIG. 1 shows a longitudinal cross-sectional view of a scroll compressor 1 during normal operation.
  • FIG. 2 shows a longitudinal cross-sectional view of the scroll compressor 1 when depleted.
  • FIG. 3 shows a fragmentary enlarged cross-sectional view of section X of FIG. 2 .
  • FIG 4 shows a schematic diagram of a structure in the vicinity of the crankshaft bottom end.
  • the scroll compressor 1 is a scroll compressor of high-low pressure dome type, and together with an evaporator, a condenser, an expansion mechanism, and the like, makes up a refrigerant circuit.
  • This scroll compressor 1 performs the role of compressing a refrigerant gas in the refrigerant circuit.
  • the scroll compressor 1 is configured mainly from a sealed dome type casing 10 of vertically elongated cylindrical shape, a pin bearing part 22, an upper bearing part 32, a lower bearing part 27, a motor 16, a volumetric pump 79, an intake pipe 19, a discharge pipe 20, a compression mechanism part 15, a crankshaft 17 that functions as a drive shaft, and an oil return guide 71. These constituent components of the scroll compressor 1 are each described in detail below.
  • the casing 10 is a vertically elongated sealed container, and has a generally cylindrical-shaped barrel casing part 11, a bowl-shaped upper wall part 12 welded airtightly to an upper end part of the barrel casing part 11, and a bowl-shaped lower wall part 13 welded airtightly to a lower end part of the barrel casing part 11.
  • the casing 10 mainly accommodates the compression mechanism part 15, which compresses the refrigerant gas, and the motor 16, which is arranged below the compression mechanism part 15.
  • the compression mechanism part 15 and the motor 16 are linked by the crankshaft 17, which is arranged extending in a vertical direction within the casing 10. Between the compression mechanism part 15 and the motor 16 is a high-pressure space 18.
  • the pin bearing part 22 supports a pin shaft part 17b at the upper end of the crankshaft 17, from the outside in a diametrical direction.
  • the pin bearing part 22 is constituted by a boss part 26c that extends in a cylindrical profile axially downward from the vicinity of the center of a moveable scroll 26, discussed below, and pin shaft bearing metal 87 fitted against the inner peripheral surface to the diametrical inside of the boss part 26c, and is disposed such that the inner peripheral surface of the pin shaft bearing metal 87 contacts the outer peripheral surface of the pin shaft part 17b of the crankshaft 17.
  • the upper bearing part 32 is located somewhat above the center within the casing 10, and supports a section of the crankshaft 17 below the pin shaft part 17b from the outside in a diametrical direction.
  • the upper bearing part 32 is configured from an upper inner peripheral section 23a situated at the diametrical inside of an upper bearing housing 23, discussed below, and upper bearing metal 88 fitted against the inner peripheral surface at the diametrical inside of the upper bearing part 32.
  • the inner peripheral surface of the upper bearing metal 88 is disposed so as to contact the outer peripheral surface the crankshaft 17 in a section thereof that lies below the pin shaft part 17b.
  • the relationship of the upper bearing part 32 to the upper bearing housing 23 is discussed below.
  • the lower bearing part 27 is located in a lower part within the casing 10, and supports a lower section of the crankshaft 17 from the outside in a diametrical direction.
  • the lower bearing part 27 is configured from a lower inner peripheral section 28a situated to the diametrical inside of the lower bearing housing 28, and lower bearing metal 89 that fits against the inner peripheral surface at the diametrical inside of the lower inner peripheral section 28a; and is moreover disposed such that the inner peripheral surface of the lower bearing metal 89 contacts the outer peripheral surface of the lower section of the crankshaft 17.
  • the lower bearing housing 28 is arranged in a lower space below the motor 16. This lower bearing housing 28 is fixed at a diametrical outside end part thereof to an inner peripheral section of the barrel casing part 11.
  • the motor 16 is configured mainly from a ring-shaped stator 51 fixed to an inner wall surface of the casing 10, and a rotor 52 accommodated rotatably to the inside of the stator 51, with a slight gap (air gap passage) therebetween.
  • Copper wire is wound about the stator 51 at top and bottom, forming a coil end 53.
  • An upper end of the coil end 53 of the stator 51 is arranged such that the heightwise position is substantially the same as that of the bottom end of the upper bearing part 32 of the upper bearing housing 23, discussed below.
  • the outer peripheral surface of the stator 51 is provided at several locations, spaced apart by prescribed distances in the circumferential direction, with groove-shaped core cut parts 51a that extend in a plumb vertical direction from an upper end surface to a lower end surface of the stator 51.
  • These core cut parts 51a are configured as motor cooling passages that extend in the vertical direction between the inner peripheral side of the barrel casing part 11 and the outer peripheral side of the stator 51.
  • an oil return flow channel 74 through which it is possible for the lubricating oil to descend is formed between the outer peripheral side of the stator 51 and the inner peripheral side of the main casing 10.
  • the rotor 52 is drive-coupled to the moveable scroll 26 of the compression mechanism part 15 via the crankshaft 17, which is arranged at the axial center of the barrel casing part 11 so as to extend in the vertical direction.
  • the volumetric pump 79 for suctioning up the lubricating oil in a lower oil reservoir part P into an oil feed passage 17a of the crankshaft 17 is disposed at the lower end of the crankshaft 17.
  • a "trochoid pump” is employed as the volumetric pump 79. This trochoid pump is configured to suction up the lubricating oil through changes in volume brought about by rotary operation of rotors or gears to produce suctioning/discharge action of the lubricating oil in the lower oil reservoir part P.
  • this volumetric pump 79 is arranged so as to communicate with the lower end of the crankshaft 17.
  • a space communicating with the discharge side of the volumetric pump 79 at the lower end of the crankshaft 17 communicates in a diametrical direction with a lower end section of the oil feed passage 17a, and is configured to suction up the lubricating oil by rotating in tandem with the crankshaft 17.
  • volumetric pump rather than a pressure differential pump or the like, as the pump for supplying the lubricating oil to the sliding sections in this manner, it is possible for oil to be supplied more easily to the sliding sections of the lower bearing part 27.
  • volumetric pump 79 by drawing up the lubricating oil in the lower oil reservoir part P with the volumetric pump 79 in a manner free of limitation to a state of driving by the compression mechanism part 15 in order to produce a pressure differential between an oil feed source and an oil feed destination, a more reliable feed of oil to the sliding sections of the lower bearing part 27 via the oil feed passage 17a of the crankshaft 17 and the oil retention space 90 is possible.
  • the intake pipe 19 is a line for guiding the refrigerant of the refrigerant circuit to the compression mechanism part 15, and is fitted airtightly into the upper wall part 12 of the casing 10.
  • the intake pipe 19 passes in the vertical direction through a low-pressure space 29 which is a space at the top of the casing 10 interior, and a bottom end part thereof is fitted into a stationary scroll 24.
  • the discharge pipe 20 is a line for discharging the refrigerant within the casing 10 to outside the casing 10, and is fitted airtightly into the barrel casing part 11 of the casing 10. An end of this discharge pipe 20 is disposed at a location so as to protrude further to the inside from the inner peripheral surface of the barrel casing part 11.
  • the compression mechanism part 15 is configured mainly from the stationary scroll 24 which is arranged airtightly above the upper bearing housing 23, discussed below, and the moveable scroll 26 which is interleaved with the stationary scroll 24.
  • the stationary scroll 24 has a flat plate-shaped end plate 24a, and a lap 24b of spiral shape (involute shape) viewed from the bottom surface, formed extending downward from the bottom surface of the end plate 24a.
  • the end plate 24a is perforated in an axial direction by a discharge port 41 at the approximate axial center of the top surface side.
  • This discharge port 41 communicates with a compression chamber 40, discussed below.
  • the discharge port 41 is formed so as to extend in the vertical direction.
  • an expanded recess part 42 that extends upward and expands further in a horizontal direction than the upper end opening section of the discharge port 41.
  • a cover 44 is affixed to the expanded recess part 42 so as to provide closure from above.
  • a space enclosed in the vertical direction by the expanded recess part 42 and the cover 44 forms a muffler space 45.
  • This muffler space 45 functions as an expansion chamber for silencing operating noise of the compression mechanism part 15.
  • a seal structure is employed between the stationary scroll 24 and the cover 44, to provide intimate contact through the agency of a gasket, not illustrated.
  • the refrigerant discharged from the discharge port 41 of the compression mechanism part 15 passes through the muffler space 45, passes downward through an access passage (not illustrated) which is formed near the outer periphery of the upper bearing housing 23 and which is formed to penetrate therethrough in the vertical direction, whereupon a portion of the flow is split off and directed into a gas guide (not illustrated), passes downward through a specific one of the core cuts 51a until reaching a space near the underside of the motor 16, and thereafter passes upward through a passage such as a different one of the core cuts 51 a, and thereby fed into the high-pressure space 18. Another portion, with the lubricating oil separated by centrifugal force, is fed to the high-pressure space 18 via a hole provided in the gas guide (not illustrated).
  • the moveable scroll 26 has an end plate 26a; a lap 26b of spiral shape (involute shape) viewed from the top surface, formed extending to the upper surface side of the end plate 26a; and a boss part 26c which configures a pin bearing part for receiving the upper end of the crankshaft 17, and which is formed so as to extend in a cylindrical profile to the lower surface side of the end plate 26a.
  • the present embodiment employs an inner drive moveable scroll.
  • the boss part 26c of the moveable scroll 26 covers from the outside in the diametrical direction the pin shaft part 17b which configures the proximity of the upper end of the crankshaft 17. In this way, the moveable scroll 26 and the crankshaft 17 are rotatably linked.
  • the lap 26b which extends upward from the moveable scroll 26, is interleaved from the vertical direction with the lap 24b which extends downward from the stationary scroll 24, in such a way that the scrolls overlap in the diametrical direction.
  • the lap 24b of the stationary scroll 24 and the lap 26b of the moveable scroll 26 are interleaved in such a way that the compression chamber 40 is formed between the contacting sections.
  • the moveable scroll 26 is supported by the upper surface of the upper bearing housing 23, in such a way as to prevent rotational motion.
  • the pin shaft part 17b at the upper end of the crankshaft 17 is inserted into the boss part 26c, to the inside thereof in the diametrical direction.
  • the boss part 26c which is linked to the pin shaft part 17b in such a way that rotary driving force is transmitted thereto, is acted upon by the force of the crankshaft 17, and the moveable scroll 26 orbits without rotating within the upper bearing housing 23.
  • the compression chamber 40 formed by the lap 24b of the stationary scroll 24 and the lap 26b of the moveable scroll 26 becomes shorter in distance in the diametrical direction from the discharge port 41, while advancing in the rotational advance direction, thereby contracting while the volume faces the center.
  • the refrigerant gas is compressed in this manner.
  • the lubricating oil which has been pressurized by the volumetric pump 79 ascends through the oil feed passage 17a which penetrates the crankshaft 17 interior in the axial direction, feeding oil to the lower bearing part 27, the upper bearing part 32, and the pin bearing part 22, respectively, and is fed into a pin shaft headspace 37 at the upper end of the crankshaft 17, which is part of a linking space to the inside of the inner peripheral surface of the boss part 26c of the moveable scroll 26.
  • the upper bearing housing 23 is affixed, along the entire outer peripheral surface thereof in the circumferential direction, against the inner peripheral surface of the barrel casing part 11 by pressure fitting. In so doing, the diametrical inside of the barrel casing part 11 and the diametrical outside of the upper bearing housing 23 are disposed in airtight intimate contact about their entire circumference.
  • the interior of the casing 10 is thereby partitioned into the high-pressure space 18 below the upper bearing housing 23, and the low-pressure space 29 above the upper bearing housing 23.
  • the stationary scroll 24 is affixed by fastening with a bolt (not illustrated) to the upper bearing housing 23, so that the upper end surface of the latter is disposed in intimate contact against the lower end surface of the stationary scroll 24.
  • This upper bearing housing 23 has a downwardly-recessed crank chamber 31 at the center of the upper surface.
  • a lower section of the upper bearing housing 23 is formed such that the diametrical length at the outer periphery thereof increases moving upwards from the lower end, while the inner periphery is formed to cylindrical shape, the axial direction of which is aligned with the plumb vertical direction.
  • the upper inner peripheral section 23a which is part of the upper bearing part 32, is a section that corresponds to this cylindrical shape.
  • This upper inner peripheral section 23a, and the round cylindrical upper bearing metal 88 which is fitted into the diametrical inside thereof and shares the same axial direction, together configure the upper bearing part 32.
  • the inner peripheral surface of this upper bearing metal 88 rotatably supports a section of the crankshaft 17 below the pin shaft part 17b, from the outside in the diametrical direction.
  • a diametrical oil passage 35 that extends diametrically outside through to reach the outer peripheral surface from the vicinity of the lower end of the crank chamber 31.
  • Lubricating oil which has been supplied into the crank chamber 31 passes through this diametrical oil passage 35 and descends between the oil return guide 71, discussed below, and the casing 10, descends through the gap between the barrel casing part 11 and the stator 51, and is returned to the lower oil reservoir part P in the lower part of the casing 10.
  • annular sealing ring 86 for sealing off the section of high pressure to the inside in the area below the moveable scroll 26 and the section of low pressure to the outside in the area below the moveable scroll 26, in order to maintain high pressure in the crank chamber 31 interior.
  • the refrigerant discharged from the discharge port 41 of the compression mechanism part 15 passes through the muffler space 45, a portion thereof passes downward through specific one of the core cuts 51a until reaching the space near the underside of the motor 16, and thereafter passes upward through a passage such as a different one of the core cuts 51a, and is thereby fed to the high-pressure space 18. Another portion passes through a hole in the gas guide (not illustrated), and is fed to the high-pressure space 18.
  • the refrigerant gas fed to the high-pressure space 18 is discharged to outside the casing 10 from the discharge pipe 20.
  • the crankshaft 17 is a drive shaft for transmitting the drive force of the motor 16 to the compression mechanism part 15.
  • crankshaft 17 is rotatably supported inside the casing 10 by the upper bearing part 32 of the upper bearing housing 23, and the lower bearing part 27.
  • a medial section of the crankshaft 17 is linked concentrically to the rotor 52 of the motor 16.
  • the pin shaft part 17b is disposed at the upper end of the crankshaft 17, and positioned eccentrically from the medial section of the crankshaft 17.
  • the pin shaft part 17b is inserted towards an inner peripheral space of the boss part 26c of the moveable scroll 26. In so doing, it is possible for the moveable scroll 26 to undergo revolutionary movement, through rotation of the crankshaft 17 by the drive force of the motor 16.
  • the oil feed passage 17a In the interior of the crankshaft 17 are formed the oil feed passage 17a extending in the axial direction of the crankshaft 17, and the oil retention space 90 which is provided separately from the oil feed passage 17a but which likewise extends in the axial direction of the crankshaft 17.
  • the pin shaft part 17b of the crankshaft 17 In the pin shaft part 17b of the crankshaft 17, there is formed a pin bearing horizontal oil-feed hole 17c which branches to extend out diametrically towards the outside from a point midway along the oil feed passage 17a, and communicates in a diametrical direction with the pin shaft part 17b. Via this the pin bearing horizontal oil-feed hole 17c, lubricating oil is supplied to sliding sections between the inner peripheral surface of the boss part 26c of the moveable scroll 26 and the outer peripheral surface of the pin shaft part 17b.
  • the discharge side of the volumetric pump 79 communicates with the lower end of the oil feed passage 17a.
  • a space that communicates with the discharge side of the volumetric pump 79 at the lower end of the crankshaft 17 communicates in a diametrical direction with a lower end section of the oil feed passage 17a.
  • the upper end of the oil feed passage 17a extends as far as the upper end section of the crankshaft 17, and the upper end section is open vertically.
  • the pin bearing horizontal oil-feed hole 17c which branches to extend out diametrically towards the outside from a point midway along the oil feed passage 17a, and communicates as far as the near side of the inner peripheral surface of the pin shaft bearing metal 87 situated at the outside.
  • the lubricating oil is supplied, via this pin bearing horizontal oil-feed hole 17c, to the sliding sections between the outer peripheral surface of the pin shaft part 17b and the inner peripheral surface of the pin shaft bearing metal 87 disposed inside the boss part 26c of the moveable scroll 26.
  • a lower bearing horizontal oil-feed hole 17d which branches and extends towards the outside in a diametrical direction from a point midway along the oil feed passage 17a, and extends to penetrate as far as the near side of the inner peripheral surface of the lower bearing metal 89 situated at the outside. Sliding sections between the inner peripheral surface of the lower bearing metal 89 of the lower bearing part 27 and outer peripheral surface in the vicinity of the lower end of the crankshaft 17 are supplied with oil via this lower bearing horizontal oil-feed hole 17d.
  • an upper bearing horizontal oil-feed hole 17e which branches and extends towards the outside in a diametrical direction from a point midway along the oil feed passage 17a, and extends to penetrate as far as the near side of the inner peripheral surface of the upper bearing metal 88 situated at the outside. Sliding sections between the inner peripheral surface of the upper bearing metal 88 of the upper bearing part 32 and the lower outer peripheral surface of the pin shaft part 17b of the crankshaft 17 are supplied with oil via this upper bearing horizontal oil-feed hole 17e.
  • the axial center of the oil feed passage 17a is arranged at a different location than the axial center of the outer peripheral surface of the crankshaft 17. Specifically, the axial center of the oil feed passage 17a is eccentric in relation to the axial center with respect to the outer periphery of the crankshaft 17. In so doing, during rotation of the crankshaft 17, centrifugal force readily acts on the lubricating oil within the oil feed passage 17a, and the oil is easily supplied upward.
  • the oil retention space 90 like the oil feed passage 17a, is cylindrical in shape, and the axial center thereof is arranged at the same location as the axial center of the outside peripheral surface of the crankshaft 17. Specifically, the axial center of the oil retention space 90 is arranged closer to the axial center of the outer peripheral surface of the crankshaft 17 than is the axial center of the oil feed passage 17a. In so doing, even during drive rotation of the crankshaft 17, the lubricating oil present inside the oil retention space 90 is largely unaffected by the action of centrifugal force, and therefore readily descends downward due to the weight of the lubricating oil itself.
  • the lower end of the oil retention space 90 does not communicate directly with the discharge side of the volumetric pump 79, but rather communicates with the discharge side of the volumetric pump 79 via a space inside the oil feed passage 17a. In this way, the vicinity of the lower end of the oil retention space 90 is connected, via a communicating passage 91 extending in the diametrical direction, to the vicinity of the lower end of the oil feed passage 17a. As shown in FIG. 4 , a communication location B at which the communicating passage 91 and the oil feed passage 17a communicate is located below the section where the lower bearing horizontal oil-feed hole 17d branches off from the oil feed passage 17a.
  • the oil retention space 90 of the present embodiment lacks a horizontal oil-feed hole configured to penetrate as far as the outer peripheral surface of the crankshaft 17. Therefore, when the lubricating oil is fed towards the bottom of the oil feed passage 17a from the volumetric pump 79 through rotary driving of the crankshaft 17, the lubricating oil collects within the oil retention space 90 via the communicating passage 91. As shown in FIG. 3 , the upper end of the oil retention space 90 extends as far as the upper end section of the crankshaft 17, and the upper end section opens vertically, to a size about equal to the inside diameter of the cylindrical section. In the present embodiment, the inside diameter of the oil retention space 90 is formed to an inside diameter equal to the inside diameter of the oil feed passage 17a.
  • the pin shaft headspace 37 which is a space lying between the upper end surface of the pin shaft part 17b of the distal end of the crankshaft 17 and the lower surface of the end plate 26a of the moveable scroll 26, and a pin shaft circumferential space 38 (part of the crank chamber 31), which is a space lying between the outer peripheral surface of the pin shaft part 17b of the distal end of the crankshaft 17 and the inner peripheral surface of the pin shaft bearing metal 87 disposed inside the boss part 26c of the moveable scroll 26, are respectively formed in the interior of the boss part 26c of the moveable scroll 26.
  • a portion of the lubricating oil supplied via the oil feed passage 17a in the crankshaft 17 interior is supplied between the moveable scroll 26 and the stationary scroll 24, via the pin shaft headspace 37.
  • the pin shaft circumferential space 38 is formed such that a diametrical width of about several tens of microns extends in the vertical direction.
  • the oil return guide 71 is a member of thin metal plate shape, arranged below the diametrical outside of the upper bearing housing 23 in a space above the motor 16, and is affixed to the barrel casing part 11, forming a flow channel in relation to the inner peripheral face of the barrel casing part 11.
  • This oil return guide 71 guides the lubricating oil which has passed through the diametrical oil passage 35 formed in the upper bearing housing 23, and extends in the diametrical direction into an upper end section of the oil return flow channel 74 situated between the outer peripheral surface of the stator 51 and the inner peripheral surface of the barrel casing part 11.
  • the lubricating oil guided into the upper end section of the oil return flow channel 74 then descends through the oil return flow channel 74, and collects in the lower oil reservoir part P in the lower part of the casing 10.
  • the low-pressure refrigerant gas is suctioned through the intake pipe 19 and into the compression chamber 40 from the peripheral edge side of the compression chamber 40, and is compressed in association with the changing volume of the compression chamber 40, becoming transformed to high-pressure refrigerant gas.
  • This high-pressure refrigerant gas is discharged from a center part of the compression chamber 40 into the muffler space 45 through the discharge port 41, and thereafter flows downward through the access passage (not illustrated) of the upper bearing housing 23, whereupon a portion of the flow is split off, flows in a circumferential direction along the inner peripheral surface of the barrel casing part 11, and is fed into the high-pressure space 18 through a hole in the gas guide (not illustrated). At this time, lubricating oil admixed into the refrigerant gas is separated, and is retained in the lower oil reservoir part P.
  • Another portion of the divided flow of refrigerant gas passes downward through a specific one of the core cuts 51a formed in the rotor 52 until reaching the space near the underside of the motor 16, and thereafter reverses course and passes upward through an airgap passage between a different one of the core cuts 51a, the stator 51, and the rotor 52, and is thereby fed to the high-pressure space 18.
  • the converged flow of the refrigerant gas fed into the high-pressure space 18 is discharged to outside the casing 10 through the discharge pipe 20.
  • the refrigerant gas discharged to outside the casing 10 is then circulated through the refrigerant circuit, and thereafter is again sucked into the compression mechanism part 15 through the intake pipe 19, and compressed.
  • the lubricating oil of lower oil reservoir part P in the casing 10 interior is drawn up by the pumping action of the volumetric pump 79, whereby the lubricating oil ascends through the oil feed passage 17a of the crankshaft 17.
  • a portion of the lubricating oil is branched off via the communicating passage 91 and is stored in the interior of the oil retention space 90 (see the arrows in FIG. 1 ).
  • Some of the lubricating oil ascending through the oil feed passage 17a is supplied to the sliding section of the lower bearing part 27 via the lower bearing horizontal oil-feed hole 17d.
  • the lubricating oil ascending further up through the oil feed passage 17a is supplied to the sliding section of the upper bearing part 32 via the upper bearing horizontal oil-feed hole 17e.
  • the lubricating oil ascending further up through the oil feed passage 17a is supplied to the sliding section of the pin bearing part 22 through the pin bearing horizontal oil-feed hole 17c.
  • the lubricating oil within the oil feed passage 17a now becomes susceptible to the action of centrifugal force produced by rotary driving of the crankshaft 17, and therefore ascends within the oil feed passage 17a.
  • the lubricating oil ascending within the oil feed passage 17a is thereby supplied in respective fashion to the sliding section of the lower bearing part 27 via the lower bearing horizontal oil-feed hole 17d, to the sliding section of the upper bearing part 32 via the upper bearing horizontal oil-feed hole 17e, and to the sliding section of the pin bearing part 22 via the pin bearing horizontal oil-feed hole 17c.
  • the volumetric pump 79 is driven, whereby the lubricating oil stored in the lower oil reservoir part P is fed upward via the oil feed passage 17a, and in so doing is supplied to the sliding section of the lower bearing part 27, the sliding section of the upper bearing part 32, the sliding section of the pin bearing part 22, and the sliding section near the compression mechanism part 15 at the top, preventing seizing and the like of these sliding sections.
  • lubricating oil can be stored to the oil retention space 90.
  • the lubricating oil being stored in the oil retention space 90 can be utilized to supply the sliding section of the lower bearing part 27, the sliding section of the upper bearing part 32, the sliding section of the pin bearing part 22, and the sliding section near the compression mechanism part 15 at the top.
  • the sliding parts can be supplied continuously until no oil is left within the oil retention space 90, so that a shortage of lubricating oil is unlikely to occur even under during abnormal circumstances, making it possible to minimize problems such as seizing and the like.
  • the preceding first embodiment described an example of a case in which the upper end of the oil retention space 90 opens vertically.
  • a scroll compressor 201 it being acceptable for a scroll compressor 201 to have a crankshaft 217 formed so as to be provided with a diametrical section 96, as shown in FIG 5 for example.
  • This diametrical section 96 is produced by extending an upper section of the oil retention space 90 near the pin shaft part 17b, so as to pass through the pin shaft part 17b towards the outside in a diametrical direction, as far as an outside peripheral section thereof.
  • This scroll compressor 201 affords working effects like those of the preceding embodiment.
  • the preceding first embodiment described an example of a case in which the oil retention space 90 and the oil feed passage 17a in the crankshaft 17 lack a communicating section in any section besides the communicating passage 91.
  • a scroll compressor 301 may be provided, for example, with a first internal passage 317s and a second internal passage 317t through which the oil retention space 90 and the oil feed passage 17a communicate with one another at locations above the communicating passage 91, as shown in FIG. 6 .
  • This first internal passage 317s is disposed at a location at the same height as the pin bearing horizontal oil-feed hole 17c, so as to pass through between the oil retention space 90 and the oil feed passage 17a.
  • the second internal passage 317t is disposed at a location at the same height as the upper bearing horizontal oil-feed hole 17e, so as to pass through between the oil retention space 90 and the oil feed passage 17a.
  • the lubricating oil retained within the oil retention space 90 is fed to the oil feed passage 17a via the first internal passage 317s and/or the second internal passage 317t, rather than via the communicating passage 91 through which the oil retention space 90 and the oil feed passage 17a communicate at a point further down, and can thereby be supplied to the sliding section of the pin bearing part 22 and/or the sliding section of the upper bearing part 32.
  • the interval from the point in time that the lubricating oil in the lower oil reservoir part P is depleted until lubricating oil can be supplied to sliding sections in the upper part of the crankshaft 17 is shortened.
  • the heightwise location of the end of the first internal passage 317s at the oil feed passage 17a side thereof may be a location lower than the heightwise location of the pin bearing horizontal oil-feed hole 17c and higher than the heightwise location of the upper bearing horizontal oil-feed hole 17e, rather than the same as the heightwise location of the pin bearing horizontal oil-feed hole 17c.
  • the lubricating oil that has been fed into the oil feed passage 17a via the first internal passage 317s can ascend somewhat within the oil feed passage 17a, and be fed as far as the pin bearing horizontal oil-feed hole 17c.
  • the heightwise location of the end of the second internal passage 317t at the oil feed passage 17a side thereof may be a location above the heightwise location of the lower bearing horizontal oil-feed hole 17d and below the heightwise location of the upper bearing horizontal oil-feed hole 17e, rather than the same as the heightwise location of the upper bearing horizontal oil-feed hole 17e.
  • the lubricating oil that has been fed into the oil feed passage 17a via the second internal passage 317t can ascend somewhat within the oil feed passage 17a, and be fed as far as the upper bearing horizontal oil-feed hole 17e.
  • the passage cross-sectional area of the first internal passage 317s (the smallest area among areas perpendicular to the direction of passage in the case where the lubricating oil passes from the oil retention space 90 to the oil feed passage 17a) may be configured to be smaller than the passage cross-sectional area of the pin bearing horizontal oil-feed hole 17c. In so doing, the extent to which the lubricating oil in the oil retention space 90 interior leaks to the outside via the first internal passage 317s can be minimized, and the lubricating oil can be easily retained within the oil retention space 90.
  • the passage cross-sectional area of the second internal passage 317t (the smallest area among areas perpendicular to the direction of passage in the case where the lubricating oil passes from the oil retention space 90 to the oil feed passage 17a) may be configured to be smaller than the passage cross-sectional area of the upper bearing horizontal oil-feed hole 17e. In so doing, the extent to which the lubricating oil in the oil retention space 90 interior leaks to the outside via the second internal passage 317t can be minimized, and the lubricating oil can be easily retained within the oil retention space 90.
  • the first embodiment described an example of a case in which the crankshaft 17 lacks a hole for communication between the interior of the oil retention space 90 and the outside of the crankshaft 17.
  • a scroll compressor 401 could, for example, be provided with a crankshaft 417 having a first outer passage 417s and a second outer passage 417t through which the oil retention space 90 and the outside of the crankshaft 417 communicate with one another at locations above the communicating passage 91, as shown in FIG. 7 .
  • This first outer passage 417s extends to pass through from the interior of the oil retention space 90 to the outside of the crankshaft 417, at the same heightwise location as the pin bearing horizontal oil-feed hole 17c.
  • the second outer passage 417t extends to pass through from the interior of the oil retention space 90 to the outside of the crankshaft 417, at the same heightwise location as the upper bearing horizontal oil-feed hole 17e.
  • the passage cross-sectional area of the first outer passage 417s (in the case where the lubricating oil passes from the oil retention space 90 to the outside of the crankshaft 417, the smallest area among areas perpendicular to the direction of passage) may be configured to be smaller than the passage cross-sectional area of the pin bearing horizontal oil-feed hole 17c. In so doing, the extent to which the lubricating oil in the oil retention space 90 interior leaks to the outside via the first outer passage 417s can be minimized, and the lubricating oil can be easily retained within the oil retention space 90.
  • the passage cross-sectional area of the second outer passage 417t (in the case where the lubricating oil passes from the oil retention space 90 to the outside of the crankshaft 417, the smallest area among areas perpendicular to the direction of passage) may be configured to be smaller than the passage cross-sectional area of the upper bearing horizontal oil-feed hole 17e. In so doing, the extent to which the lubricating oil in the oil retention space 90 interior leaks to the outside via the second outer passage 417t can be minimized, and the lubricating oil can be easily retained within the oil retention space 90.
  • the lubricating oil retained in the oil retention space 90 can be supplied to the sliding section of the pin bearing part 22 and/or the sliding section of the upper bearing part 32 via the first outer passage 417s and the second outer passage 417t, instead of via the communicating passage 91 through which the oil feed passage 17a and the oil retention space 90 communicate further towards the bottom.
  • the interval from the point in time that the lubricating oil in the lower oil reservoir part P is depleted until lubricating oil can be supplied to sliding sections in the upper part of the crankshaft 417 is shortened.
  • the porous substance 590x retains the lubricating oil to a greater degree than in the case of a hollow space, and therefore the speed of descent of the lubricating oil is slower.
  • the material of the porous substance 590x e.g., polyethylene or polypropylene could be used.
  • the form of the porous substance 590x but a sponge-like form is preferred.
  • a scroll compressor 601 provided with a crankshaft 617 like that shown in FIG. 9 for example, having a first inner passage 617s and a second inner passage 617t through which the oil retention space 90 and the oil feed passage 17a communicate with one another at a location above the communicating passage 91, and having a porous substance 690x packed into the interior of the oil retention space 90 (specifically, the porous substance 690x may be packed into the oil retention space 90 of the aforedescribed embodiment of (5-2)).
  • the lubricating oil retained in the oil retention space 90 can be fed into the oil feed passage 17a through the first inner passage 617s and the second inner passage 617t, to supply the sliding parts via the pin bearing horizontal oil-feed hole 17c and/or the upper bearing horizontal oil-feed hole 17e, whereby the interval from the point in time that the lubricating oil in the lower oil reservoir part P is depleted until lubricating oil can be supplied to sliding sections in the upper part of the crankshaft 617 is shortened.
  • a scroll compressor 701 provided with a crankshaft 717 having a first outer passage 717s and a second outer passage 717t through which the oil retention space 90 and the outside of the crankshaft 917 communicate with one another at a location above the communicating passage 91, and having a porous substance 790x packed into the interior of the oil retention space 90 (specifically, the porous substance 790x may be packed into the oil retention space 90 of the aforedescribed embodiment of (5-3)).
  • the lubricating oil retained in the oil retention space 90 can be supplied to sliding sections via the first outer passage 717s and/or the second outer passage 717t, prior to passing through the communicating passage 91 below, and then ascending within the oil feed passage 17a to be supplied to the sliding parts from the upper bearing horizontal oil-feed hole 17e and/or the pin bearing horizontal oil-feed hole 17c, thereby shortening the interval from the point in time that the lubricating oil in the lower oil reservoir part P is depleted until lubricating oil is supplied to sliding sections in the upper part of the crankshaft 717.
  • crankshaft 17 has the lower bearing horizontal oil-feed hole 17d, the upper bearing horizontal oil-feed hole 17e, and the pin bearing horizontal oil-feed hole 17c.
  • the crankshaft 817 of the scroll compressor 801 unlike the crankshaft 17 of the aforedescribed first embodiment, lacks the pin bearing horizontal oil-feed hole 17c, instead having a pin shaft groove part 17x formed by cutting on the vertical a part of the outer surface of the pin shaft part 17b at the diametrical outside end part thereof. By cutting away part of an outer peripheral section in an upper end section of the pin shaft part 17b, this pin shaft groove part 17x is configured as a groove part that is recessed diametrically inward, the recessed groove part extending so as to lead downward from the upper end of the pin shaft part 17b.
  • This scroll compressor 801 has a pin shaft supply path 817c formed between the pin shaft groove part 17x and the inner peripheral surface of the pin shaft bearing metal 87.
  • the embodiments there is no limitation of the embodiments to this particular arrangement; e.g., a range of 0.5-2.0 times the inside diameter of the oil feed passage 17a would be an acceptable range for the inside diameter of the oil retention space 90. It is preferable for the inside diameter of the oil retention space 90 to be such that the space has the capacity to retain lubricating oil in an amount necessary to compensate for a temporary abnormal condition encountered in cases of depleted lubricating oil in the lower oil reservoir part P.
  • the size of the inside diameter of the communicating passage 91 was described as being arbitrary.
  • the channel cross-sectional area of the communicating passage 91 could be made smaller, so as to slow the descent speed of the lubricating oil within the oil retention space 90 when an abnormal condition is encountered. In so doing, it is possible to ensure a supply of lubricating oil for a prolonged period during an abnormal condition.
  • the size of the inside diameter of the communicating passage 91 may be determined, as appropriate, in the light of factors such as the rotation frequency of the crankshaft 17 during normal operation, and the like.
  • the scroll compressor of the present invention is particularly useful, for example, as a scroll compressor having a crankshaft that extends in the vertical direction, and in which lubricating oil is stored in a lower end part.
  • Patent Literature 1 Japanese Laid-open Patent Application 2011-137523

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EP14836075.3A 2013-08-12 2014-08-04 Scroll compressor Withdrawn EP3034878A1 (en)

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JP2013167451A JP2015036525A (ja) 2013-08-12 2013-08-12 スクロール圧縮機
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US20160208803A1 (en) 2016-07-21
JP2015036525A (ja) 2015-02-23
CN105452666A (zh) 2016-03-30
WO2015022869A1 (ja) 2015-02-19

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