US20160208803A1 - Scroll compressor - Google Patents
Scroll compressor Download PDFInfo
- Publication number
- US20160208803A1 US20160208803A1 US14/911,459 US201414911459A US2016208803A1 US 20160208803 A1 US20160208803 A1 US 20160208803A1 US 201414911459 A US201414911459 A US 201414911459A US 2016208803 A1 US2016208803 A1 US 2016208803A1
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- US
- United States
- 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.)
- Abandoned
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
- F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
- F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/0042—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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/0042—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.
- the oil retention space 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 A longitudinal cross-sectional view of a scroll compressor according to a first embodiment, depicting a normal condition.
- FIG. 2 A longitudinal cross-sectional view of the scroll compressor according to the first embodiment, depicting depletion.
- FIG. 3 A fragmentary enlarged cross-sectional view of section X of FIG. 2 .
- FIG. 4 A schematic diagram showing a structure in the vicinity of the crankshaft bottom end
- FIG. 5 A fragmentary enlarged cross-sectional view according to another embodiment (5-1).
- FIG. 6 A fragmentary enlarged cross-sectional view of a scroll compressor according to another embodiment (5-2).
- FIG. 7 A fragmentary enlarged cross-sectional view of a scroll compressor according to another embodiment (5-3).
- FIG. 8 A fragmentary enlarged cross-sectional view of a scroll compressor according to another embodiment (5-4).
- FIG. 9 A fragmentary enlarged cross-sectional view of a scroll compressor according to another embodiment (5-5).
- FIG. 10 A fragmentary enlarged cross-sectional view of a scroll compressor according to another embodiment (5-6).
- FIG. 11 A fragmentary enlarged cross-sectional view of a scroll compressor according to another embodiment (5-7).
- 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 .
- a sealed dome type casing 10 of vertically elongated cylindrical shape
- a pin bearing part 22 of vertically elongated cylindrical shape
- 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 that functions as a drive shaft
- an oil return guide 71 an oil return guide 71 .
- 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 shall part 17 b 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 26 c 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 26 c, 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 17 b 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 17 b from the outside in a diametrical direction.
- the upper bearing part 32 is configured from an upper inner peripheral section 23 a 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 17 h.
- the relationship of the upper hearing 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 28 a 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 28 a; 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 51 a 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 51 a 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 17 a 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.
- the discharge side of 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 17 a, 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 17 a 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 24 a, and a lap 24 b of spiral shape (involute shape) viewed from the bottom surface, formed extending downward from the bottom surface of the end plate 24 a.
- the end plate 24 a 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 51 a 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 has an end plate 26 a; a lap 26 b of spiral shape (involute shape) viewed from the top surface, formed extending to the upper surface side of the end plate 26 a; and a boss part 26 c 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 26 a.
- the present embodiment employs an inner drive moveable scroll.
- the boss part 26 c of the moveable scroll 26 covers from the outside in the diametrical direction the pin shaft part 17 b 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 26 b which extends upward from the moveable scroll 26 , is interleaved from the vertical direction with the lap 24 b which extends downward from the stationary scroll 24 , in such a way that the scrolls overlap in the diametrical direction.
- the lap 24 b of the stationary scroll 24 and the lap 26 b 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 17 b at the upper end of the crankshaft 17 is inserted into the boss part 26 c, to the inside thereof in the diametrical direction.
- the boss part 26 c which is linked to the pin shaft part 17 b 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 24 b of the stationary scroll 24 and the lap 26 b 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 17 a 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 26 c 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 23 a which is part of the upper bearing part 32 , is a section that corresponds to this cylindrical shape.
- This upper inner peripheral section 23 a, 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 17 b, 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 51 a 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 51 a, 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 17 b 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 17 b is inserted towards an inner peripheral space of the boss part 26 c 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 17 a In the interior of the crankshaft 17 are formed the oil feed passage 17 a extending in the axial direction of the crankshaft 17 , and the oil retention space 90 which is provided separately from the oil feed passage 17 a but which likewise extends in the axial direction of the crankshaft 17 .
- the pin shaft part 17 b of the crankshaft 17 In the pin shaft part 17 b of the crankshaft 17 , there is formed a pin bearing horizontal oil-feed hole 17 c which branches to extend out diametrically towards the outside from a point midway along the oil feed passage 17 a, and communicates in a diametrical direction with the pin shaft part 17 b. Via this the pin bearing horizontal oil-feed hole 17 c, lubricating oil is supplied to sliding sections between the inner peripheral surface of the boss part 26 c of the moveable scroll 26 and the outer peripheral surface of the pin shaft part 17 b.
- the discharge side of the volumetric pump 79 communicates with the lower end of the oil feed passage 17 a.
- 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 17 a.
- the upper end of the oil feed passage 17 a 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 17 c which branches to extend out diametrically towards the outside from a point midway along the oil feed passage 17 a, 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 17 c, to the sliding sections between the outer peripheral surface of the pin shaft part 17 b and the inner peripheral surface of the pin shaft bearing metal 87 disposed inside the boss part 26 c of the moveable scroll 26 .
- a lower bearing horizontal oil-feed hole 17 d which branches and extends towards the outside in a diametrical direction from a point midway along the oil feed passage 17 a, 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 beating 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 17 d.
- an upper bearing horizontal oil-feed hole 17 e which branches and extends towards the outside in a diametrical direction from a point midway along the oil feed passage 17 a, 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 17 b of the crankshaft 17 are supplied with oil via this upper bearing horizontal oil-feed hole 17 e.
- the axial center of the oil feed passage 17 a 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 17 a 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 17 a, and the oil is easily supplied upward.
- the oil retention space 90 like the oil feed passage 17 a, 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 17 a. 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 17 a. 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 17 a. As shown in FIG. 4 , a communication location B at which the communicating passage 91 and the oil feed passage 17 a communicate is located below the section where the lower bearing horizontal oil-feed hole 17 d branches off from the oil feed passage 17 a.
- 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 17 a 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 17 a.
- the pin shaft headspace 37 which is a space lying between the upper end surface of the pin shaft part 17 b of the distal end of the crankshaft 17 and the lower surface of the end plate 26 a of the moveable scroll 26
- 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 17 b 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 26 c of the moveable scroll 26 , are respectively formed in the interior of the boss part 26 c of the moveable scroll 26 .
- a portion of the lubricating oil supplied via the oil feed passage 17 a 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 Pin 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 ted 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 51 a 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 51 a, 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 17 a 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 17 a is supplied to the sliding section of the lower bearing part 27 via the lower bearing horizontal oil-feed hole 17 d.
- the lubricating oil ascending further up through the oil feed passage 17 a is supplied to the sliding section of the upper bearing part 32 via the upper bearing horizontal oil-feed hole 17 e.
- the lubricating oil ascending further up through the oil feed passage 17 a is supplied to the sliding section of the pin bearing part 22 through the pin bearing horizontal oil-feed hole 17 c.
- surplus oil in the pin shaft headspace 37 collects in the oil retention space 90 interior, from the open section at the upper end of the oil retention space 90 .
- the lubricating oil within the oil feed passage 17 a 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 17 a.
- the lubricating oil ascending within the oil feed passage 17 a is thereby supplied in respective fashion to the sliding section of the lower bearing part 27 via the lower bearing horizontal oil-feed hole 17 d, to the sliding section of the upper bearing part 32 via the upper bearing horizontal oil-feed hole 17 e, and to the sliding section of the pin bearing part 22 via the pin bearing horizontal oil-feed hole 17 c.
- 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 17 a, 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 17 b, so as to pass through the pin shaft part 17 b 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 17 a 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 317 s and a second internal passage 317 t through which the oil retention space 90 and the oil feed passage 17 a communicate with one another at locations above the communicating passage 91 , as shown in FIG. 6 .
- This first internal passage 317 s is disposed at a location at the same height as the pin bearing horizontal oil-feed hole 17 c, so as to pass through between the oil retention space 90 and the oil feed passage 17 a.
- the second internal passage 317 t is disposed at a location at the same height as the upper bearing horizontal oil-feed hole 17 e, so as to pass through between the oil retention space 90 and the oil feed passage 17 a.
- the lubricating oil retained within the oil retention space 90 is fed to the oil feed passage 17 a via the first internal passage 317 s and/or the second internal passage 317 t, rather than via the communicating passage 91 through which the oil retention space 90 and the oil feed passage 17 a 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 317 s at the oil feed passage 17 a side thereof may be a location lower than the heightwise location of the pin bearing horizontal oil-feed hole 17 c and higher than the heightwise location of the upper bearing horizontal oil-feed hole 17 e, rather than the same as the heightwise location of the in bearing horizontal oil-feed hole 17 c.
- the lubricating oil that has been fed into the oil feed passage 17 a via the first internal passage 317 s can ascend somewhat within the oil feed passage 17 a, and be fed as far as the pin bearing horizontal oil-feed hole 17 c.
- the heightwise location of the end of the second internal passage 317 t at the oil feed passage 17 a side thereof may be a location above the heightwise location of the lower bearing horizontal oil-feed hole 17 d and below the heightwise location of the upper bearing horizontal oil-feed hole 17 e, rather than the same as the heightwise location of the upper bearing horizontal oil-feed hole 17 e.
- the lubricating oil that has been fed into the oil feed passage 17 a via the second internal passage 317 t can ascend somewhat within the oil feed passage 17 a, and be fed as far as the upper bearing horizontal oil-feed hole 17 e.
- the passage cross-sectional area of the first internal passage 317 s (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 17 a ) may be configured to be smaller than the passage cross-sectional area of the in bearing horizontal oil-feed hole 17 c. 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 317 s 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 317 t (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 17 a ) may be configured to be smaller than the passage cross-sectional area of the upper bearing horizontal oil-feed hole 17 e. 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 317 t 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 417 s and a second outer passage 417 t 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 417 s 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 17 c.
- the second outer passage 417 t 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 17 e.
- the passage cross-sectional area of the first outer passage 417 s (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 17 c. 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 417 s can be minimized, and the lubricating oil can he easily retained within the oil retention space 90 .
- the passage cross-sectional area of the second outer passage 417 t (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 17 e. In an doing, the extent to which the lubricating oil in the oil retention space 90 interior leaks to the outside via the second outer passage 417 t can he 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 in bearing part 22 and/or the sliding section of the upper bearing part 32 via the first outer passage 417 s and the second outer passage 417 t, instead of via the communicating passage 91 through which the oil feed passage 17 a 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 590 x 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 590 x e.g., polyethylene or polypropylene could be used.
- the form of the porous substance 590 x 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 617 s and a second inner passage 617 t through which the oil retention space 90 and the oil feed passage 17 a communicate with one another at a location above the communicating passage 91 , and having a porous substance 690 x packed into the interior of the oil retention space 90 (specifically, the porous substance 690 x 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 17 a through the first inner passage 617 s and the second inner passage 617 t, to supply the sliding parts via the pin bearing horizontal oil-feed hole 17 c and/or the upper bearing horizontal oil-feed hole 17 e, 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 717 s and a second outer passage 717 t 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 790 x packed into the interior of the oil retention space 90 (specifically, the porous substance 790 x 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 717 s and/or the second outer passage 717 t, prior to passing through the communicating passage 91 below, and then ascending within the oil feed passage 17 a to be supplied to the sliding parts from the upper bearing horizontal oil-feed hole 17 e and/or the pin bearing horizontal oil-feed hole 17 c, 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 17 d, the upper bearing horizontal oil-feed hole 17 e, and the pin bearing horizontal oil-feed hole 17 c.
- 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 17 c, instead having a pin shaft groove part 17 x formed by cutting on the vertical a part of the outer surface of the pin shaft part 17 b 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 17 b, this pin shaft groove part 17 x 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 17 b.
- This scroll compressor 801 has a pin shaft supply path 817 c formed between the pin shaft groove part 17 x 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 17 a 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.
- Porous substance member for reducing lubricating oil descent speed
- Porous substance member for reducing lubricating oil descent speed
- Second outer passage (hole of small passage cross-sectional area)
- Porous substance member for reducing lubricating oil descent speed
Abstract
A scroll compressor includes a casing, a compression mechanism accommodated within the casing, a motor arranged to rotatably drive the crankshaft, an oil feed pump arranged to feed lubricating oil upward, a lower oil reservoir disposed in a space below the oil feed pump to hold lubricating oil, an oil feed path and an oil retention space. The compression mechanism has a stationary scroll and a moveable scroll forming a compression chamber. The crankshaft is linked to the moveable scroll. The oil feed passage is formed so as to extend in an axial direction within an 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 interior of the crankshaft separately from the oil feed passage and communicates with the oil feed passage.
Description
- 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.
- In a scroll compressor of this design, 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.
- In such cases, there will be an insufficient amount of lubricating oil supplied to the sliding sections, which, though temporary, poses a risk that seizing and/or abnormal friction will occur in the sliding sections and/or periphery thereof, causing damage to the sections in question.
- With the foregoing in view, it is an object of the present invention to provide a scroll compressor with which it is possible to reduce damage in sliding sections, even under conditions in which the lubricating oil in the lower oil reservoir part has been 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.
- In this scroll compressor, 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
- 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, the lubricating oil retained within the oil retention space is fed into the oil feed passage, thereby making it possible to supply oil on a temporary basis via the oil feed passage.
- 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.
- In this scroll compressor, 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.
- In this scroll compressor, because the oil retention space communicates with the discharge side of the oil feed pump via a space within the oil feed passage, 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.
- In this scroll compressor, 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
- With this scroll compressor, centrifugal force acting on the lubricating oil retained within the oil retention space can be held to an even lower level, even while the crankshaft is rotating. For this reason, even while the crankshaft is rotating, the lubricating oil is easily fed to the oil feed passage below via the section communicating with the oil feed passage. Additionally, because the oil retention space is disposed at the axial center of the crankshaft, decline in strength of the crankshaft can be minimized.
- 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.
- There are no particular limitations as to 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.
- With this scroll compressor, it is possible for the vicinity of the outer periphery of the crankshaft to be supplied with lubricating oil via a supply passage extending from the interior of the oil feed passage.
- 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.
- With this scroll compressor, 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.
- With this scroll compressor, 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.
- With this scroll compressor, it is possible to minimize friction in sliding sections between the upper 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 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.
- With this scroll compressor, it is possible to minimize friction in sliding sections between the cylindrical part of the moveable scroll 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 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.
- With this scroll compressor, because the inside diameter of the oil retention space is 0.5-2.0 times the inside diameter of the oil feed passage, it is possible for an ample quantity of lubricating oil to be retained within the oil retention space.
- 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.
- With this scroll compressor, because the upper end of the oil retention space is open, lubricating oil that, of the lubricating oil fed upwardly from the oil feed passage, represents surplus oil present above the crankshaft may be easily retained. In so doing, it is possible for lubricating oil for use in abnormal circumstances to be retained within the oil retention space in a more reliable manner.
- 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.
- With this scroll compressor, the speed of descent of the lubricating oil in the oil retention space can be limited. In so doing, the time required from the point in time at which the lubricating oil in the lower oil reservoir part is depleted until the lubricating oil in the oil retention space is also depleted can be extended. In so doing, it is possible to continuously supply oil to sliding sections of the crankshaft for a longer period, starting at the point in time at which the lubricating oil in the lower oil reservoir part is depleted.
- With the scroll compressor according to the first aspect of the present invention, under abnormal circumstances such as when the lubricating oil in the lower oil reservoir part has been depleted, it is possible for oil to be supplied on a temporary basis via the oil feed passage, by feeding the lubricating oil retained within the oil retention space to the oil feed passage.
- With the scroll compressor according to the second aspect of the present invention, the oil feed passage can be easily fed lubricating oil from the oil retention space.
- With 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.
- With the scroll compressor according to the fourth aspect of the present invention, it is possible for the lubricating oil to be easily retained in the interior.
- With the scroll compressor according to the fifth aspect of the present invention, 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.
- With the scroll compressor according to the sixth aspect of the present invention, it is possible for the vicinity of the outer periphery of the crankshaft to be supplied with lubricating oil via the supply passage extending from the interior of the oil feed passage.
- With the scroll compressor according to the seventh aspect of the present invention, it is possible to induce the flow of lubricating oil to branch into the horizontal oil-feed hole at a point midway along the oil feed passage and supplied to outer peripheral sections of the crankshaft, without being fed as far as the upper end of the oil feed passage.
- With the scroll compressor according to the eighth aspect of the present invention, it is possible to minimize leakage of lubricating oil to the outside from inside the oil retention space, and to easily retain the lubricating oil in a space in the interior of the oil retention space.
- With the scroll compressor according to the ninth aspect of the present invention, it is possible to minimize friction in the sliding section between the lower bearing part and the crankshaft.
- With the scroll compressor according to the tenth aspect of the present invention, 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 a sliding section above the crankshaft.
- With the scroll compressor according to the eleventh aspect of the present invention, it is possible to minimize friction in sliding sections between the upper bearing part and the crankshaft.
- With the scroll compressor according to the twelfth aspect of the present invention, it is possible to minimize friction in sliding sections between the cylindrical part of the moveable scroll and the crankshaft.
- With the scroll compressor according to the thirteenth aspect of the present invention, it is possible for an ample quantity of lubricating oil to be retained within the oil retention space.
- With the scroll compressor according to the fourteenth aspect of the present invention, it is possible for lubricating oil for use in abnormal circumstances to be retained within the oil retention space in a more reliable manner.
- With the scroll compressor according to the fifteenth aspect of the present invention, it is possible to continuously supply oil to sliding sections of the crankshaft for a longer period, starting at the point in time at which the lubricating oil in the lower oil reservoir part is depleted.
- [
FIG. 1 ] A longitudinal cross-sectional view of a scroll compressor according to a first embodiment, depicting a normal condition. - [
FIG. 2 ] A longitudinal cross-sectional view of the scroll compressor according to the first embodiment, depicting depletion. - [
FIG. 3 ] A fragmentary enlarged cross-sectional view of section X ofFIG. 2 . - [
FIG. 4 ] A schematic diagram showing a structure in the vicinity of the crankshaft bottom end, - [
FIG. 5 ] A fragmentary enlarged cross-sectional view according to another embodiment (5-1). - [
FIG. 6 ] A fragmentary enlarged cross-sectional view of a scroll compressor according to another embodiment (5-2). - [
FIG. 7 ] A fragmentary enlarged cross-sectional view of a scroll compressor according to another embodiment (5-3). - [
FIG. 8 ] A fragmentary enlarged cross-sectional view of a scroll compressor according to another embodiment (5-4). - [
FIG. 9 ] A fragmentary enlarged cross-sectional view of a scroll compressor according to another embodiment (5-5). - [
FIG. 10 ] A fragmentary enlarged cross-sectional view of a scroll compressor according to another embodiment (5-6). - [
FIG. 11 ] A fragmentary enlarged cross-sectional view of a scroll compressor according to another embodiment (5-7). - An embodiment of the scroll compressor will be described below, while referring to the drawings.
-
FIG. 1 shows a longitudinal cross-sectional view of ascroll compressor 1 during normal operation.FIG. 2 shows a longitudinal cross-sectional view of thescroll compressor 1 when depleted.FIG. 3 shows a fragmentary enlarged cross-sectional view of section X ofFIG. 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. Thisscroll 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, apin bearing part 22, anupper bearing part 32, alower bearing part 27, amotor 16, avolumetric pump 79, anintake pipe 19, adischarge pipe 20, acompression mechanism part 15, acrankshaft 17 that functions as a drive shaft, and anoil return guide 71. These constituent components of thescroll compressor 1 are each described in detail below. - The
casing 10 is a vertically elongated sealed container, and has a generally cylindrical-shapedbarrel casing part 11, a bowl-shapedupper wall part 12 welded airtightly to an upper end part of thebarrel casing part 11, and a bowl-shapedlower wall part 13 welded airtightly to a lower end part of thebarrel casing part 11. Thecasing 10 mainly accommodates thecompression mechanism part 15, which compresses the refrigerant gas, and themotor 16, which is arranged below thecompression mechanism part 15. Thecompression mechanism part 15 and themotor 16 are linked by thecrankshaft 17, which is arranged extending in a vertical direction within thecasing 10. Between thecompression mechanism part 15 and themotor 16 is a high-pressure space 18. - The
pin bearing part 22 supports a pin shall part 17 b at the upper end of thecrankshaft 17, from the outside in a diametrical direction. Thepin bearing part 22 is constituted by aboss part 26 c that extends in a cylindrical profile axially downward from the vicinity of the center of amoveable scroll 26, discussed below, and pinshaft bearing metal 87 fitted against the inner peripheral surface to the diametrical inside of theboss part 26 c, and is disposed such that the inner peripheral surface of the pinshaft bearing metal 87 contacts the outer peripheral surface of thepin shaft part 17 b of thecrankshaft 17. - (1-3) Upper Bearing Part
- The
upper bearing part 32 is located somewhat above the center within thecasing 10, and supports a section of thecrankshaft 17 below thepin shaft part 17 b from the outside in a diametrical direction. Theupper bearing part 32 is configured from an upper innerperipheral section 23 a situated at the diametrical inside of anupper bearing housing 23, discussed below, andupper bearing metal 88 fitted against the inner peripheral surface at the diametrical inside of theupper bearing part 32. The inner peripheral surface of theupper bearing metal 88 is disposed so as to contact the outer peripheral surface thecrankshaft 17 in a section thereof that lies below the pin shaft part 17 h. The relationship of theupper hearing part 32 to the upper bearinghousing 23 is discussed below. - The
lower bearing part 27 is located in a lower part within thecasing 10, and supports a lower section of thecrankshaft 17 from the outside in a diametrical direction. Thelower bearing part 27 is configured from a lower innerperipheral section 28 a situated to the diametrical inside of thelower bearing housing 28, andlower bearing metal 89 that fits against the inner peripheral surface at the diametrical inside of the lower innerperipheral section 28 a; and is moreover disposed such that the inner peripheral surface of thelower bearing metal 89 contacts the outer peripheral surface of the lower section of thecrankshaft 17. Thelower bearing housing 28 is arranged in a lower space below themotor 16. This lower bearinghousing 28 is fixed at a diametrical outside end part thereof to an inner peripheral section of thebarrel casing part 11. - The
motor 16 is configured mainly from a ring-shapedstator 51 fixed to an inner wall surface of thecasing 10, and arotor 52 accommodated rotatably to the inside of thestator 51, with a slight gap (air gap passage) therebetween. - Copper wire is wound about the
stator 51 at top and bottom, forming acoil end 53. An upper end of thecoil end 53 of thestator 51 is arranged such that the heightwise position is substantially the same as that of the bottom end of theupper bearing part 32 of the upper bearinghousing 23, discussed below. The outer peripheral surface of thestator 51 is provided at several locations, spaced apart by prescribed distances in the circumferential direction, with groove-shaped core cutparts 51 a that extend in a plumb vertical direction from an upper end surface to a lower end surface of thestator 51. These core cutparts 51 a are configured as motor cooling passages that extend in the vertical direction between the inner peripheral side of thebarrel casing part 11 and the outer peripheral side of thestator 51. As shown inFIG. 1 , an oilreturn flow channel 74 through which it is possible for the lubricating oil to descend is formed between the outer peripheral side of thestator 51 and the inner peripheral side of themain casing 10. - The
rotor 52 is drive-coupled to themoveable scroll 26 of thecompression mechanism part 15 via thecrankshaft 17, which is arranged at the axial center of thebarrel 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 anoil feed passage 17 a of thecrankshaft 17 is disposed at the lower end of thecrankshaft 17. In the present first embodiment, a “trochoid pump” is employed as thevolumetric 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. - As shown in
FIG. 4 , the discharge side of thisvolumetric pump 79 is arranged so as to communicate with the lower end of thecrankshaft 17. A space communicating with the discharge side of thevolumetric pump 79 at the lower end of thecrankshaft 17 communicates in a diametrical direction with a lower end section of theoil feed passage 17 a, and is configured to suction up the lubricating oil by rotating in tandem with thecrankshaft 17. - By employing a 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. Specifically, by drawing up the lubricating oil in the lower oil reservoir part P with thevolumetric pump 79 in a manner free of limitation to a state of driving by thecompression 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 thelower bearing part 27 via theoil feed passage 17 a of thecrankshaft 17 and theoil retention space 90 is possible. - The
intake pipe 19 is a line for guiding the refrigerant of the refrigerant circuit to thecompression mechanism part 15, and is fitted airtightly into theupper wall part 12 of thecasing 10. Theintake 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 astationary scroll 24. - The
discharge pipe 20 is a line for discharging the refrigerant within thecasing 10 to outside thecasing 10, and is fitted airtightly into thebarrel casing part 11 of thecasing 10. An end of thisdischarge pipe 20 is disposed at a location so as to protrude further to the inside from the inner peripheral surface of thebarrel casing part 11. - As shown in
FIG. 1 , thecompression mechanism part 15 is configured mainly from thestationary scroll 24 which is arranged airtightly above the upper bearinghousing 23, discussed below, and themoveable scroll 26 which is interleaved with thestationary scroll 24. - Each of the constituent parts of this
compression mechanism part 15 will be described in detail below. - As shown in
FIG. 1 , thestationary scroll 24 has a flat plate-shapedend plate 24 a, and alap 24 b of spiral shape (involute shape) viewed from the bottom surface, formed extending downward from the bottom surface of theend plate 24 a. - The
end plate 24 a is perforated in an axial direction by adischarge port 41 at the approximate axial center of the top surface side. Thisdischarge port 41 communicates with acompression chamber 40, discussed below. Thedischarge port 41 is formed so as to extend in the vertical direction. - In a portion further towards the top from the
discharge port 41 at the upper surface side of theend plate 24 a is formed an expandedrecess part 42 that extends upward and expands further in a horizontal direction than the upper end opening section of thedischarge port 41. Acover 44 is affixed to the expandedrecess part 42 so as to provide closure from above. A space enclosed in the vertical direction by the expandedrecess part 42 and thecover 44 forms amuffler space 45. Thismuffler space 45 functions as an expansion chamber for silencing operating noise of thecompression mechanism part 15, A seal structure is employed between thestationary scroll 24 and thecover 44, to provide intimate contact through the agency of a gasket, not illustrated. - The refrigerant discharged from the
discharge port 41 of thecompression mechanism part 15 passes through themuffler space 45, passes downward through an access passage (not illustrated) which is formed near the outer periphery of the upper bearinghousing 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 51 a until reaching a space near the underside of themotor 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). - As shown in
FIG. 1 , the moveable scroll has anend plate 26 a; alap 26 b of spiral shape (involute shape) viewed from the top surface, formed extending to the upper surface side of theend plate 26 a; and aboss part 26 c which configures a pin bearing part for receiving the upper end of thecrankshaft 17, and which is formed so as to extend in a cylindrical profile to the lower surface side of theend plate 26 a. - While there is no particular limitation as to the type of the
moveable scroll 26, the present embodiment employs an inner drive moveable scroll. Theboss part 26 c of themoveable scroll 26 covers from the outside in the diametrical direction thepin shaft part 17 b which configures the proximity of the upper end of thecrankshaft 17. In this way, themoveable scroll 26 and thecrankshaft 17 are rotatably linked. - The
lap 26 b, which extends upward from themoveable scroll 26, is interleaved from the vertical direction with thelap 24 b which extends downward from thestationary scroll 24, in such a way that the scrolls overlap in the diametrical direction. Here, thelap 24 b of thestationary scroll 24 and thelap 26 b of themoveable scroll 26 are interleaved in such a way that thecompression chamber 40 is formed between the contacting sections. - The
moveable scroll 26 is supported by the upper surface of the upper bearinghousing 23, in such a way as to prevent rotational motion. As mentioned above, thepin shaft part 17 b at the upper end of thecrankshaft 17 is inserted into theboss part 26 c, to the inside thereof in the diametrical direction. - Through rotary driving of the
crankshaft 17, theboss part 26 c, which is linked to thepin shaft part 17 b in such a way that rotary driving force is transmitted thereto, is acted upon by the force of thecrankshaft 17, and themoveable scroll 26 orbits without rotating within the upper bearinghousing 23. In the process, in association with the orbiting of themoveable scroll 26, thecompression chamber 40 formed by thelap 24 b of thestationary scroll 24 and thelap 26 b of themoveable scroll 26 becomes shorter in distance in the diametrical direction from thedischarge port 41, while advancing in the rotational advance direction, thereby contracting while the volume faces the center. In thescroll compressor 1 according to the present embodiment, the refrigerant gas is compressed in this manner. - Due to the above structure, the lubricating oil which has been pressurized by the
volumetric pump 79 ascends through theoil feed passage 17 a which penetrates the crankshaft 17 interior in the axial direction, feeding oil to thelower bearing part 27, theupper bearing part 32, and thepin bearing part 22, respectively, and is fed into apin shaft headspace 37 at the upper end of thecrankshaft 17, which is part of a linking space to the inside of the inner peripheral surface of theboss part 26 c of themoveable 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 thebarrel casing part 11 by pressure fitting. In so doing, the diametrical inside of thebarrel casing part 11 and the diametrical outside of the upper bearinghousing 23 are disposed in airtight intimate contact about their entire circumference. The interior of thecasing 10 is thereby partitioned into the high-pressure space 18 below the upper bearinghousing 23, and the low-pressure space 29 above the upper bearinghousing 23. Thestationary scroll 24 is affixed by fastening with a bolt (not illustrated) to the upper bearinghousing 23, so that the upper end surface of the latter is disposed in intimate contact against the lower end surface of thestationary scroll 24. - This upper bearing
housing 23 has a downwardly-recessedcrank chamber 31 at the center of the upper surface. A lower section of the upper bearinghousing 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 innerperipheral section 23 a, which is part of theupper bearing part 32, is a section that corresponds to this cylindrical shape. This upper innerperipheral section 23 a, and the round cylindrical upper bearingmetal 88 which is fitted into the diametrical inside thereof and shares the same axial direction, together configure theupper bearing part 32. The inner peripheral surface of this upper bearingmetal 88 rotatably supports a section of thecrankshaft 17 below thepin shaft part 17 b, from the outside in the diametrical direction. - In the upper bearing
housing 23 there is formed adiametrical oil passage 35 that extends diametrically outside through to reach the outer peripheral surface from the vicinity of the lower end of thecrank chamber 31. Lubricating oil which has been supplied into thecrank chamber 31 passes through thisdiametrical oil passage 35 and descends between theoil return guide 71, discussed below, and thecasing 10, descends through the gap between thebarrel casing part 11 and thestator 51, and is returned to the lower oil reservoir part P in the lower part of thecasing 10. - Further, in a section of the upper surface of the upper bearing
housing 23 situated diametrically to outside thecrank chamber 31, there is provided anannular sealing ring 86 for sealing off the section of high pressure to the inside in the area below themoveable scroll 26 and the section of low pressure to the outside in the area below themoveable scroll 26, in order to maintain high pressure in thecrank chamber 31 interior. - As mentioned above, the refrigerant discharged from the
discharge port 41 of thecompression mechanism part 15 passes through themuffler space 45, a portion thereof passes downward through specific one of the core cuts 51 a until reaching the space near the underside of themotor 16, and thereafter passes upward through a passage such as a different one of the core cuts 51 a, 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 thecasing 10 from thedischarge pipe 20. - The
crankshaft 17 is a drive shaft for transmitting the drive force of themotor 16 to thecompression mechanism part 15. - The
crankshaft 17 is rotatably supported inside thecasing 10 by theupper bearing part 32 of the upper bearinghousing 23, and thelower bearing part 27. A medial section of thecrankshaft 17 is linked concentrically to therotor 52 of themotor 16. - The
pin shaft part 17 b is disposed at the upper end of thecrankshaft 17, and positioned eccentrically from the medial section of thecrankshaft 17. Thepin shaft part 17 b is inserted towards an inner peripheral space of theboss part 26 c of themoveable scroll 26. In so doing, it is possible for themoveable scroll 26 to undergo revolutionary movement, through rotation of thecrankshaft 17 by the drive force of themotor 16. - In the interior of the
crankshaft 17 are formed theoil feed passage 17 a extending in the axial direction of thecrankshaft 17, and theoil retention space 90 which is provided separately from theoil feed passage 17 a but which likewise extends in the axial direction of thecrankshaft 17. In thepin shaft part 17 b of thecrankshaft 17, there is formed a pin bearing horizontal oil-feed hole 17 c which branches to extend out diametrically towards the outside from a point midway along theoil feed passage 17 a, and communicates in a diametrical direction with thepin shaft part 17 b. Via this the pin bearing horizontal oil-feed hole 17 c, lubricating oil is supplied to sliding sections between the inner peripheral surface of theboss part 26 c of themoveable scroll 26 and the outer peripheral surface of thepin shaft part 17 b. - The discharge side of the
volumetric pump 79 communicates with the lower end of theoil feed passage 17 a. Specifically, as shown inFIG. 4 , a space that communicates with the discharge side of thevolumetric pump 79 at the lower end of thecrankshaft 17 communicates in a diametrical direction with a lower end section of theoil feed passage 17 a. As shown inFIG. 3 , the upper end of theoil feed passage 17 a extends as far as the upper end section of thecrankshaft 17, and the upper end section is open vertically. In the aforedescribed manner, the interior of thepin shaft part 17 b of thecrankshaft 17, there is formed the pin bearing horizontal oil-feed hole 17 c which branches to extend out diametrically towards the outside from a point midway along theoil feed passage 17 a, and communicates as far as the near side of the inner peripheral surface of the pinshaft bearing metal 87 situated at the outside. The lubricating oil is supplied, via this pin bearing horizontal oil-feed hole 17 c, to the sliding sections between the outer peripheral surface of thepin shaft part 17 b and the inner peripheral surface of the pinshaft bearing metal 87 disposed inside theboss part 26 c of themoveable scroll 26. - In a section of the
crankshaft 17 that is supported by thelower bearing part 27, there is formed a lower bearing horizontal oil-feed hole 17 d which branches and extends towards the outside in a diametrical direction from a point midway along theoil feed passage 17 a, and extends to penetrate as far as the near side of the inner peripheral surface of thelower bearing metal 89 situated at the outside. Sliding sections between the inner peripheral surface of thelower beating metal 89 of thelower bearing part 27 and outer peripheral surface in the vicinity of the lower end of thecrankshaft 17 are supplied with oil via this lower bearing horizontal oil-feed hole 17 d. - In a section of the
crankshaft 17 that is supported by theupper bearing part 32, there is formed an upper bearing horizontal oil-feed hole 17 e which branches and extends towards the outside in a diametrical direction from a point midway along theoil feed passage 17 a, and extends to penetrate as far as the near side of the inner peripheral surface of theupper bearing metal 88 situated at the outside. Sliding sections between the inner peripheral surface of theupper bearing metal 88 of theupper bearing part 32 and the lower outer peripheral surface of thepin shaft part 17 b of thecrankshaft 17 are supplied with oil via this upper bearing horizontal oil-feed hole 17 e. - The axial center of the
oil feed passage 17 a is arranged at a different location than the axial center of the outer peripheral surface of thecrankshaft 17, Specifically, the axial center of theoil feed passage 17 a is eccentric in relation to the axial center with respect to the outer periphery of thecrankshaft 17. In so doing, during rotation of thecrankshaft 17, centrifugal force readily acts on the lubricating oil within theoil feed passage 17 a, and the oil is easily supplied upward. - The
oil retention space 90, like theoil feed passage 17 a, 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 thecrankshaft 17. Specifically, the axial center of theoil retention space 90 is arranged closer to the axial center of the outer peripheral surface of thecrankshaft 17 than is the axial center of theoil feed passage 17 a. In so doing, even during drive rotation of thecrankshaft 17, the lubricating oil present inside theoil 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 theoil retention space 90 does not communicate directly with the discharge side of thevolumetric pump 79, but rather communicates with the discharge side of thevolumetric pump 79 via a space inside theoil feed passage 17 a. In this way, the vicinity of the lower end of theoil retention space 90 is connected, via a communicatingpassage 91 extending in the diametrical direction, to the vicinity of the lower end of theoil feed passage 17 a. As shown inFIG. 4 , a communication location B at which the communicatingpassage 91 and theoil feed passage 17 a communicate is located below the section where the lower bearing horizontal oil-feed hole 17 d branches off from theoil feed passage 17 a. Unlike theoil feed passage 17 a, theoil retention space 90 of the present embodiment lacks a horizontal oil-feed hole configured to penetrate as far as the outer peripheral surface of thecrankshaft 17. Therefore, when the lubricating oil is fed towards the bottom of theoil feed passage 17 a from thevolumetric pump 79 through rotary driving of thecrankshaft 17, the lubricating oil collects within theoil retention space 90 via the communicatingpassage 91. As shown inFIG. 3 , the upper end of theoil retention space 90 extends as far as the upper end section of thecrankshaft 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 theoil retention space 90 is formed to an inside diameter equal to the inside diameter of theoil feed passage 17 a. - As shown in
FIG. 1 , thepin shaft headspace 37, which is a space lying between the upper end surface of thepin shaft part 17 b of the distal end of thecrankshaft 17 and the lower surface of theend plate 26 a of themoveable 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 thepin shaft part 17 b of the distal end of thecrankshaft 17 and the inner peripheral surface of the pinshaft bearing metal 87 disposed inside theboss part 26 c of themoveable scroll 26, are respectively formed in the interior of theboss part 26 c of themoveable scroll 26. A portion of the lubricating oil supplied via theoil feed passage 17 a in the crankshaft 17 interior is supplied between themoveable scroll 26 and thestationary scroll 24, via thepin shaft headspace 37. The pin shaftcircumferential space 38 is formed such that a diametrical width of about several tens of microns extends in the vertical direction. - As shown in
FIG. 1 , theoil return guide 71 is a member of thin metal plate shape, arranged below the diametrical outside of the upper bearinghousing 23 in a space above themotor 16, and is affixed to thebarrel casing part 11, forming a flow channel in relation to the inner peripheral face of thebarrel casing part 11. - This
oil return guide 71 guides the lubricating oil which has passed through thediametrical oil passage 35 formed in the upper bearinghousing 23, and extends in the diametrical direction into an upper end section of the oilreturn flow channel 74 situated between the outer peripheral surface of thestator 51 and the inner peripheral surface of thebarrel casing part 11. - The lubricating oil guided into the upper end section of the oil
return flow channel 74 then descends through the oilreturn flow channel 74, and collects in the lower oil reservoir part Pin the lower part of thecasing 10. - Next, the operating behavior of the
scroll compressor 1 will be briefly described, while referring toFIG. 1 . - First, when driving of the
motor 16 starts, thecrankshaft 17 rotates, and themoveable scroll 26 performs orbiting operation without rotating. - In so doing, in the
compression mechanism part 15 which receives rotational force from thecrankshaft 17, the low-pressure refrigerant gas is suctioned through theintake pipe 19 and into thecompression chamber 40 from the peripheral edge side of thecompression chamber 40, and is compressed in association with the changing volume of thecompression 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 themuffler space 45 through thedischarge port 41, and thereafter flows downward through the access passage (not illustrated) of the upper bearinghousing 23, whereupon a portion of the flow is split off, flows in a circumferential direction along the inner peripheral surface of thebarrel casing part 11, and is ted 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 51 a formed in therotor 52 until reaching the space near the underside of themotor 16, and thereafter reverses course and passes upward through an airgap passage between a different one of the core cuts 51 a, thestator 51, and therotor 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 thecasing 10 through thedischarge pipe 20. - The refrigerant gas discharged to outside the
casing 10 is then circulated through the refrigerant circuit, and thereafter is again sucked into thecompression mechanism part 15 through theintake pipe 19, and compressed. - During driving of the
scroll compressor 1, the lubricating oil of lower oil reservoir part P in thecasing 10 interior is drawn up by the pumping action of thevolumetric pump 79, whereby the lubricating oil ascends through theoil feed passage 17 a of thecrankshaft 17. In the process, a portion of the lubricating oil is branched off via the communicatingpassage 91 and is stored in the interior of the oil retention space 90 (see the arrows inFIG. 1 ). Some of the lubricating oil ascending through theoil feed passage 17 a is supplied to the sliding section of thelower bearing part 27 via the lower bearing horizontal oil-feed hole 17 d. The lubricating oil ascending further up through theoil feed passage 17 a is supplied to the sliding section of theupper bearing part 32 via the upper bearing horizontal oil-feed hole 17 e. The lubricating oil ascending further up through theoil feed passage 17 a is supplied to the sliding section of thepin bearing part 22 through the pin bearing horizontal oil-feed hole 17 c. In the event that extra space is remaining within theoil retention space 90, surplus oil in thepin shaft headspace 37 collects in theoil retention space 90 interior, from the open section at the upper end of theoil retention space 90. - During normal operation in the above manner, within the space inside the
casing 10 of thescroll compressor 1, the refrigerant and the lubricating oil are separated, and the separated lubricating oil descends, to become stored in the lower oil reservoir part P. - Depending on the operating status of the refrigeration cycle, there may be instances in which separation of the lubricating oil is insufficient, and lubricating oil, entrained by the refrigerant passing through the
discharge pipe 20, flows to the outside of thecasing 10. In such cases, the amount of lubricating oil stored in the lower oil reservoir part P will progressively decrease. In the event that the lubricating oil in the lower oil reservoir part P becomes depleted, thevolumetric pump 79 will no longer be able to draw up lubricating oil. - When this occurs, the system goes from a state of normal operation in which the lubricating oil is pushed towards the
oil retention space 90 side from theoil feed passage 17 a side within the communicatingpassage 91, to an abnormal state in which this pushing flow ceases. - In this abnormal state, there is no flow of lubricating oil into the
oil retention space 90 through the communicatingpassage 91; moreover, because the axial center of theoil retention space 90 is at the same location as the axial center of the outer periphery of thecrankshaft 17, and the lubricating oil within theoil retention space 90 is largely unaffected by centrifugal forced produced during rotary driving of thecrankshaft 17, the lubricating oil within theoil retention space 90 starts to descend under its own weight. The lubricating oil having descended within theoil retention space 90 in this manner moves towards theoil feed passage 17 a side through the communicatingpassage 91, whereby the lubricating oil is supplied to theoil feed passage 17 a (see the arrows inFIG. 2 ). The lubricating oil within theoil feed passage 17 a now becomes susceptible to the action of centrifugal force produced by rotary driving of thecrankshaft 17, and therefore ascends within theoil feed passage 17 a. The lubricating oil ascending within theoil feed passage 17 a is thereby supplied in respective fashion to the sliding section of thelower bearing part 27 via the lower bearing horizontal oil-feed hole 17 d, to the sliding section of theupper bearing part 32 via the upper bearing horizontal oil-feed hole 17 e, and to the sliding section of thepin bearing part 22 via the pin bearing horizontal oil-feed hole 17 c. - With the
scroll compressor 1 according to the first embodiment, during normal operation when themotor 16 is driven and thecrankshaft 17 is rotatably driven, thevolumetric pump 79 is driven, whereby the lubricating oil stored in the lower oil reservoir part P is fed upward via theoil feed passage 17 a, and in so doing is supplied to the sliding section of thelower bearing part 27, the sliding section of theupper bearing part 32, the sliding section of thepin bearing part 22, and the sliding section near thecompression mechanism part 15 at the top, preventing seizing and the like of these sliding sections. - Additionally, during normal operation, lubricating oil can be stored to the
oil retention space 90. - Further, during abnormal circumstances in which the lubricating oil in the lower oil reservoir part P is depleted, the lubricating oil being stored in the
oil retention space 90 can be utilized to supply the sliding section of thelower bearing part 27, the sliding section of theupper bearing part 32, the sliding section of thepin bearing part 22, and the sliding section near thecompression mechanism part 15 at the top. In so doing, even during abnormal circumstances in which the lubricating oil in the lower oil reservoir part P is depleted, it is possible for the sliding parts to be supplied continuously until no oil is left within theoil 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. - In the preceding first embodiment, one embodiment of the present invention was described as an example.
- However, the present invention is not limited to this embodiment, and other embodiments resulting from appropriate modifications within the spirit of the present invention are included within the scope thereof. In the following embodiments, elements indicated by identical symbols are not described.
- (5-1)
- The preceding first embodiment described an example of a case in which the upper end of the
oil retention space 90 opens vertically. - However, there is no limitation of the embodiments to this particular arrangement, it being acceptable for a
scroll compressor 201 to have acrankshaft 217 formed so as to be provided with adiametrical section 96, as shown inFIG. 5 for example. - This
diametrical section 96 is produced by extending an upper section of theoil retention space 90 near thepin shaft part 17 b, so as to pass through thepin shaft part 17 b towards the outside in a diametrical direction, as far as an outside peripheral section thereof. Thisscroll compressor 201 affords working effects like those of the preceding embodiment. - (5-2)
- The preceding first embodiment described an example of a case in which the
oil retention space 90 and theoil feed passage 17 a in thecrankshaft 17 lack a communicating section in any section besides the communicatingpassage 91. - However, there is no limitation of the embodiments to this particular arrangement, it being acceptable for a
scroll compressor 301 to be provided, for example, with a first internal passage 317 s and a secondinternal passage 317 t through which theoil retention space 90 and theoil feed passage 17 a communicate with one another at locations above the communicatingpassage 91, as shown inFIG. 6 . - This first internal passage 317 s is disposed at a location at the same height as the pin bearing horizontal oil-
feed hole 17 c, so as to pass through between theoil retention space 90 and theoil feed passage 17 a. The secondinternal passage 317 t is disposed at a location at the same height as the upper bearing horizontal oil-feed hole 17 e, so as to pass through between theoil retention space 90 and theoil feed passage 17 a. - In so doing, in the event that the lubricating oil in the lower oil reservoir part P has been depleted, the lubricating oil retained within the
oil retention space 90 is fed to theoil feed passage 17 a via the first internal passage 317 s and/or the secondinternal passage 317 t, rather than via the communicatingpassage 91 through which theoil retention space 90 and theoil feed passage 17 a communicate at a point further down, and can thereby be supplied to the sliding section of thepin bearing part 22 and/or the sliding section of theupper bearing part 32. In so doing, 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 thecrankshaft 17 is shortened. - The heightwise location of the end of the first internal passage 317 s at the
oil feed passage 17 a side thereof may be a location lower than the heightwise location of the pin bearing horizontal oil-feed hole 17 c and higher than the heightwise location of the upper bearing horizontal oil-feed hole 17 e, rather than the same as the heightwise location of the in bearing horizontal oil-feed hole 17 c. In so doing, the lubricating oil that has been fed into theoil feed passage 17 a via the first internal passage 317 s can ascend somewhat within theoil feed passage 17 a, and be fed as far as the pin bearing horizontal oil-feed hole 17 c. - Moreover, the heightwise location of the end of the second
internal passage 317 t at theoil feed passage 17 a side thereof may be a location above the heightwise location of the lower bearing horizontal oil-feed hole 17 d and below the heightwise location of the upper bearing horizontal oil-feed hole 17 e, rather than the same as the heightwise location of the upper bearing horizontal oil-feed hole 17 e. In so doing, the lubricating oil that has been fed into theoil feed passage 17 a via the secondinternal passage 317 t can ascend somewhat within theoil feed passage 17 a, and be fed as far as the upper bearing horizontal oil-feed hole 17 e. - The passage cross-sectional area of the first internal passage 317 s (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 theoil feed passage 17 a) may be configured to be smaller than the passage cross-sectional area of the in bearing horizontal oil-feed hole 17 c. In so doing, the extent to which the lubricating oil in theoil retention space 90 interior leaks to the outside via the first internal passage 317 s can be minimized, and the lubricating oil can be easily retained within theoil retention space 90. - The passage cross-sectional area of the second
internal passage 317 t (the smallest area among areas perpendicular to the direction of passage in the case where the lubricating oil passes from theoil retention space 90 to theoil feed passage 17 a) may be configured to be smaller than the passage cross-sectional area of the upper bearing horizontal oil-feed hole 17 e. In so doing, the extent to which the lubricating oil in theoil retention space 90 interior leaks to the outside via the secondinternal passage 317 t can be minimized, and the lubricating oil can be easily retained within theoil retention space 90. - (5-3)
- The first embodiment described an example of a case in which the
crankshaft 17 lacks a hole for communication between the interior of theoil retention space 90 and the outside of thecrankshaft 17. - However, there is no limitation of the embodiments to this particular arrangement, and a
scroll compressor 401 could, for example, be provided with acrankshaft 417 having a firstouter passage 417 s and a secondouter passage 417 t through which theoil retention space 90 and the outside of thecrankshaft 417 communicate with one another at locations above the communicatingpassage 91, as shown inFIG. 7 . - This first
outer passage 417 s extends to pass through from the interior of theoil retention space 90 to the outside of thecrankshaft 417, at the same heightwise location as the pin bearing horizontal oil-feed hole 17 c. The secondouter passage 417 t extends to pass through from the interior of theoil retention space 90 to the outside of thecrankshaft 417, at the same heightwise location as the upper bearing horizontal oil-feed hole 17 e. - The passage cross-sectional area of the first
outer passage 417 s (in the case where the lubricating oil passes from theoil retention space 90 to the outside of thecrankshaft 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 17 c. In so doing, the extent to which the lubricating oil in theoil retention space 90 interior leaks to the outside via the firstouter passage 417 s can be minimized, and the lubricating oil can he easily retained within theoil retention space 90. - The passage cross-sectional area of the second
outer passage 417 t (in the case where the lubricating oil passes from theoil retention space 90 to the outside of thecrankshaft 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 17 e. In an doing, the extent to which the lubricating oil in theoil retention space 90 interior leaks to the outside via the secondouter passage 417 t can he minimized, and the lubricating oil can be easily retained within theoil retention space 90. - By means of the above configuration, in cases in which the lubricating oil in the lower oil reservoir part P has been depleted, the lubricating oil retained in the
oil retention space 90 can be supplied to the sliding section of the in bearingpart 22 and/or the sliding section of theupper bearing part 32 via the firstouter passage 417 s and the secondouter passage 417 t, instead of via the communicatingpassage 91 through which theoil feed passage 17 a and theoil retention space 90 communicate further towards the bottom. In so doing, 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 thecrankshaft 417 is shortened. - (5-4)
- The preceding embodiment described an example of a case in which t e or of the
oil retention space 90 of thecrankshaft 17 is a hollow space. - However, there is no limitation of the embodiments to this particular arrangement; for example, also it being acceptable for a
scroll compressor 501 provided with acrankshaft 517 in which the interior of theoil retention space 90 is filled with aporous substance 590 x, as shown inFIG. 8 . - With the
oil retention space 90 of thiscrankshaft 517, theporous substance 590 x 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. There are no particular limitations as to the material of theporous substance 590 x; e.g., polyethylene or polypropylene could be used. Moreover, there is no limitation as to the form of theporous substance 590 x, but a sponge-like form is preferred. - By disposing the
porous substance 590 x in this manner, a low flow rate of lubricating oil flowing through the communicatingpassage 91 from theoil retention space 90 to theoil feed passage 17 a can be maintained, making it possible to extend the time over which the lubricating oil retained in theoil retention space 90 is continuously supplied, starting at the point in time when the lubricating oil in the lower oil reservoir part P is depleted, In so doing, even when the lubricating oil in the lower oil reservoir part P is depleted, the feed of oil to the sliding sections via the lower bearing horizontal oil-feed hole 17 d and/or the upper bearing horizontal oil-feed hole 17 e and/or the pin bearing horizontal oil-feed hole 17 c is readily maintained until the refrigerant flowing through the refrigerant circuit and entraining the lubricating oil is returned to within thescroll compressor 501. - It would also be acceptable to use fibrous members that give rise to resistance to movement of the lubricating oil, in place of the
porous substance 590 x of the aforedescribed embodiment. - (5-5)
- In another embodiment, it being acceptable for a
scroll compressor 601 provided with acrankshaft 617 like that shown inFIG. 9 for example, having a firstinner passage 617 s and a secondinner passage 617 t through which theoil retention space 90 and theoil feed passage 17 a communicate with one another at a location above the communicatingpassage 91, and having aporous substance 690 x packed into the interior of the oil retention space 90 (specifically, theporous substance 690 x may be packed into theoil retention space 90 of the aforedescribed embodiment of (5-2)). - In this case, as in the aforedescribed embodiment of (5-2), the lubricating oil retained in the
oil retention space 90 can be fed into theoil feed passage 17 a through the firstinner passage 617 s and the secondinner passage 617 t, to supply the sliding parts via the pin bearing horizontal oil-feed hole 17 c and/or the upper bearing horizontal oil-feed hole 17 e, 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 thecrankshaft 617 is shortened. - Additionally, as in the aforedescribed embodiment of (5-4), it will be possible to extend the time until no lubricating oil is left within the
oil retention space 90. - (5-6)
- In another embodiment, e.g., as shown in
FIG. 10 , it being acceptable for ascroll compressor 701 provided with acrankshaft 717 having a firstouter passage 717 s and a secondouter passage 717 t through which theoil retention space 90 and the outside of the crankshaft 917 communicate with one another at a location above the communicatingpassage 91, and having aporous substance 790 x packed into the interior of the oil retention space 90 (specifically, theporous substance 790 x may be packed into theoil retention space 90 of the aforedescribed embodiment of (5-3)). - In this case, as in the aforedescribed embodiment of (5-3), the lubricating oil retained in the
oil retention space 90 can be supplied to sliding sections via the firstouter passage 717 s and/or the secondouter passage 717 t, prior to passing through the communicatingpassage 91 below, and then ascending within theoil feed passage 17 a to be supplied to the sliding parts from the upper bearing horizontal oil-feed hole 17 e and/or the pin bearing horizontal oil-feed hole 17 c, 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 thecrankshaft 717. - Additionally, as in the aforedescribed embodiment of (5-4), it will be possible to extend the time until no lubricating oil is left within the
oil retention space 90. - (5-7)
- The aforedescribed embodiment described an example in which the
crankshaft 17 has the lower bearing horizontal oil-feed hole 17 d, the upper bearing horizontal oil-feed hole 17 e, and the pin bearing horizontal oil-feed hole 17 c. - However, there is no limitation of the embodiments to this particular arrangement; e.g., as shown in
FIG. 11 , it being acceptable for ascroll compressor 801 provided with acrankshaft 817 that lacks these horizontal oil-feed holes. - The
crankshaft 817 of thescroll compressor 801, unlike thecrankshaft 17 of the aforedescribed first embodiment, lacks the pin bearing horizontal oil-feed hole 17 c, instead having a pinshaft groove part 17 x formed by cutting on the vertical a part of the outer surface of thepin shaft part 17 b at the diametrical outside end part thereof. By cutting away part of an outer peripheral section in an upper end section of thepin shaft part 17 b, this pinshaft groove part 17 x 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 thepin shaft part 17 b. Thisscroll compressor 801 has a pinshaft supply path 817 c formed between the pinshaft groove part 17 x and the inner peripheral surface of the pinshaft bearing metal 87. - Part of the lubricating oil which has been fed into the
pin shaft headspace 37 via theoil feed passage 17 a of thecrankshaft 817 is then fed to the pinshaft supply path 817 c through a gap between the inside of theboss part 26 c of themoveable scroll 26 and thepin shaft part 17 b of thecrankshaft 817. In so doing, it is possible for the lubricating oil to easily enter the pinshaft supply path 817 c, providing lubrication between the outer peripheral surface of the pin shaft part 17 h and the inner peripheral surface of the pinshaft bearing metal 87. - In this way, effects comparable to those of the aforedescribed embodiment can be obtained, even in the case of adopting the
crankshaft 817 lacking the pin bearing horizontal oil-feed hole 17 c penetrating in the diametrical direction through thepin shaft part 17 b of the aforedescribed first embodiment. - (5-8)
- The aforedescribed embodiment described an example of a case of “slide bearings,” in which the three bearings, i.e., the
pin bearing part 22, theupper bearing part 32, and thelower bearing part 27, are configured such that the inner peripheral surface of the pinshaft bearing metal 87, the inner peripheral surface of theupper bearing metal 88, and the inner peripheral surface of thelower bearing metal 89 contact the outer peripheral surface of thecrankshaft 17 at their respective heightwise locations. - However, there is no limitation of the embodiments to this particular arrangement; e.g., a configuration in which at least any one of these three bearings is a rolling bearing would be acceptable.
- Effects comparable to those of the aforedescribed embodiment can be obtained with such a scroll compressor as well.
- (5-9)
- The aforedescribed embodiment described an example of a case in which the inside diameter of the
oil retention space 90 and the inside diameter of theoil feed passage 17 a are equal. - However, 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 17 a would be an acceptable range for the inside diameter of theoil retention space 90. It is preferable for the inside diameter of theoil 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. - (5-10)
- In the aforedescribed first embodiment, the size of the inside diameter of the communicating
passage 91 was described as being arbitrary. - However, there is no limitation of the embodiments to this particular arrangement; for example, 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 theoil 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 thecrankshaft 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.
- 1, 201, 301, 401, 501, 601, 701, 801, 901: Scroll compressor
- 15: Compression mechanism part
- 16: Motor
- 17, 217, 317, 417, 517, 617, 717, 817, 917: Crankshaft
- 17 a: Oil feed passage
- 17 b: Pin shaft part
- 17 c: Pin shaft bearing horizontal oil-feed hole (supply hole, horizontal oil-feed hole, upper horizontal oil-feed hole)
- 17 d: Lower bearing horizontal oil-feed hole (supply hole, horizontal oil-feed hole)
- 17 e: Upper bearing horizontal oil-feed hole (supply hole, horizontal oil-feed hole)
- 24: Stationary scroll
- 26: Moveable scroll
- 26 c: Boss part (cylindrical part)
- 27: Lower bearing part
- 32: Upper bearing part
- 37: Pin shaft headspace
- 38: Pin shaft circumferential space
- 40: Compression chamber
- 79: Volumetric pump
- 90: Oil retention space
- 91: Communicating passage
- 96: Diametrical section
- 317 s: First inner passage (upper communicating passage)
- 317 t: Second inner passage (upper communicating passage)
- 417 s: First outer passage (hole of small passage cross-sectional area)
- 417 t: Second outer passage (hole of small passage cross-sectional area)
- 590 x: Porous substance (member for reducing lubricating oil descent speed)
- 617 s: First inner passage (upper communicating passage)
- 617 t: Second inner passage (upper communicating passage)
- 690 x: Porous substance (member for reducing lubricating oil descent speed)
- 717 s: First outer passage (hole of small passage cross-sectional area)
- 717 t: Second outer passage (hole of small passage cross-sectional area)
- 790 x: Porous substance (member for reducing lubricating oil descent speed)
- 917 c: Pin shaft supply path (supply path)
- B: Communication location
- P: Lower oil reservoir part
-
Patent Literature 1 - Japanese Laid-open Patent Application 2011-137523
Claims (18)
1. A scroll compressor comprising:
a casing;
a compression mechanism accommodated within the casing, the compression mechanism having a stationary scroll and a moveable scroll forming a compression chamber in relation to the stationary scroll;
a crankshaft linked to the moveable scroll;
a motor or arranged to rotatably drive the crankshaft;
an oil feed pump arranged to feed lubricating oil upward;
a lower oil reservoir disposed in a space below the oil feed pump to hold lubricating oil;
an oil feed passage formed so as to extend in an axial direction within an interior of the crankshaft and communicating at a lower end with a discharge side of the oil feed pump; and
an oil retention space formed so as to extend in an axial direction within the interior of the crankshaft separately from the oil feed passage and communicating with the oil feed passage.
2. The scroll compressor according to claim 1 , wherein
the oil feed passage and the oil retention space communicate via a communicating passage disposed in the interior of the crankshaft.
3. The scroll compressor according to claim 1 , 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.
4. The scroll compressor according to claim 1 , wherein
the oil feed passage, the crankshaft, and the oil retention space are each cylindrical in shape, and
an axial center of the oil retention space is disposed at a location closer to an axial center of the crankshaft with respect to an outer periphery thereof, than an axial center of the oil feed passage.
5. The scroll compressor according to claim 4 , wherein
the axial center of the oil retention space is disposed at a location identical to the location of the axial center of the crankshaft with respect to the outer periphery thereof.
6. The scroll compressor according to claim 1 , further comprising
a supply passage disposed such that it is possible to supply lubricating oil towards an outer periphery of the crankshaft from an interior of the oil feed passage.
7. The scroll compressor according to claim 6 , 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.
8. The scroll compressor according to claim 7 , 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 an interior of the oil retention space to the outer periphery of the crankshaft and has a smaller passage cross-sectional area than the horizontal oil-feed hole.
9. The scroll compressor according to claim 7 , further comprising:
an upper bearing part supporting the crankshaft from a circumferential direction; and
a lower bearing part supporting the crankshaft from a circumferential direction, at a point below the upper bearing part,
the horizontal oil-feed hole having a lower bearing horizontal oil-feed hole that extends towards the lower bearing part from within the oil feed passage, and
the oil retention space and the oil feed passage communicating at a location below a location at which the lower bearing horizontal oil-feed hole branches from the oil feed passage.
10. The scroll compressor according to claim 9 , further comprising
an upper communicating passage providing 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 communicating at a location below the upper communicating passage.
11. The scroll compressor according to claim 7 , further comprising:
an upper bearing part supporting the crankshaft from a circumferential direction; and
a lower bearing part supporting the crankshaft from a circumferential direction, at a point below the upper bearing part,
the horizontal oil-feed hole having an upper bearing horizontal oil-feed hole that extends towards an inner peripheral surface of the upper bearing part from within the oil feed passage.
12. The scroll compressor according to claim 7 , wherein
the moveable scroll has a cylindrical part covering an upper end of the crankshaft from the circumferential direction, and
the horizontal oil-feed hole has an upper horizontal oil-feed hole that extends towards an inner peripheral surface of the cylindrical part from within the oil feed passage.
13. The scroll compressor according to any of claims 4 , wherein
an inside diameter of the oil retention space is 0.5-2.0 times an inside diameter of the oil feed passage.
14. The scroll compressor according to claim 1 , wherein
the oil retention space is open at an upper end.
15. The scroll compressor according to claim 1 , further comprising
a member arranged in an interior of the oil retention space to limit a descent speed of the lubricating oil within the oil retention space.
16. The scroll compressor according to claim 2 , 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.
17. The scroll compressor according to claim 2 , wherein
the oil feed passage, the crankshaft, and the oil retention space are each cylindrical n shape, and
an axial center of the oil retention space is disposed at a location closer to an axial center of the crankshaft with respect to an outer periphery thereof than an axial center of the oil feed passage.
18. The scroll compressor according to claim 3 , wherein
the oil feed passage, the crankshaft, and the oil retention space are each cylindrical in shape, and
an axial center of the oil retention space is disposed at a location closer to an axial center of the crankshaft with respect to an outer periphery thereof than an axial center of the oil feed passage.
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2013167451A JP2015036525A (en) | 2013-08-12 | 2013-08-12 | Scroll compressor |
JP2013-167451 | 2013-08-12 | ||
PCT/JP2014/070476 WO2015022869A1 (en) | 2013-08-12 | 2014-08-04 | Scroll compressor |
Publications (1)
Publication Number | Publication Date |
---|---|
US20160208803A1 true US20160208803A1 (en) | 2016-07-21 |
Family
ID=52468256
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US14/911,459 Abandoned US20160208803A1 (en) | 2013-08-12 | 2014-08-04 | Scroll compressor |
Country Status (5)
Country | Link |
---|---|
US (1) | US20160208803A1 (en) |
EP (1) | EP3034878A1 (en) |
JP (1) | JP2015036525A (en) |
CN (1) | CN105452666A (en) |
WO (1) | WO2015022869A1 (en) |
Cited By (13)
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US10294942B2 (en) * | 2014-12-12 | 2019-05-21 | Daikin Industries, Ltd. | Compressor |
CN111749899A (en) * | 2019-03-26 | 2020-10-09 | 艾默生环境优化技术有限公司 | Compressor with oil distribution member |
US10801495B2 (en) | 2016-09-08 | 2020-10-13 | Emerson Climate Technologies, Inc. | Oil flow through the bearings of a scroll compressor |
US10907633B2 (en) | 2012-11-15 | 2021-02-02 | Emerson Climate Technologies, Inc. | Scroll compressor having hub plate |
US10954940B2 (en) | 2009-04-07 | 2021-03-23 | Emerson Climate Technologies, Inc. | Compressor having capacity modulation assembly |
US10962008B2 (en) | 2017-12-15 | 2021-03-30 | Emerson Climate Technologies, Inc. | Variable volume ratio compressor |
US10995753B2 (en) | 2018-05-17 | 2021-05-04 | Emerson Climate Technologies, Inc. | Compressor having capacity modulation assembly |
US11022119B2 (en) | 2017-10-03 | 2021-06-01 | Emerson Climate Technologies, Inc. | Variable volume ratio compressor |
US11125233B2 (en) * | 2019-03-26 | 2021-09-21 | Emerson Climate Technologies, Inc. | Compressor having oil allocation member |
US11655813B2 (en) | 2021-07-29 | 2023-05-23 | Emerson Climate Technologies, Inc. | Compressor modulation system with multi-way valve |
US11680568B2 (en) | 2018-09-28 | 2023-06-20 | Emerson Climate Technologies, Inc. | Compressor oil management system |
US11846287B1 (en) | 2022-08-11 | 2023-12-19 | Copeland Lp | Scroll compressor with center hub |
US11965507B1 (en) | 2022-12-15 | 2024-04-23 | Copeland Lp | Compressor and valve assembly |
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US20200025199A1 (en) | 2018-07-17 | 2020-01-23 | Air Squared, Inc. | Dual drive co-rotating spinning scroll compressor or expander |
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US11898557B2 (en) * | 2020-11-30 | 2024-02-13 | Air Squared, Inc. | Liquid cooling of a scroll type compressor with liquid supply through the crankshaft |
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JPH0311188A (en) * | 1989-06-09 | 1991-01-18 | Toshiba Corp | Compressor |
JP2616094B2 (en) * | 1990-02-14 | 1997-06-04 | ダイキン工業株式会社 | Scroll compressor |
JPH03242487A (en) * | 1990-02-16 | 1991-10-29 | Mitsubishi Electric Corp | Scroll type compressor |
JP3635732B2 (en) * | 1995-09-13 | 2005-04-06 | 松下電器産業株式会社 | Scroll compressor |
US5885066A (en) * | 1997-02-26 | 1999-03-23 | Matsushita Electric Industrial Co., Ltd. | Scroll compressor having oil bores formed through the crank shaft |
JP2000179481A (en) * | 1998-12-14 | 2000-06-27 | Hitachi Ltd | Scroll type compressor |
JP3843333B2 (en) * | 2002-09-11 | 2006-11-08 | 株式会社日立製作所 | Scroll fluid machinery |
FR2885966B1 (en) * | 2005-05-23 | 2011-01-14 | Danfoss Commercial Compressors | SPIRAL REFRIGERATING COMPRESSOR |
JP2011137523A (en) * | 2009-12-28 | 2011-07-14 | Daikin Industries Ltd | Rotary shaft and compressor |
CN102878081B (en) * | 2011-07-14 | 2016-05-04 | 艾默生环境优化技术(苏州)有限公司 | Rotary compressor |
JP2013137002A (en) * | 2011-12-28 | 2013-07-11 | Daikin Industries Ltd | Scroll compressor |
-
2013
- 2013-08-12 JP JP2013167451A patent/JP2015036525A/en active Pending
-
2014
- 2014-08-04 US US14/911,459 patent/US20160208803A1/en not_active Abandoned
- 2014-08-04 CN CN201480044293.1A patent/CN105452666A/en active Pending
- 2014-08-04 WO PCT/JP2014/070476 patent/WO2015022869A1/en active Application Filing
- 2014-08-04 EP EP14836075.3A patent/EP3034878A1/en not_active Withdrawn
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US11635078B2 (en) | 2009-04-07 | 2023-04-25 | Emerson Climate Technologies, Inc. | Compressor having capacity modulation assembly |
US10954940B2 (en) | 2009-04-07 | 2021-03-23 | Emerson Climate Technologies, Inc. | Compressor having capacity modulation assembly |
US10907633B2 (en) | 2012-11-15 | 2021-02-02 | Emerson Climate Technologies, Inc. | Scroll compressor having hub plate |
US11434910B2 (en) | 2012-11-15 | 2022-09-06 | Emerson Climate Technologies, Inc. | Scroll compressor having hub plate |
US10294942B2 (en) * | 2014-12-12 | 2019-05-21 | Daikin Industries, Ltd. | Compressor |
US10801495B2 (en) | 2016-09-08 | 2020-10-13 | Emerson Climate Technologies, Inc. | Oil flow through the bearings of a scroll compressor |
US11022119B2 (en) | 2017-10-03 | 2021-06-01 | Emerson Climate Technologies, Inc. | Variable volume ratio compressor |
US10962008B2 (en) | 2017-12-15 | 2021-03-30 | Emerson Climate Technologies, Inc. | Variable volume ratio compressor |
US11754072B2 (en) | 2018-05-17 | 2023-09-12 | Copeland Lp | Compressor having capacity modulation assembly |
US10995753B2 (en) | 2018-05-17 | 2021-05-04 | Emerson Climate Technologies, Inc. | Compressor having capacity modulation assembly |
US11680568B2 (en) | 2018-09-28 | 2023-06-20 | Emerson Climate Technologies, Inc. | Compressor oil management system |
US11125233B2 (en) * | 2019-03-26 | 2021-09-21 | Emerson Climate Technologies, Inc. | Compressor having oil allocation member |
CN111749899A (en) * | 2019-03-26 | 2020-10-09 | 艾默生环境优化技术有限公司 | Compressor with oil distribution member |
US11655813B2 (en) | 2021-07-29 | 2023-05-23 | Emerson Climate Technologies, Inc. | Compressor modulation system with multi-way valve |
US11879460B2 (en) | 2021-07-29 | 2024-01-23 | Copeland Lp | Compressor modulation system with multi-way valve |
US11846287B1 (en) | 2022-08-11 | 2023-12-19 | Copeland Lp | Scroll compressor with center hub |
US11965507B1 (en) | 2022-12-15 | 2024-04-23 | Copeland Lp | Compressor and valve assembly |
Also Published As
Publication number | Publication date |
---|---|
CN105452666A (en) | 2016-03-30 |
EP3034878A1 (en) | 2016-06-22 |
WO2015022869A1 (en) | 2015-02-19 |
JP2015036525A (en) | 2015-02-23 |
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Legal Events
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STCB | Information on status: application discontinuation |
Free format text: EXPRESSLY ABANDONED -- DURING EXAMINATION |