US20200284257A1 - Scroll compressor - Google Patents

Scroll compressor Download PDF

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Publication number
US20200284257A1
US20200284257A1 US16/751,422 US202016751422A US2020284257A1 US 20200284257 A1 US20200284257 A1 US 20200284257A1 US 202016751422 A US202016751422 A US 202016751422A US 2020284257 A1 US2020284257 A1 US 2020284257A1
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United States
Prior art keywords
rotary shaft
bearing
scroll
gap
journal
Prior art date
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Abandoned
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US16/751,422
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English (en)
Inventor
Sangbaek PARK
Jungsun Choi
Cheolhwan Kim
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LG Electronics Inc
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LG Electronics Inc
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Publication date
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Assigned to LG ELECTRONICS INC. reassignment LG ELECTRONICS INC. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: CHOI, JUNGSUN, KIM, CHEOLHWAN, PARK, SANGBAEK
Publication of US20200284257A1 publication Critical patent/US20200284257A1/en
Abandoned legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/02—Arrangements of bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/008—Hermetic pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/10—Sliding-contact bearings for exclusively rotary movement for both radial and axial load
    • F16C17/102—Sliding-contact bearings for exclusively rotary movement for both radial and axial load with grooves in the bearing surface to generate hydrodynamic pressure
    • F16C17/105—Sliding-contact bearings for exclusively rotary movement for both radial and axial load with grooves in the bearing surface to generate hydrodynamic pressure with at least one bearing surface providing angular contact, e.g. conical or spherical bearing surfaces
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/26—Systems consisting of a plurality of sliding-contact bearings
    • 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
    • F04C2210/00—Fluid
    • F04C2210/26—Refrigerants with particular properties, e.g. HFC-134a
    • 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
    • F04C2230/00—Manufacture
    • F04C2230/60—Assembly methods
    • F04C2230/602—Gap; Clearance
    • 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
    • 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
    • F04C2240/52—Bearings for assemblies with supports on both sides
    • 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
    • F04C2240/60—Shafts
    • 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
    • F04C2240/60—Shafts
    • F04C2240/601—Shaft flexion
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2210/00—Working fluid
    • F05B2210/10—Kind or type
    • F05B2210/14—Refrigerants with particular properties, e.g. HFC-134a
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2240/00—Components
    • F05B2240/50—Bearings

Definitions

  • the present invention relates to a compressor having a structure for compensating for eccentricity of a rotary shaft caused by a driving load.
  • a compressor is applied to a vapor compression type refrigeration cycle (hereinafter referred to simply as a refrigeration cycle) such as a refrigerator or an air conditioner.
  • the compressor compresses the refrigerant to provide work necessary for heat exchange in the refrigeration cycle.
  • Compressors can be divided into reciprocating compressors, rotary compressors, and scroll compressors according to how the refrigerant is compressed.
  • the reciprocating compressor is a system in which the volume of the compression space is varied while the piston reciprocates in the cylinder.
  • the rotary compressor compresses the refrigerant while the rolling piston pivotally moves using the rotating force of the drive unit.
  • the scroll compressor is a compressor in which an orbiting scroll is pivotably engaged with a fixed scroll fixed in the inner space of a hermetically sealed container to form a compression chamber between a fixed lap of the fixed scroll and an orbiting lap of the orbiting scroll.
  • the orbiting scroll rotates, the refrigerant is introduced, compressed and discharged as the volume of the compression chamber varies.
  • the scroll compressor is widely employed in an air conditioner or the like to compress a refrigerant because it can obtain a relatively high compression ratio as compared with other types of compressors and can obtain a stable torque as the intake, compression and discharge operations of the refrigerant are smoothly connected to each other.
  • Scroll compressors may be divided into an upper compression compressor or a lower compression compressor depending on the positions of the drive motor and the compression unit.
  • the compression unit In the upper compression compressor, the compression unit is positioned over the drive motor. In the lower compression compressor, the compression unit is positioned under the drive motor.
  • a discharge cover is hermetically coupled to the lower surface of the fixed scroll to prevent the refrigerant discharged from the compression chamber to the inner space of the casing from mixing with the oil contained in an oil reservoir space.
  • a conventional scroll compressor includes a case defining an outer appearance and having a discharge portion through which a refrigerant is discharged, a compression unit fixed to the case and configured to compress the refrigerant, and a drive unit is fixed to the case and configured to drive the compression unit, wherein the compression unit and the drive unit are connected by a rotary shaft rotatably coupled to the drive unit.
  • the compression unit includes a fixed scroll fixed to the case and having a fixed lap, and an orbiting scroll including an orbiting lap engaging with the fixed lap and driven by the rotary shaft.
  • the rotary shaft is eccentrically disposed, and the orbiting scroll is fixed to the eccentric rotary shaft and rotated. Thereby, the orbiting scroll revolves (orbits) around the fixed scroll to compress the refrigerant.
  • FIGS. 1A and 1B are sectional views showing the structure of a rotary shaft and a bearing of a conventional scroll compressor.
  • FIG. 1A is a view showing the shape of the bearing and the rotary shaft 226
  • FIG. 1B is a sectional view of FIG. 1A .
  • the rotary shaft and the bearing arranged around and rotatably coupled to the rotary shaft are engaged with the main frame and the fixed scroll, and thus the position thereof is fixed when the rotary shaft rotates. That is, the main frame and the fixed scroll are fixed so as not to rotate, and the bearing is interposed such that the rotary shaft can rotate with minimized friction.
  • the bearing may be designed to have an inner diameter slightly larger than the diameter of the rotary shaft such that the bearing and the rotary shaft are not in contact with each other but spaced apart from each other by a predetermined distance.
  • the scroll compressor includes an eccentric portion of the orbiting scroll for varying the volume of the compression space. The eccentric portion should have a sufficient size to sufficiently induce a volume change during rotation of the orbiting scroll. However, when the scroll compressor rotates occurs, a portion of the rotary shaft where the orbiting scroll is positioned tends to bend.
  • FIGS. 2A and 2B are views showing the rotary shaft and the bearing during rotation of the rotary shaft. As the orbiting scroll portion is eccentric, the rotary shaft is bent when it rotates as shown in FIG. 3 .
  • the present invention is directed to a scroll compressor that substantially obviates one or more problems due to limitations and disadvantages of the related art.
  • An object of the present invention is to provide a scroll compressor capable of addressing performance deterioration of a bearing resulting from eccentricity of a rotary shaft caused by a driving load.
  • a scroll compressor includes a casing, a drive motor arranged in an inner space of the casing, a rotary shaft coupled to the drive motor to rotate, a main frame arranged under the drive motor, a fixed scroll arranged under the main frame, an orbiting scroll engaging with the orbiting scroll to make an orbiting motion, the rotary shaft being inserted into and eccentrically coupled to the orbiting scroll, a first bearing positioned between the main frame and the rotary shaft, and a second bearing positioned between the fixed scroll and the rotary shaft, wherein a gap between the first and second bearings and the rotary shaft varies with a vertical position.
  • the rotary shaft may be disposed such that a center of mass thereof is displaced from a center of the scroll compressor to one side.
  • a portion of the rotary shaft between the first bearing and the second bearing may be asymmetric.
  • a gap between a lower portion of the first bearing and the rotary shaft may be wider than a gap between an upper portion of the first bearing and the rotary shaft.
  • a gap between an upper portion of the second bearing and the rotary shaft may be wider than a gap between a lower portion of the second bearing and the rotary shaft.
  • At least one of the first bearing and the second bearing may include a first ring having a first diameter and a second ring having a second diameter greater than the first diameter, wherein the first ring and the second ring may be arranged side by side in a vertical direction.
  • At least one of the first bearing and the second bearing may include an inclined surface on an inner side surface thereof, wherein a distance from the inclined surface to the rotary shaft may gradually change.
  • a main journal of the rotary shaft surrounded by the first bearing and a sub-journal of the rotary shaft surrounded by the second bearing may have a diameter varying with a vertical position.
  • FIGS. 1A to 2B are views showing a rotary shaft and a bearing of a conventional scroll compressor
  • FIG. 3 is a sectional view illustrating a scroll compressor according to an embodiment of the present invention.
  • FIGS. 4A to 6B are views showing the rotary shaft and bearing of the scroll compressor of the present invention.
  • FIG. 3 is a sectional view illustrating a scroll compressor according to an embodiment of the present invention.
  • a scroll compressor 1 may include a casing 210 having an inner space, a drive motor 220 provided in an upper portion of the inner space, a compression unit 200 disposed under the drive motor 220 , and a rotary shaft 226 configured to transmit the driving force of the drive motor 220 to the compression unit 200 .
  • the inner space of the casing 210 includes a first space V 1 , which is at an upper side of the drive motor 220 , and a second space V 2 , which is a space between the drive motor 220 and the compression unit 200 .
  • the space under the fixed scroll 250 may be divided into a third space V 3 (closed space) defined by a discharge cover 270 hermetically coupled to a lower portion of the fixed scroll 250 , and a fourth space V 4 (oil reservoir space), which is under the compression unit 200 .
  • the casing 210 may have, for example, a cylindrical shape.
  • the casing 210 may include a cylindrical shell 211 .
  • An upper shell 212 may be provided to an upper portion of the cylindrical shell 211 and a lower shell 214 may be provided to a lower portion of the cylindrical shell 211 .
  • the upper and lower shells 212 and 214 may be joined to the cylindrical shell 211 by, for example, welding to define an inner space.
  • the upper shell 212 may be provided with a refrigerant discharge pipe 216 .
  • the refrigerant discharge pipe 216 is a passage through which a compressed refrigerant discharged from the compression unit 200 to the second space V 2 and the first space V 1 is discharged to the outside.
  • an oil separator (not shown) for separating the oil mixed in the discharged refrigerant may be connected to the refrigerant discharge pipe 216 .
  • the lower shell 214 may define an oil reservoir space V 4 capable of storing oil.
  • the oil reservoir space V 4 may function as an oil chamber for supplying oil to the compression unit 200 to allow the compressor 1 to smoothly operate.
  • a refrigerant suction pipe 218 serving as a passage through which the refrigerant to be compressed is introduced may be provided on the side surface of the cylindrical shell 211 .
  • the refrigerant suction pipe 218 may extend to a compression chamber Si along the side of the fixed scroll 250 in a penetrating manner.
  • the drive motor 220 may be arranged in the upper operation of the casing 210 .
  • the drive motor 220 may include a stator 222 and a rotor 224 .
  • the stator 222 may be cylindrical, for example, and may be fixed to the casing 210 .
  • the stator 222 has a plurality of slots (not shown) formed on the inner circumferential surface thereof in a circumferential direction such that a coil 222 a is wound.
  • the outer circumferential surface of the stator 222 may be cut into a D-cut shape to form a refrigerant channel groove 212 a to allow the refrigerant or oil discharged from the compression unit 200 to pass therethrough.
  • the rotor 224 may be coupled to the inside of the stator 222 and may generate rotational power.
  • the rotary shaft 226 may be precisely fitted into the center of the rotor 224 such that the rotary shaft 226 can rotate together with the rotor 224 .
  • the rotational power generated by the rotor 224 is transmitted to the compression unit 200 through the rotary shaft 226 .
  • the compression unit 200 is arranged under the drive motor 220 , may include a fixed scroll 250 coupled to the casing 210 , an orbiting scroll 240 coupled with the rotary shaft 226 and engaged with the fixed scroll 250 to form a compression chamber, and a main frame 230 configured to accommodate the orbiting scroll 240 and seated on the fixed scroll 250 to form an outer appearance of the compression unit 200 .
  • the compression unit 200 may further include an Oldham ring 150 arranged between the main frame 230 and the orbiting scroll 240 to prevent the orbiting scroll 240 from rotating on the axis thereof
  • the main frame 230 may be provided under the drive motor 220 and form the top of the compression unit 200 .
  • the main frame 230 may include a frame head plate 232 (hereinafter referred to as a first head plate) having a substantially circular shape, and a frame bearing 232 (hereinafter referred to as a first bearing) disposed at the center of the first head plate 232 and penetrated by the rotary shaft 226 , and a frame sidewall portion 231 (hereinafter referred to as a first sidewall portion) protruding downward from an outer circumferential portion of the first head plate 232 .
  • a frame head plate 232 hereinafter referred to as a first head plate
  • a frame bearing 232 hereinafter referred to as a first bearing
  • the outer circumferential portion of the first sidewall portion 231 may be in contact with the inner circumferential surface of the cylindrical shell 211 , and the lower end of the first sidewall portion 231 may be in contact with the upper end of a fixed scroll sidewall portion 255 , which will be described later.
  • the first sidewall portion 231 may be provided with a frame discharge hole 231 a (hereinafter referred to as a first discharge hole) which penetrates the first sidewall portion 231 in the axial direction and forms a refrigerant passage.
  • the inlet of the first discharge hole 231 a may be connected to the outlet of a fixed scroll discharge hole 256 b, which will be described later, and the outlet of the first discharge hole 231 a may be connected to the second space V 2 .
  • the first bearing 232 a may protrude from the upper surface of the first head plate 232 toward the drive motor 220 .
  • the first bearing 232 a may be provided with a first rotation portion through which a main journal 226 c of the rotary shaft 226 , which will be described later, is arranged so as to be supported.
  • the first bearing 232 a through which the main journal 226 c of the rotary shaft 226 is rotatably inserted and supported, may be formed at the center of the main frame 230 in the axial direction.
  • An oil pocket 232 b for collecting oil discharged from a gap between the first bearing 232 a and the rotary shaft 226 may be formed in the upper surface of the first head plate 232 .
  • the oil pocket 232 b may be engraved on the upper surface of the first head plate 232 and be formed in an annular shape along the outer circumferential surface of the first bearing 232 a.
  • a back pressure chamber S 2 may be formed on the bottom surface (i.e., the lower surface) of the main frame 230 to define a space together with the fixed scroll 250 and the orbiting scroll 240 such that t the orbiting scroll 240 is supported by the pressure in the space.
  • the back pressure chamber S 2 may be an intermediate pressure area (i.e., an intermediate pressure chamber) and an oil supply passage 226 a provided in the rotary shaft 226 may be at a higher pressure than the back pressure chamber S 2 .
  • the space enclosed by the rotary shaft 226 , the main frame 230 , and the orbiting scroll 240 may be a high-pressure area.
  • a back pressure seal 280 may be provided between the main frame 230 and the orbiting scroll 240 to distinguish the high pressure area from the intermediate pressure area S 2 .
  • the back pressure seal 280 may serve as, for example, a sealing member.
  • the main frame 230 may be coupled with the fixed scroll 250 to define a space in which the orbiting scroll 240 can be pivotably arranged. That is, this structure may be configured to surround the rotary shaft 226 such that rotational power can be transmitted to the compression unit 200 via the rotary shaft 226 .
  • the fixed scroll 250 which forms the first scroll, may be coupled to the bottom surface of the main frame 230 .
  • the fixed scroll 250 may be arranged under the main frame 230 .
  • the fixed scroll 250 may include a fixed scroll head plate (second head plate) 254 having a substantially circular shape, a fixed scroll sidewall portion 254 protruding upward from the outer circumferential portion of the second head plate 254 , a fixed lap 251 protruding from the upper surface of the second head plate 254 and meshing (i.e., engaging) with an orbiting lap 241 of the orbiting scroll 240 , which will be described later, to form the compression chamber S 1 , and a fixed scroll bearing accommodation portion 252 (hereinafter referred to as a second bearing accommodation portion) formed at the center of the back surface (i.e., lower surface) of the second head plate 254 and penetrated by the rotary shaft 226 .
  • a fixed scroll bearing accommodation portion 252 hereinafter referred to as a second bearing accommodation portion
  • the second head plate 254 may be provided with a discharge port 253 for guiding the compressed refrigerant from the compression chamber S 1 to the inner space of the discharge cover 270 . Further, the position of the discharge port 253 may be set in consideration of a required discharge pressure or the like.
  • the discharge port 253 is arranged to face the lower shell 214 . Accordingly, the discharge cover 270 for accommodating the discharged refrigerant and guiding the refrigerant to a fixed scroll discharge hole 256 b, which will be described later, so as not to be mixed with oil may be coupled to the bottom surface (i.e., lower surface) of the fixed scroll 250 .
  • the discharge cover 270 may be hermetically coupled to the bottom surface of the fixed scroll 250 to separate the refrigerant discharge passage from the oil reservoir space V 4 .
  • the discharge cover 270 may be provided with a through hole (not shown) through which an oil feeder 271 , which is coupled to a sub-journal 226 g of the rotary shaft 226 and submerged in the oil reservoir space V 4 of the casing 210 , is arranged.
  • the discharge cover 270 is also referred to as a muffler, and a detailed description thereof will be given later.
  • the outer circumferential portion of the second sidewall portion 255 may be in contact with the inner circumferential surface of the cylindrical shell 211 and the upper end portion of the second sidewall portion 255 may be in contact with the lower end portion of the first sidewall portion 231 .
  • the second sidewall portion 255 may be provided with a fixed scroll discharge hole 256 b (hereinafter referred to as a second discharge hole) penetrating the second sidewall portion 255 in the axial direction to form a refrigerant passage together with the first discharge hole 231 a.
  • a second discharge hole penetrating the second sidewall portion 255 in the axial direction to form a refrigerant passage together with the first discharge hole 231 a.
  • the second discharge hole 256 b may be formed so as to correspond to the first discharge hole 231 a.
  • the inlet of the second discharge hole 256 b may be connected to the inner space of the discharge cover 270 and the outlet of the second discharge hole 256 b may be connected to the inlet of the first discharge hole 231 a.
  • the second discharge hole 256 b and the first discharge hole 231 a may be formed to connect the third space V 3 and the second space V 2 such that the refrigerant discharged from the compression chamber S 1 into the inner space of the discharge cover 270 is guided to the second space V 2 .
  • the second sidewall 255 may be provided with a refrigerant suction pipe 218 connected to the suction side of the compression chamber S 1 .
  • the refrigerant suction pipe 218 may be arranged spaced apart from the second discharge hole 256 b.
  • the second bearing 252 may protrude from the lower surface of the second head plate 254 toward the oil reservoir space V 4 .
  • a second rotation portion may be provided in the second bearing 252 such that a sub journal 226 g of the rotary shaft 226 , which will be described later, is inserted into and supported by the second rotation portion.
  • the lower end portion of the second bearing 252 may be bent toward the center of the shaft to support the lower end of the sub-journal 226 g of the rotary shaft 226 to form a thrust bearing surface.
  • the orbiting scroll 240 which is formed as the second scroll, may be arranged between the main frame 230 and the fixed scroll 250 .
  • the orbiting scroll 240 may be coupled to the rotary shaft 226 to form a pair of two compression chambers S 1 between the fixed scroll 250 and the orbiting scroll 240 while making an orbiting motion.
  • the orbiting scroll 240 may include an orbiting scroll head plate 245 (hereinafter referred to as a third head plate) having a substantially circular shape, an orbiting lap 254 protruding from the lower surface of the third head plate 245 and engaged with the fixed lap 251 , and a rotary shaft coupling portion 242 provided at the center of the third head plate 245 and rotatably coupled to an eccentric portion 226 f of the rotary shaft 226 , which will be described later.
  • a third head plate having a substantially circular shape
  • an orbiting lap 254 protruding from the lower surface of the third head plate 245 and engaged with the fixed lap 251
  • a rotary shaft coupling portion 242 provided at the center of the third head plate 245 and rotatably coupled to an eccentric portion 226 f of the rotary shaft 226 , which will be described later.
  • the outer circumferential portion of the third head plate 245 may be located at the upper end portion of the second sidewall portion 255 and the lower end portion of the orbiting lap 241 may be in close contact with the upper surface of the second head plate 254 so as to be supported by the fixed scroll 250 .
  • the outer circumferential portion of the rotary shaft coupling portion 242 is connected to the orbiting lap 241 to form the compression chamber Si together with the fixed lap 251 during the compression operation.
  • the fixed lap 251 and the orbiting lap 241 may be formed in an involute shape, or may be formed in various other shapes.
  • the involute shape refers to a curve corresponding to a trajectory drawn by an end of a thread when the thread wound around a base circle having an arbitrary radius is released.
  • the eccentric portion 226 f of the rotary shaft 226 may be inserted into the rotary shaft coupling portion 242 .
  • the eccentric portion 226 f inserted into the rotary shaft coupling portion 242 may overlap the orbiting lap 241 or the fixed lap 251 in the radial direction of the compressor.
  • the radial direction may refer to a direction (i.e., the lateral direction) perpendicular to the axial direction (i.e., the vertical direction). More specifically, the radial direction may refer to a direction extending inward from the outside outward from the inside with respect to the rotatory shaft.
  • the repulsive force of the refrigerant and the compressive force may be applied to the same plane with respect to the third head plate 245 , and may thus be canceled to a certain degree.
  • the rotary shaft 226 may be coupled to the drive motor 220 and be provided with an oil supply passage 226 a for guiding the oil contained in the oil reservoir space V 4 of the casing 210 upward.
  • the upper portion of the rotary shaft 226 may be press-fitted to the center of the rotor 224 , and the lower portion thereof may be coupled to the compression unit 200 and supported in the radial direction.
  • the rotary shaft 226 may transmit the rotational power of the drive motor 220 to the orbiting scroll 240 of the compression unit 200 .
  • the orbiting scroll 240 eccentrically coupled to the rotary shaft 226 makes an orbiting movement with respect to the fixed scroll 250 .
  • the main journal 226 c may be formed at a lower portion of the rotary shaft 226 so as to be inserted into the first bearing 232 a of the main frame 230 and radially supported.
  • the sub journal 226 g may be formed at the lower portion of the main journal 226 c so as to be inserted into the second bearing 252 of the fixed scroll 250 and radially supported.
  • the eccentric portion 226 f may be formed between the main journal 226 c and the sub journal 226 g so as to be inserted into and coupled to the rotary shaft coupling portion 242 of the orbiting scroll 240 .
  • the main journal 226 c and the sub-journal 226 g may be coaxially arranged so as to have the same axial center.
  • the eccentric portion 226 f may be arranged so as to be eccentric in the radial direction with respect to the main journal 226 c or the sub-journal 226 g.
  • the eccentric portion 226 f may have an outer diameter less than the outer diameter of the main journal 226 c and larger than an outer diameter of the sub-journal 226 g .
  • the rotary shaft 226 may be easily coupled through the respective bearing accommodation portions 232 a and 252 and the rotary shaft coupling portion 242 .
  • the eccentric portion 226 f may not be integrated with the rotary shaft 226 but may be formed using a separate bearing.
  • the outer diameter of the sub-journal 226 g may not be less than the outer diameter of the eccentric portion 226 f, and the rotation axis 226 may be inserted into and coupled to the respective bearing accommodation portions 232 a and 252 and the rotary shaft coupling portion 242 .
  • An oil supply passage 226 a for supplying the oil from the oil reservoir space V 4 to the outer circumferential surfaces of the rotary portions 226 c and 226 g and the outer circumferential surface of the eccentric portion 226 f may be formed in the rotary shaft 226 .
  • the rotary portions 226 c and 226 g and the eccentric portion 226 f of the rotary shaft 226 may be provided with oil holes 228 a, 228 b, 228 d, and 228 e extending from the oil supply passage 226 a to the outer circumferential surfaces in a penetrating manner.
  • the oil guided upward through the oil supply passage 226 a may be discharged through the oil holes 228 a, 228 b, 228 d, and 228 e and supplied to the bearing surface or the like.
  • An oil feeder 271 for pumping the oil filling the oil reservoir space V 4 may be coupled to the lower end of the rotary shaft 226 , that is, the lower end of the sub-journal 226 g.
  • the oil feeder 271 may include an oil supply pipe 273 inserted into and coupled to the oil supply passage 226 a of the rotary shaft 226 , and an oil intake member 274 inserted into the oil supply pipe 273 to suction the oil.
  • the oil supply pipe 273 may be arranged through the through hole of the discharge cover 270 so as to be submerged in the oil reservoir space V 4 , and the oil intake member 274 may function like a propeller.
  • a trochoid pump (not shown) may be provided in the sub journal 226 g or the discharge cover 270 in place of the oil feeder 271 to forcibly pump the oil contained in the oil reservoir space V 4 upward.
  • the scroll compressor according to the embodiment of the present invention may further include a first sealing member (not shown) for sealing the gap between the upper end of the main journal 226 c and the upper end of the main frame 230 , and a second sealing member (not shown) for sealing the gap between the lower end of the sub-journal 226 g and the lower end of the fixed scroll 250 .
  • the oil may be prevented from flowing out of the compression unit 200 along the bearing surface, thereby realizing a differential-pressure oil supply structure and preventing reverse flow of the refrigerant.
  • the rotor 224 or the rotary shaft 226 may be coupled with a balance weight 227 for suppressing noise vibration.
  • the balance weight 227 may be arranged in a space between the drive motor 220 and the compression unit 200 , that is, the second space V 2 .
  • the rotary shaft 226 coupled to the rotor 224 of the drive motor 220 begins to rotate. Then, the orbiting scroll 240 eccentrically coupled to the rotary shaft 226 is pivotally moved with respect to the fixed scroll 250 to form the compression chamber S 1 between the orbiting lap 241 and the fixed lap 251 .
  • the compression chamber Si may be formed in several stages in succession as the volume gradually decreases toward the center.
  • the refrigerant supplied from the outside of the casing 210 through the refrigerant suction pipe 218 may be directly introduced into the compression chamber S 1 .
  • the refrigerant may be compressed as it is moved toward the discharge chamber of the compression chamber S 1 by the orbiting motion of the orbiting scroll 240 . Then, the refrigerant may be discharged from the discharge chamber to the third space V 3 through the discharge port 253 of the fixed scroll 250 .
  • the compressed refrigerant discharged into the third space V 3 flows to the inner space of the casing 210 (i.e., the second space V 2 and the first space V 1 ) through the second discharge hole 256 b and the first discharge hole 231 a, and is then discharged from the casing 210 through the refrigerant discharge pipe 216 .
  • the refrigerant discharged into the third space V 3 may be guided to the second discharge hole 256 b by the discharge cover 270 without being leaked to the oil reservoir space V 4 .
  • FIGS. 4A to 6B are views showing the rotary shaft 226 and bearing of the scroll compressor of the present invention.
  • the rotary shaft 226 is coupled to the drive motor 220 and is rotated by the rotational force of the drive motor 220 transmitted thereto.
  • the rotary shaft 226 is arranged through the main frame 230 , the orbiting scroll 240 , the fixed scroll 250 and the discharge cover, and the lower end thereof is submerged in the oil reservoir space.
  • the oil feeder 271 located at the lower end of the rotary shaft 226 submerged in the oil reservoir space suctions the oil in the oil reservoir space and supplies the oil to the oil supply passage 226 a inside the rotary shaft 226 .
  • the oil in the oil supply passage 226 a is supplied to the journal bearing through the oil holes 228 a, 228 b, 228 d, and 228 e extending from the oil supply passage 226 a to the outer circumferential surface in a penetrating manner, thereby enhancing the rotation operation between the rotary shaft 226 and the bearing.
  • the scroll compressor of the present invention may employ a journal bearing, which enhances the rotational operation using oil between the bearing and the rotary shaft 226 such that force is uniformly applied along the circumference of the rotary shaft.
  • the journal bearing is not fixed to the rotary shaft 226 but is spaced apart from the rotary shaft 226 by a predetermined distance.
  • the main frame 230 and the fixed scroll 250 which do not rotate, include a first bearing 232 a and a second bearing 252 that are spaced apart from the rotary shaft 226 by a predetermined distance in order not to interfere with rotation of the rotary shaft 226 .
  • a portion of the rotary shaft 226 surrounded by the first bearing 232 a is referred to as a main journal 226 c.
  • the rotary shaft 226 may rotate while the main journal 226 c and the first bearing 232 a are not in direct contact with each other but maintained at a predetermined distance from each other using the oil between the first bearing 232 a and the main journal 226 c .
  • the first bearing 232 a and the main journal 226 c constitute a first rotating portion.
  • a portion of the rotary shaft 226 surrounded by the second bearing 252 is referred to as a sub-journal 226 g.
  • the rotary shaft 226 may rotate while the sub-journal 226 g and the second bearing 252 are not in direct contact with each other but maintained at a predetermined distance from each other using the oil between the second bearing 252 and the sub-journal.
  • the second bearing 252 and the sub-journal 226 g constitute a second rotating portion.
  • the first bearing 232 a and the main journal 226 c are spaced apart from each other and the second bearing 252 and the sub journal 226 g are spaced apart from each other by a predetermined distance.
  • the eccentric portion 226 f in a space between the first bearing 232 a and the second bearing 252 where the orbiting scroll 240 is located has an asymmetric structure. Accordingly, when the rotary shaft 226 is rotated by the driving force of the drive unit, the eccentric portion 226 f is slightly displaced from the center, and thus the rotary shaft 226 is bent as shown in FIG. 2A . When the rotary shaft is bent, the first bearing 232 a and the main journal 226 c come into contact with each other to generate friction, and the second bearing 252 and the sub journal 226 g come into contact with each other to generate friction, shown in FIG. 2B . Thereby, rotation is not smoothly performed.
  • the eccentric portion 226 f Since the eccentric portion 226 f is biased to one side, the portions of the first bearing 232 a and the second bearing 252 that come into contact with the main journal 226 c and the sub journal 226 g are closer to the eccentric portion 226 f. That is, the lower portion of the first bearing 232 a and the upper portion of the second bearing 252 come into contact with the journals.
  • the first bearing 232 a and the main journal 226 c in the first rotating portion of the present invention may be arranged such that the gap therebetween varies according to a vertical position, and the second bearing 252 and the sub journal 226 g in the second rotating portion are arranged such that the gap therebetween varies according to a vertical position.
  • the gap between the first bearing 232 a and the main journal 226 c is wider at a lower position than at a higher position, while the gap between the second bearing 252 and the sub journal 226 g is narrower at a lower position than at an higher position.
  • the first bearing 232 a and the second bearing 252 needs to be designed differently from the conventional cases, or the shape of the main journal 226 c or the sub-journal 226 g needs to be changed from the conventional shape.
  • each of the first bearing 232 a and the second bearing 252 may include a plurality of rings arranged in the vertical direction and having diameters different from each other. Since the first ring has a smaller diameter than the second ring, the gap between the main journal 226 c or the sub journal 226 g and the second ring is larger than the gap between the main journal 226 c or the sub journal 226 g and the first ring.
  • the portion of the rotary shaft corresponding to the second ring is eccentrically rotated with respect to the center, and accordingly the second ring may be formed to be larger than the first ring to avoid contact between the rotary shaft and the bearing.
  • the first ring 2321 may be disposed on the second ring 2322 .
  • the first ring 2521 is disposed under the second ring 2522 .
  • the second rings 2322 and 2522 are larger than the conventional bearings, and accordingly may rotate without contacting the main journal 226 c and the sub-journal 226 g. Therefore, deterioration of the rotational force and durability caused by friction may be prevented, and noise may be reduced.
  • the rings may also be formed to have steps on the inner side surfaces thereof. The number of steps may not be two but may be greater than or equal three. The steps may have different heights.
  • the first bearing 232 a and the second bearing 252 may have inclined surfaces in the vertical direction.
  • the inclined surface of the first bearing 232 a may have a narrow upper portion and a wide lower portion.
  • the inclined surface of the second bearing 252 may have a wide upper portion and a narrow lower portion.
  • the gap between the first bearing 232 a and the main journal 226 c and the gap between the second bearing 252 and the sub journal 226 g may be varied with a vertical position by the inclined surfaces of the first bearing 232 a and the second bearing 252 .
  • the inclined surface of the bearing may have the same slope from the upper portion to the lower portion of the bearing.
  • the inclined surface may have a slop varying with the position, or the inclined surface may be curved.
  • the diameters of first bearing 232 a and the second bearing 252 may be constant, but the diameters of the main journal 226 c and the sub-journal 226 g may vary between the upper portions and lower portions of the main journal 226 c and the sub journal 226 g.
  • and inclined surfaces may be formed on the rotary shaft 226 such that the upper portion of the main journal 226 c has a larger diameter than the lower portion of the main journal 226 c, and the upper portion of the sub journal 226 g has a smaller diameter than the lower portion of the sub journal 226 g.
  • the gap between the first bearing 232 a and the main journal 226 c and the gap between the second bearing 252 and the sub-journal 226 g may vary with a vertical position.
  • the gap between the first bearing 232 a and the main journal 226 c and the gap between the second bearing 252 and the sub journal 226 g are formed to vary with a vertical position as described above, degradation of the performance of the first bearing 232 a and the second bearing 252 due to deflection of the rotary shaft 226 , which occurs when the orbiting scroll 240 is rotated according to rotation of the rotary shaft 226 , may be addressed.
  • first bearing 232 a and the second bearing 252 are vertically symmetric with respect to the eccentric portion 226 f, but they are not necessarily required to have a symmetrical structure.
  • the embodiments of FIGS. 4A to 6B may be used in combination.
  • first bearing 232 a may be composed of a first ring 2321 and a second ring 2322 which have different diameters, and the second bearing 252 may have an inclined inner surface.
  • the scroll compressor 1 may prevent an eccentric effect occurring during rotation of the rotary shaft 226 from lowering performance of the bearing, thereby preventing noise and degradation of compression performance.
  • the scroll compressor according to the present invention may prevent performance of the bearing from being deteriorated due to the eccentric effect occurring during rotation of the rotary shaft, thereby preventing noise from being generated and preventing compression performance from being degraded.
  • friction may be prevented from deteriorating durability, thereby increasing the service life of the compressor and reducing the maintenance cost.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Rotary Pumps (AREA)
US16/751,422 2019-03-08 2020-01-24 Scroll compressor Abandoned US20200284257A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
KR1020190026741A KR102182171B1 (ko) 2019-03-08 2019-03-08 스크롤 압축기
KR10-2019-0026741 2019-03-08

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US (1) US20200284257A1 (fr)
EP (1) EP3705723B1 (fr)
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Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT107213B (de) * 1926-07-16 1927-09-10 Georg Dr Ing Dettmar Wellenlagerung.
JP2712914B2 (ja) * 1991-03-04 1998-02-16 三菱電機株式会社 スクロール圧縮機
JPH0783179A (ja) * 1993-09-16 1995-03-28 Hitachi Ltd スクロール圧縮機
JP3642604B2 (ja) * 1995-04-21 2005-04-27 東芝キヤリア株式会社 スクロール式圧縮機
JP4629567B2 (ja) * 2005-12-14 2011-02-09 三菱電機株式会社 スクロール圧縮機
KR101238205B1 (ko) * 2006-06-22 2013-03-04 엘지전자 주식회사 스크롤 압축기의 베어링장치
JP5075810B2 (ja) * 2008-12-26 2012-11-21 株式会社日立産機システム スクロール式流体機械
KR101718045B1 (ko) 2015-09-07 2017-03-20 엘지전자 주식회사 스크롤 압축기

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EP3705723A1 (fr) 2020-09-09
EP3705723B1 (fr) 2023-02-22
KR102182171B1 (ko) 2020-11-24

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