WO2021215652A1 - Compresseur - Google Patents

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Publication number
WO2021215652A1
WO2021215652A1 PCT/KR2021/002816 KR2021002816W WO2021215652A1 WO 2021215652 A1 WO2021215652 A1 WO 2021215652A1 KR 2021002816 W KR2021002816 W KR 2021002816W WO 2021215652 A1 WO2021215652 A1 WO 2021215652A1
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WO
WIPO (PCT)
Prior art keywords
fixed
wrap
skin
orbiting
compressor
Prior art date
Application number
PCT/KR2021/002816
Other languages
English (en)
Korean (ko)
Inventor
최중선
이강욱
이호원
Original Assignee
엘지전자 주식회사
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Publication date
Application filed by 엘지전자 주식회사 filed Critical 엘지전자 주식회사
Publication of WO2021215652A1 publication Critical patent/WO2021215652A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • 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
    • F04C2240/00—Components
    • F04C2240/20—Rotors
    • 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
    • F04C2240/30—Casings or housings
    • 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
    • F04C2240/80—Other components
    • F04C2240/809—Lubricant sump
    • 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
    • F04C27/00—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids
    • 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
    • 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
    • F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • 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
    • F05B2240/20—Rotors
    • 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
    • F05B2260/00—Function
    • F05B2260/98—Lubrication

Definitions

  • the present invention relates to a compressor. More particularly, it relates to a scroll compressor in which a part of the fixed wrap or the orbiting wrap is processed.
  • a compressor is a device applied to a refrigeration cycle (hereinafter, referred to as a refrigeration cycle) such as a refrigerator or an air conditioner, and provides work necessary for heat exchange in the refrigeration cycle by compressing the refrigerant.
  • a refrigeration cycle such as a refrigerator or an air conditioner
  • the compressor may be classified into a reciprocating type, a rotating seat type, a scroll type, etc. according to a method of compressing the refrigerant.
  • the scroll compressor is a compressor in which a compression chamber is formed between the fixed lap of the fixed scroll and the orbiting lap of the orbiting scroll by rotating the orbiting scroll in engagement with the fixed scroll fixed in the inner space of the sealed container.
  • the scroll compressor is continuously compressed through the interlocking scroll shape, so a relatively high compression ratio can be obtained, and the suction, compression, and discharge strokes of the refrigerant are smoothly continued to obtain a stable torque. For this reason, scroll compressors are widely used for refrigerant compression in air conditioners and the like.
  • a conventional scroll compressor includes a case having an external appearance and having a discharge unit for discharging refrigerant, a compression unit fixed to the case to compress the refrigerant, and a compression unit fixed to the case to compress the refrigerant and a driving unit for driving the unit, and the compression unit and the driving unit are coupled to the driving unit and connected by a rotating shaft.
  • the compression unit includes a fixed scroll fixed to the case and having a fixed wrap, and a revolving scroll including a revolving wrap driven by being engaged with the fixed wrap by the rotation shaft.
  • the rotation shaft is eccentric
  • the orbiting scroll is fixed to the eccentric rotation shaft and rotates.
  • the orbiting scroll orbits (orbits) along the fixed scroll and compresses the refrigerant.
  • the compression unit is provided under the discharge unit, and the driving unit is provided below the compression unit.
  • the rotating shaft has one end coupled to the compression unit and the other end passing through the driving unit.
  • the conventional scroll compressor since the compression part is provided above the driving part and close to the discharge part, it is difficult to supply oil to the compression part. There are disadvantages.
  • the conventional scroll compressor has a problem in that efficiency and reliability are deteriorated due to tilting of the scroll because the action points of the gas force generated by the refrigerant in the compressor and the reaction force supporting the same do not match.
  • a driving unit is provided closer to the discharge unit than the compression unit, and the compression unit is provided farthest from the discharge unit.
  • the orbiting wrap may be pushed out by the suction temperature and the temperature difference at the center of the rotation shaft. Accordingly, it is disclosed that the offset machining of the inlet portion crank angle -30° to +30°. However, it is impossible to prevent contact with other points as thermal deformation may occur between the swivel lap and the fixed lap. In addition, the form in which the thermal deformation of the orbiting lap and the fixed lap occurs is different for each position, so that the contact cannot be effectively prevented.
  • Korean Patent Application Laid-Open No. 10-2017-0122011 discloses that the thickness of the orbiting wrap or the fixed wrap becomes thinner from the discharge hole to the suction port. This is because thermal expansion generated at the center of the wrap is accumulated and the amount of thermal expansion is increased at the edge of the wrap. However, since the entire wrap is provided with a thin thickness, there is a problem in that deformation and damage due to concentration of centrifugal force occur.
  • the fixed end of the orbiting wrap and the fixed end of the fixed lap are thickly provided, and the free end of the orbiting wrap and the free end of the fixed lap are thin in order to reinforce the strength of the center of the orbiting lap and the central portion of the fixed lap.
  • an object to be solved is to provide a compressor that prevents local contact of the wrap due to deformation of the wrap.
  • an object of the present invention is to provide a compressor in which the fixed lap and the orbiting lap are processed to be differently selected depending on the positions of the fixed lap and the orbiting lap.
  • a case having a discharge unit through which the refrigerant is discharged and a storage space in which oil is stored, a driving unit coupled to an inner circumferential surface of the case, a driving unit coupled to the driving unit and rotating but provided to supply the oil
  • a rotating shaft a fixed head plate including a fixed through-hole provided to pass through the rotating shaft, a fixed side plate extending from the fixed end plate in the direction of the discharge part to be coupled to the case, and a fixed end plate provided closer to the rotating shaft than the fixed side plate in the fixed head plate
  • a fixed scroll including a fixed wrap extending in the discharge direction to form a compression chamber in which the refrigerant is compressed, a revolving mirror plate including a revolving through hole coupled to the rotary shaft, and one surface of the fixed head facing the revolving mirror plate
  • a orbiting scroll extending to and including a turning lap forming a compression chamber together with the fixed lap, a partial region of at least one of the fixed lap and the orbiting
  • the avoidance portion is formed on the outer surface of the fixed wrap, the fixed end of the fixed wrap is provided with a smaller cross-sectional area than the free end of the fixed wrap is provided with a compressor characterized in that it comprises a first fixed avoidance skin formed want to
  • the avoiding portion is formed on the outer surface of the fixed wrap, the fixed end of the fixed wrap is provided with a larger cross-sectional area than the free end of the fixed wrap is provided, characterized in that it comprises a second fixed avoidance skin is formed want to
  • the avoidance portion is formed on the inner surface of the orbital wrap, the fixed end of the orbital wrap is provided with a larger cross-sectional area than the free end of the fixed wrap, the compressor characterized in that it comprises a first turning skin formed want to
  • the first revolving skin is to provide a compressor, characterized in that provided in the revolving wrap positioned between the fixed lap facing the fixed side plate and the fixed side plate.
  • the avoiding portion is formed on the inner surface of the orbital wrap
  • the fixed end of the orbital wrap is provided with a smaller cross-sectional area than the free end of the fixed wrap is provided with a compressor, characterized in that it comprises a second turning skin formed want to
  • the second revolving skin is to provide a compressor, characterized in that provided in the revolving lap facing the fixed lap facing the rotation shaft and positioned in the direction of the fixed side plate.
  • the second turning skin is to provide a compressor, characterized in that provided so as to be inclined or stepped in a direction opposite to the center of the rotation axis on the inner surface of the turning wrap.
  • the avoiding portion is formed on the inner surface of the first fixed avoidance skin formed on the outer surface of the fixed wrap and the fixed end of the fixed wrap is provided with a smaller cross-sectional area than the free end of the fixed wrap, the inner surface of the orbiting wrap,
  • a fixed end of the orbiting wrap includes a first pivoting skin formed with a cross-sectional area larger than that of the free end of the fixed wrap, and the first fixed bypassing skin is provided on the fixed wrap facing the fixed side plate, and the first It is an object of the present invention to provide a compressor, characterized in that the turning skin is provided in the orbiting wrap positioned between the fixed side plate and the fixed wrap facing the fixed side plate.
  • first fixed circumferential skin is provided to be inclined or stepped from the outer surface of the fixed wrap in the direction of the center of the rotation axis, and the first turning skin is inclined or stepped from the inner surface of the orbit wrap to the opposite direction of the center of the rotation axis.
  • the avoiding portion is formed on the inner surface of the second fixed avoidance skin formed on the outer surface of the fixed wrap and the fixed end of the fixed wrap is provided with a larger cross-sectional area than the free end of the fixed wrap, and is formed on the inner surface of the orbiting wrap.
  • the fixed end of the orbiting wrap includes a second turning skin having a smaller cross-sectional area than the free end of the fixed wrap, and the second fixed turning skin is provided on the fixed wrap facing the rotation shaft and the second turning It is an object of the present invention to provide a compressor, characterized in that the avoidance portion is provided in the orbital wrap located in the direction of the fixed side plate facing the fixed wrap facing the rotation shaft.
  • the second fixed circumferential skin is provided to be inclined or stepped from the outer surface of the fixed wrap toward the center of the rotation axis, and the second turning skin is inclined or stepped from the inner surface of the orbit wrap to the opposite direction of the center of the rotation axis.
  • the avoiding portion is formed on the inner surface of the first fixed avoidance skin formed on the outer surface of the fixed wrap and the fixed end of the fixed wrap is provided with a smaller cross-sectional area than the free end of the fixed wrap, the inner surface of the orbiting wrap, A first turning skin formed by having a fixed end of the orbiting wrap having a cross-sectional area larger than that of the free end of the fixed wrap, formed on the outer surface of the fixed wrap, the fixed end of the fixed wrap having a cross-sectional area greater than that of the free end of the fixed wrap It includes a second fixed circumferential skin provided with a large size, a second turning skin formed on the inner surface of the orbiting wrap and having a fixed end of the orbiting wrap having a smaller cross-sectional area than the free end of the fixed wrap, and 1 fixed circumferential skin is provided in the fixed lap facing the fixed side plate, and the first pivoting skin is provided in the orbiting lap positioned between the fixed side plate and the fixed lap facing the fixed side plate, and the second A fixed dia
  • first fixed circumferential skin is provided to be inclined or stepped from the outer surface of the fixed wrap in the direction of the center of the rotation axis, and the first turning skin is inclined or stepped from the inner surface of the orbit wrap to the opposite direction of the center of the rotation axis.
  • second fixed diaphragm is provided to be inclined or stepped from the outer surface of the fixed wrap toward the center of the rotation axis, and the second revolving skin is inclined or stepped from the inner surface of the orbit wrap to the opposite direction of the center of the rotation axis.
  • the parts to be processed are provided differently depending on the degree of deformation of the fixed lap and the orbiting lap, so that the structural safety of the fixed lap and the orbiting lap can be secured and breakage can be prevented.
  • FIG. 1 is a view showing a basic configuration of a compressor according to an embodiment of the present invention.
  • FIG. 2 is a view showing the thermal deformation of the fixed scroll and the orbiting scroll when the compressor is operated.
  • 3 is a graph showing the thermal deformation trend of the fixed scroll and the orbiting scroll when the compressor is operated.
  • FIG. 4 is a view showing a contact point between the fixed wrap and the orbiting wrap according to the operation of the compressor.
  • FIG. 5 is a view showing an avoidance part and a first fixed avoidance part according to an embodiment of the present invention.
  • FIG. 6 is a view showing a second fixed avoidance skin according to an embodiment of the present invention.
  • FIG. 7 is a view showing a first turning skin according to an embodiment of the present invention.
  • FIG. 8 is a view showing a second turning skin according to an embodiment of the present invention.
  • 9 is a view showing that the avoidance portion is provided in consideration of the contact point between the fixed wrap and the orbiting wrap according to an embodiment of the present invention.
  • FIG. 1 illustrates a structure of a compressor according to an embodiment of the present invention. Specifically, FIG. 1 shows an internal structure and an oil supply structure of the compressor 10 according to an embodiment of the present invention.
  • a compressor 10 rotates a case 100 having a space in which a fluid is stored or flows, and is coupled to an inner circumferential surface of the case 100 to rotate a rotating shaft 230 .
  • It may include a driving unit 200 that is provided to make the fluid move, and a compression unit 300 that is coupled with the rotation shaft 230 inside the case to compress the fluid.
  • the case 100 may have a discharge unit 121 through which the refrigerant is discharged on one side.
  • the case 100 is provided in a cylindrical shape and is coupled to an accommodating shell 110 accommodating the driving unit 200 and the compression unit 300, and one end of the accommodating shell 110 so that the discharge unit 121 is formed.
  • the provided discharge shell 120 and the blocking shell 130 coupled to the other end of the receiving shell 110 to seal the receiving shell 110 may be included.
  • the driving unit 200 includes a stator 210 for generating a rotating magnetic field, and a rotor 220 provided to rotate by the rotating magnetic field, and the rotating shaft 230 is coupled to the rotor 220 . It may be provided to rotate together with the rotor 220 .
  • the stator 210 is provided with a plurality of slots formed along the circumferential direction on the inner circumferential surface of the stator 210, the coil is wound and can be fixed to the inner circumferential surface of the receiving shell 110, the rotor 220 is a permanent magnet is coupled and is rotatably coupled inside the stator 210 to generate rotational power.
  • the rotation shaft 230 may be press-fitted to the center of the rotor 220 .
  • the compression unit 300 is coupled to the receiving shell 110 and is coupled to a fixed scroll 320 provided in a direction away from the discharge unit 121 from the driving unit 200 and the rotating shaft 230 to be fixed.
  • An orbiting scroll 330 engaged with the scroll 320 to form a compression chamber; 310) may be included.
  • the driving unit 200 is disposed between the discharge unit 121 and the compression unit 300 .
  • the driving unit 200 may be provided on one side of the discharge unit 121
  • the compression unit 300 may be provided in a direction away from the discharge unit 121 from the driving unit 200 .
  • the discharge unit 121 is provided on the upper portion of the case 100
  • the compression unit 300 is provided under the driving unit 200
  • the driving unit 200 is provided on the discharge unit It may be provided between the 121 and the compression unit 300 .
  • the oil when oil is stored on the bottom surface of the case 100 , the oil may be directly supplied to the compression unit 300 without passing through the driving unit 200 .
  • the rotation shaft 230 since the rotation shaft 230 is coupled to and supported by the compression unit 300 , a lower frame that separately rotatably supports the rotation shaft may be omitted.
  • the rotating shaft 230 passes through not only the orbiting scroll 330 but also the fixed scroll 320 to provide the orbiting scroll 330 and the fixed scroll 320 . All of them may be provided for an interview.
  • an inflow force generated when a fluid such as a refrigerant flows into the compression unit 300 and a gas force generated when the refrigerant is compressed inside the compression unit 300 and a reaction force supporting the same are applied to the rotation shaft ( 230) can act as it is. Accordingly, the inlet force, gas force, and reaction force may be applied to one action point of the rotation shaft 230 . As a result, since an overturning moment does not act on the orbiting scroll 330 coupled to the rotation shaft 230 , tilting or overturning of the orbiting scroll can be fundamentally blocked.
  • up to axial vibration among the vibrations generated in the orbiting scroll 330 may be attenuated or prevented, and the overturning moment of the orbiting scroll 330 may also be attenuated or suppressed. Accordingly, noise and vibration generated by the lower scroll compressor 10 may be blocked.
  • the fixed scroll 320 supports the rotation shaft 230 in surface contact, even when the inflow force and gas force act on the rotation shaft 230 , durability of the rotation shaft 230 can be reinforced.
  • the rotation shaft 230 partially absorbs or supports the back pressure generated while the refrigerant is discharged to the outside, so that the orbiting scroll 330 and the fixed scroll 320 are in close contact with each other in the axial direction (vertical). drag) can be reduced. As a result, the frictional force between the orbiting scroll 330 and the fixed scroll 320 can be greatly reduced.
  • the compressor 10 attenuates the axial shaking and overturning moment of the orbiting scroll 330 inside the compression unit 300 , and reduces the frictional force of the orbiting scroll to increase the efficiency of the compression unit 300 . and reliability.
  • the main frame 310 of the compression unit 300 includes a main head plate 311 provided on one side of the driving unit 200 or a lower portion of the driving unit 200 and an inner peripheral surface of the main mirror plate 311 .
  • a main side plate 312 extending in a direction away from the driving part 200 and seated on the fixed scroll 320, and a main shaft bearing part extending from the main mirror plate 311 to rotatably support the rotating shaft 230 ( 318) may be included.
  • a main hole for guiding the refrigerant discharged from the fixed scroll 320 to the discharge unit 121 may be further provided in the main head plate 311 or the main side plate 312 .
  • the main mirror plate 311 may further include an oil pocket 314 engraved outside the main shaft portion 318 .
  • the oil pocket 314 may be provided in an annular shape, and may be provided to be eccentric from the main shaft portion 318 .
  • the oil pocket 314 is provided to be supplied to a portion where the fixed scroll 320 and the orbiting scroll 330 are engaged when the oil stored in the blocking shell 130 is transferred through the rotating shaft 230 and the like. can be
  • the fixed scroll 320 is provided in combination with the receiving shell 110 in a direction away from the driving unit 200 from the main head 311 to form the other surface of the compression unit 300.
  • the fixed scroll 320 has a fixed through-hole 328 provided to allow the rotating shaft 230 to pass therethrough, and a fixed shaft portion 3281 extending from the fixed through-hole 328 so that the rotating shaft is rotatably supported. may include.
  • the fixed shaft portion 3281 may be provided at the center of the fixed head plate 321 .
  • the thickness of the fixed head plate 321 may be the same as the thickness of the fixed shaft portion 3281 .
  • the fixed shaft portion 3281 may not protrude and extend from the fixed end plate 321 , but may be inserted into the fixed through hole 328 to be provided.
  • An inlet hole 325 for introducing a refrigerant into the fixed wrap 323 may be provided in the fixed side plate 322 , and a discharge hole 326 through which the refrigerant is discharged may be provided in the fixed end plate 321 .
  • the discharge hole 326 may be provided in the center direction of the fixed lap 323, but in order to avoid interference with the fixed bearing unit 3281, it may be provided spaced apart from the fixed bearing unit 3281, It may be provided in plurality.
  • the orbiting scroll 330 includes a turning mirror plate 331 provided between the main frame 310 and the fixed scroll 320, and an orbiting wrap forming a compression chamber together with the fixed wrap 323 in the orbiting mirror plate. (333).
  • the orbiting scroll 330 may further include an orbiting through-hole 338 provided through the orbiting mirror plate 331 so that the rotating shaft 230 is rotatably coupled.
  • the rotating shaft 230 may be provided such that a portion coupled to the orbiting through-hole 338 is eccentric. Accordingly, when the rotating shaft 230 rotates, the orbiting scroll 330 engages and moves along the fixed lap 323 of the fixed scroll 320 to compress the refrigerant.
  • the rotating shaft 230 includes a main shaft 231 coupled to the driving unit 200 and rotating, and a bearing unit connected to the main shaft 231 and rotatably coupled to the compression unit 300 ( 232) may be provided.
  • the bearing part 232 may be provided as a separate member from the main shaft 231 to accommodate the main shaft 231 therein, or may be provided integrally with the main shaft 231 . .
  • the bearing part 232 is inserted into the main bearing part 232c and the fixed shaft part 3281 of the fixed scroll 320 so that it is inserted into the main bearing part 318 of the main frame 310 and supported in the radial direction.
  • An eccentric shaft (232b) provided between the fixed bearing part (232a) and the main bearing part (232c) and the fixed bearing part (232a) to be supported in the radial direction and inserted into the orbiting through hole (338) of the orbiting scroll (330) may include.
  • the main bearing part 232c and the fixed bearing part 232a are formed on a coaxial line to have the same axial center, and the eccentric shaft 232b has a center of gravity of the main bearing part 232c or the fixed bearing part 232a. It may be formed eccentrically in the radial direction with respect to .
  • the outer diameter of the eccentric shaft 232b may be larger than the outer diameter of the main bearing portion 232c or the outer diameter of the fixed bearing portion 232a.
  • the eccentric shaft 232b provides a force for compressing the refrigerant while revolving the orbiting scroll 330 when the bearing part 232 rotates, and the orbiting scroll 330 is the fixed scroll 320 ) may be provided to rotate regularly by the eccentric shaft (232b).
  • the compressor 10 may further include an Oldham's ring 340 coupled to the upper portion of the orbiting scroll 330 .
  • the Oldham ring 340 may be provided between the orbiting scroll 330 and the main frame 310 to contact both the orbiting scroll 330 and the main frame 310 .
  • the Oldham ring 340 is provided to linearly move in four directions of front, back, left, and right to prevent rotation of the orbiting scroll 330 .
  • the rotation shaft 230 may be provided to completely penetrate the fixed scroll 320 and protrude to the outside of the compression unit 300 .
  • the oil stored in the outside of the compression unit 300 and the blocking shell 130 and the rotation shaft 230 can come into direct contact, and the rotation shaft 230 rotates inside the compression unit 300 . oil can be supplied.
  • the oil may be supplied to the compression unit 300 through the rotation shaft 230 .
  • An oil supply passage 234 for supplying the oil to the outer peripheral surface of the main bearing part 232c, the outer peripheral surface of the fixed bearing part 232a, and the outer peripheral surface of the eccentric shaft 232b is provided in the rotation shaft 230 or the interior of the rotation shaft can be formed.
  • a plurality of oil holes 234a, b, c, and d may be formed in the oil supply passage 234 .
  • the oil hole may include a first oil hole 234a , a second oil hole 234b , a third oil hole 234d , and a fourth oil hole 234e .
  • the first oil hole 234a may be formed to pass through the outer peripheral surface of the main bearing part 232c.
  • the first oil hole 234a may be formed to penetrate from the oil supply passage 234 to the outer peripheral surface of the main bearing part 232c. Also, the first oil hole 234a may be formed to pass through, for example, an upper portion of an outer circumferential surface of the main bearing part 232c, but is not limited thereto. That is, it may be formed to penetrate the lower part of the outer peripheral surface of the main bearing part 232c.
  • the first oil hole 234a may include a plurality of holes, unlike that illustrated in the drawing.
  • each hole may be formed only on the upper or lower part of the outer peripheral surface of the main bearing part 232c, and upper and lower parts of the outer peripheral surface of the main bearing part 232c. may be formed in each.
  • the rotating shaft 230 may include an oil feeder 233 (reference numeral added) provided to pass through a muffler 500 to be described later and contact the oil stored in the case 100 .
  • the oil feeder 233 is provided spirally on the outer peripheral surface of the extension shaft 233a and the extension shaft 233a through the muffler 500 and in contact with the oil, and is a spiral communicating with the oil supply passage 234 .
  • a groove 233b may be included.
  • Oil discharged through the plurality of oil holes 234a, 234b, 234d, and 234e forms an oil film between the fixed scroll 250 and the orbiting scroll 330 to maintain an airtight state, as well as It may be provided to absorb and radiate the frictional heat generated in the friction part between the components.
  • the oil guided along the rotation shaft 230 and the oil supplied through the first oil hole 234a may be provided to lubricate the main frame 310 and the rotation shaft 230 .
  • the oil may be discharged through the second oil hole 234b and supplied to the upper surface of the orbiting scroll 330 , and the oil supplied to the upper surface of the orbiting scroll 330 may be guided to the intermediate pressure chamber through the pocket groove 314 .
  • oil discharged through the second oil hole 234b as well as the first oil hole 234a or the third oil hole 234d may be supplied to the pocket groove 314 .
  • the oil guided along the rotating shaft 230 may be supplied to the Oldham ring 340 installed between the orbiting scroll 330 and the main frame 310 and the fixed side plate 322 of the fixed scroll 320 . .
  • the oil supplied to the third oil hole 234c is supplied to the compression chamber, thereby reducing wear due to friction between the orbiting scroll 330 and the fixed scroll 320 as well as forming an oil film and dissipating heat. Compression efficiency can be improved.
  • centrifugal refueling structure in which the lower scroll compressor 10 supplies oil to the bearings using the rotation of the rotating shaft 230 has been described so far, but this is only an example, and the pressure difference inside the compression unit 300 is used. It goes without saying that a differential pressure refueling structure for refueling oil and a forced refueling structure for supplying oil through a torochoid pump can also be applied.
  • the compressed refrigerant is discharged to the discharge hole 326 along the space formed by the fixed wrap 323 and the orbit wrap 333 .
  • the discharge hole 326 may be more advantageously provided toward the discharge unit 121 . This is because it is most advantageous for the refrigerant discharged from the discharge hole 326 to be delivered to the discharge unit 121 without a significant change in the flow direction.
  • the compression unit 300 is provided in a direction away from the discharge unit 121 from the driving unit 200 , and the fixed scroll 320 is provided at the outermost portion of the compression unit 300 . Because of the negative characteristics, the discharge hole 326 is provided to inject the refrigerant in the opposite direction to the discharge unit 121 .
  • the discharge hole 326 is provided to inject the refrigerant in a direction away from the discharge part 121 from the fixed head plate 321 . Therefore, when the refrigerant is directly injected into the discharge hole 326 , the refrigerant may not be smoothly discharged to the discharge unit 121 , and when oil is stored in the blocking shell 130 , the refrigerant is mixed with the oil There is a risk of cooling or mixing by collision.
  • the compressor 10 further includes a muffler 500 coupled to the outermost portion of the fixed scroll 320 to provide a space for guiding the refrigerant to the discharge unit 121 . can do.
  • the muffler 500 seals one surface of the fixed scroll 320 in a direction away from the discharge unit 121 so as to guide the refrigerant discharged from the fixed scroll 320 to the discharge unit 121 . may be provided to do so.
  • the muffler 500 may include a coupling body 520 coupled to the fixed scroll 320 and a receiving body 510 extending from the coupling body 520 to form a closed space. Accordingly, the refrigerant injected from the discharge hole 326 may be discharged to the discharge unit 121 by changing the flow direction along the sealed space formed by the muffler 500 .
  • the fixed scroll 320 since the fixed scroll 320 is provided by being coupled to the receiving shell 110 , the refrigerant may be prevented from moving to the discharge unit 121 by being obstructed by the fixed scroll 320 . Accordingly, the fixed scroll 320 may further include a bypass hole 327 through the fixed head plate 321 through which the refrigerant may pass through the fixed scroll 320 . The bypass hole 327 may be provided to communicate with the main hole 317 . Accordingly, the refrigerant may pass through the compression unit 300 , pass through the driving unit 200 , and be discharged to the discharge unit 121 .
  • the inside of the fixing wrap 323 and the orbiting wrap 333 maintain a high pressure state. Accordingly, the discharge pressure acts on the rear surface of the orbiting scroll as it is, and the back pressure acts from the orbiting scroll toward the fixed scroll as a reaction.
  • the compressor 10 according to the present embodiment prevents leakage between the orbiting wrap 333 and the fixed wrap 323 by focusing the back pressure on the portion where the orbiting scroll 330 and the rotating shaft 230 are coupled. It may further include a back pressure seal (seal, 350).
  • the back pressure seal 350 is provided in a ring shape to maintain the inner circumferential surface at high pressure, and separate the outer circumferential surface at an intermediate pressure lower than the high pressure. Accordingly, the back pressure is concentrated on the inner circumferential surface of the back pressure seal 350 so that the orbiting scroll 330 is brought into close contact with the fixed scroll 320 .
  • the back pressure seal 350 may also be provided so that the center thereof is biased toward the discharge hole 326 .
  • the oil supplied to the compression unit 300 or the oil stored in the case 100 moves to the upper part of the case 100 together with the refrigerant as the refrigerant is discharged to the discharge unit 121 .
  • the oil has a higher density than the refrigerant and cannot move to the discharge unit 121 due to the centrifugal force generated by the rotor 220 , and is not moved to the inner wall of the discharge shell 120 and the receiving shell 110 .
  • the lower scroll compressor 10 includes the driving unit 200 and the compression unit 300 to recover the oil attached to the inner wall of the case 100 to the oil storage space of the case 100 or the blocking shell 130 . ) may further include a recovery passage on the outer peripheral surface.
  • the recovery passage includes a drive return passage 201 provided on the outer peripheral surface of the driving unit 200 , a compression return passage 301 provided on the outer peripheral surface of the compression unit 300 , and an outer peripheral surface of the muffler 500 . It may include a muffler return passage 501 that is.
  • the driving return passage 201 may be provided with a part of the outer peripheral surface of the stator 210 depressed, and the compression recovery passage 301 may be provided with a part of the outer peripheral surface of the fixed scroll 320 depressed.
  • the muffler recovery passage 501 may be provided in which a part of the outer peripheral surface of the muffler is recessed.
  • the drive return passage 201 , the compression return passage 301 , and the muffler return passage 501 may communicate with each other to allow oil to pass therethrough.
  • the lower scroll compressor 10 may further include a balancer 400 capable of offsetting an eccentric moment that may occur due to the eccentric shaft 232b.
  • the balancer 400 is preferably coupled to the rotation shaft 230 itself or the rotor 220 provided to rotate. Accordingly, the balancer 400 is a center balancer 410 provided on one surface toward the lower end of the rotor 220 or the compression unit 300 so as to offset or reduce the eccentric load of the eccentric shaft 232b and , The outer balancer coupled to the other surface facing the upper end or the discharge part 121 of the rotor 220 to offset the eccentric load or eccentric moment of at least one of the eccentric shaft 232b or the lower balancer 420 ( 420) may be included.
  • the center balancer 410 is provided relatively close to the eccentric shaft 232b, there is an advantage that can directly offset the eccentric load of the eccentric shaft 232b. Therefore, it is preferable that the center balancer 410 is eccentric in a direction opposite to the eccentric shaft 232b. As a result, even when the rotation shaft 230 rotates at a low speed or a high speed, the eccentric shaft 232b and the spaced distance are close, so that the eccentric force or the eccentric load generated in the eccentric shaft 232b is almost uniformly effectively offset. can
  • the outer balancer 420 may be provided to be eccentric in a direction opposite to the eccentric shaft 232b. However, the outer balancer 420 may be provided eccentrically in a direction corresponding to the eccentric shaft 232b to partially offset the eccentric load generated by the center balancer 410 .
  • center balancer 410 and the outer balancer 420 may offset the eccentric moment generated by the eccentric shaft 232b to assist the rotation shaft 230 to rotate stably.
  • FIG. 2 is a view showing the thermal deformation of the fixed scroll and the orbiting scroll when the compressor is operating
  • FIG. 3 is a graph showing the thermal deformation of the fixed scroll and the orbiting scroll when the compressor is operating.
  • FIG. 2(a) shows the thermal deformation of the fixed scroll 320 when the compressor is operated
  • FIG. 2(b) shows the thermal deformation of the orbiting scroll 330 when the compressor is operated
  • FIG. 2(c) is The low-temperature and high-temperature regions of the compression section are shown.
  • 3 (a) is a graph showing the amount of radial deformation of the fixed scroll 320 according to the crank angle when the compressor is operating
  • FIG. 3 (b) is a graph showing the amount of radial deformation of the orbiting scroll 330 when the compressor is operated at the crank angle It is a graph that follows.
  • a negative number of the deformation amount indicates deformation to the center of the rotation shaft 230
  • a positive number of the deformation amount indicates deformation outside the rotation shaft 230 . That is, in the fixed scroll 320 , the fixed wrap 323 is deformed in the central direction of the rotating shaft 230 from a crank angle of 0 to 300 degrees. In addition, in the fixed scroll 320 , the fixed wrap 323 is deformed in an outward direction of the rotation shaft 230 at a crank angle of 300 degrees or more.
  • the fixed scroll 320 may introduce a low-temperature refrigerant through the inlet hole 325 . Due to this, a low-temperature region A may be formed in a region between the fixing side plate 322 and the fixing lap 323 facing the fixing side plate 322 . The low-temperature region A may be formed at a crank angle of 0 degrees to 300 degrees of the fixed scroll 320 .
  • a first high-temperature region B is formed in the region between the rotating shaft 230 and the fixed wrap 323 facing the rotating shaft 230 due to the high-temperature and high-pressure compressed refrigerant. That is, the first high temperature region B may be formed at a crank angle of 300 degrees or more of the fixed scroll 320 .
  • a second high-temperature region C may be formed between the inside of the case 100 and the outside of the compression unit 300 due to the high-temperature and high-pressure compressed refrigerant flowing.
  • the fixed side plate 322 faces the fixed side plate 322 due to the temperature difference between the low temperature region A and the first high temperature region B and the temperature difference between the low temperature region A and the second high temperature region C.
  • the fixed wrap 323 viewed may be thermally deformed in the central direction of the rotation shaft 230 . That is, in a region provided far from the rotation shaft 230 and adjacent to the suction port 111 , thermal deformation of the fixed head plate 321 due to a temperature difference may be accumulated. Accordingly, the accumulated thermal deformation may be the dominant cause of the deformation of the fixing wrap 323 .
  • the fixed wrap 323 facing the rotation shaft 230 due to the temperature difference between the low temperature region A and the first high temperature region B and the compressed high-pressure refrigerant is opposite to the center of the rotation shaft 230 . Thermal deformation may occur in the direction.
  • the accumulation of thermal deformation of the fixed head plate 321 due to the temperature difference may be less than in the region adjacent to the suction port 111 . Accordingly, it may be the dominant cause of the deformation of the fixing wrap 323 due to the high pressure in the vicinity of the rotation shaft 230 rather than the accumulated thermal deformation.
  • a negative number of the deformation amount indicates deformation to the center of the rotation shaft 230
  • a positive number of the deformation amount indicates deformation outside the rotation shaft 230 . That is, in the orbiting scroll 330 , the orbiting wrap 333 is deformed in the central direction of the rotating shaft 230 from a crank angle of 0 to 480 degrees. In addition, in the orbiting scroll 330 , the orbiting wrap 333 is deformed in an outward direction of the rotating shaft 230 at a crank angle of 480 degrees or more.
  • the fixed side plate due to the temperature difference between the low temperature region A and the first high temperature region B and the temperature difference between the low temperature region A and the second high temperature region C, the fixed side plate
  • the orbiting wrap 333 positioned between the 322 and the fixed wrap 323 facing the fixed side plate 322 may be thermally deformed in the central direction of the rotation shaft 230 .
  • thermal deformation of the orbiting mirror plate 331 due to a temperature difference may be accumulated. Accordingly, the accumulated thermal deformation may be the dominant cause of the deformation of the orbiting wrap 333 .
  • the accumulation of thermal deformation of the revolving mirror plate 331 due to the temperature difference may be less than in the region adjacent to the suction port 111 . Accordingly, a high pressure in the vicinity of the rotation shaft 230 rather than the accumulated thermal deformation may be a dominant cause of the deformation of the orbiting wrap 333 .
  • FIG. 4 is a view showing a contact point between the fixed wrap and the orbiting wrap according to the operation of the compressor. Specifically, FIG. 4(a) shows a contact point between the fixed wrap 323 and the orbiting wrap 333 in the low-temperature area A, and FIG. 4(b) illustrates the contact point in the first high-temperature area B. It shows the contact point of the fixed wrap 323 and the orbiting wrap 333.
  • the fixing lap 323 facing the fixing side plate 322 may be thermally deformed in the central direction of the rotation shaft 230 .
  • the orbiting wrap 333 positioned between the fixed side plate 322 and the fixed lap 323 facing the fixed side plate 322 may be thermally deformed in the central direction of the rotation shaft 230 . have.
  • the fixing wrap 323 facing the rotation shaft 230 may be thermally deformed in a direction opposite to the center of the rotation shaft 230 .
  • the pivoting wrap ( 333) may be thermally deformed in a direction opposite to the center of the rotation shaft 230 .
  • the free end of the fixing wrap 323 facing the rotation shaft 230 and the outer surface of the fixing wrap 323 facing the rotation shaft 230 face the rotation shaft 230.
  • the fixed end of the orbiting wrap 333 positioned between the fixed wrap 323 and the fixed side plate 322 facing the can be in contact with each other.
  • FIG 5 is a view showing an avoidance unit according to an embodiment of the present invention. Specifically, it is a view showing the first fixing avoidance skin 361 formed on the outer surface of the fixing wrap (323).
  • the compressor 10 may include an avoiding part 360 in which a partial region of at least one of the fixed wrap 323 and the orbiting wrap 333 is recessed or concave. .
  • the avoidance part 360 may extend the interval between the fixed wrap 323 and the orbit wrap 333 .
  • the fixed wrap 323 even if thermal deformation of the fixed head plate 321 , the turning mirror plate 331 , the fixed wrap 323 and the turning wrap 333 occurs when the compressor 10 is operated, the fixed wrap 323 and It is possible to prevent contact with the orbital wrap 333, thereby reducing noise.
  • the fixed wrap 323 and the orbital wrap 333 are not entirely processed, a reduction in compression efficiency and a decrease in efficiency due to refrigerant leakage can be prevented.
  • the avoidance part 360 prevents the fixed wrap 323 and the turning wrap 333 from contacting, and at the same time, the fixed head plate 321 and the turning mirror plate 331 can be provided as thin as possible. have.
  • the avoiding part 360 may include a first fixing avoiding skin 361 formed on the outer surface of the fixing wrap 323 .
  • the first fixed avoidance skin 361 may be formed such that the fixed end of the fixed wrap 323 has a smaller cross-sectional area than the free end of the fixed wrap 323 .
  • the first fixed avoidance skin 361 may be provided to be inclined from the outer surface of the fixed wrap 323 toward the center of the rotation shaft 230 .
  • the cross-sectional area of the fixed wrap 323 from a specific point on the outer surface of the fixed wrap 323 to the fixed end plate 321 may be reduced in the central direction of the rotation shaft 230 .
  • a specific point on the outer surface of the fixing wrap 323 and the inclination of the first fixing avoidance 361 are the main operating pressure, operating speed, operating temperature, operating environment, and generated fixing wrap 323 of the compressor 10 . It can be determined in consideration of the amount of deformation of
  • first fixed avoidance skin 361 may be provided so as to be stepped from the outer surface of the fixed wrap 323 in the direction of the center of the rotation axis.
  • the cross-sectional area of the fixing wrap 323 may be depressed to decrease in the central direction of the rotation shaft 230 . That is, the first fixed avoidance skin 361 may be provided in a stepped shape.
  • a specific point on the outer surface of the fixed wrap 323 and the reduced cross-sectional area of the fixed wrap 323 are the main operating pressure, operating speed, operating temperature, operating environment, and generated fixed wrap 323 of the compressor 10 . It may be determined in consideration of the amount of deformation.
  • the first fixed avoidance skin 361 may determine the interval between the fixed wrap 323 and the orbital wrap 333 .
  • the fixed wrap 323 even if thermal deformation of the fixed head plate 321 , the turning mirror plate 331 , the fixed wrap 323 and the turning wrap 333 occurs when the compressor 10 is operated, the fixed wrap 323 and It is possible to prevent contact with the orbital wrap 333, thereby reducing noise.
  • the fixed wrap 323 and the orbital wrap 333 are not entirely processed, a reduction in compression efficiency and a decrease in efficiency due to refrigerant leakage can be prevented.
  • the first fixing avoidance skin 361 may be provided on the fixing wrap 323 facing the fixing side plate 322 . That is, it may be provided in the fixing wrap 323 located in the low temperature region A.
  • the fixing wrap 323 facing the fixing side plate 322 may be thermally deformed in the central direction of the rotation shaft 230 .
  • the orbiting wrap 333 positioned between the fixed side plate 322 and the fixed lap 323 facing the fixed side plate 322 may be thermally deformed in the central direction of the rotation shaft 230 . have.
  • the orbiting wrap is positioned between the fixed end of the fixed lap 323 facing the fixed side plate 322 and the fixed lap 323 facing the fixed side plate 322 and the fixed side plate 322 .
  • the free ends of (333) can be contacted.
  • the first fixed diaphragm 361 is provided on the fixed lap 323 facing the fixed side plate 322 and is positioned between the fixed laps 323 facing the fixed side plate 322. Contact with the free end of the wrap 333 can be prevented.
  • the first fixed evaporative skin 361 is only partially processed in the fixed wrap 323 while preventing the contact between the fixed wrap 323 and the orbiting wrap 333, thereby reducing the compression efficiency due to leakage of the refrigerant. can be prevented
  • the avoiding part 360 may include a third fixing avoiding skin (not shown) formed on the inner surface of the fixing wrap 323 .
  • the third fixed avoidance skin may be formed such that the fixed end of the fixed wrap 323 has a smaller cross-sectional area than the free end of the fixed wrap 323 .
  • the third fixed avoidance may be inclined or stepped in a direction opposite to the center of the rotation shaft 230 from the inner surface of the fixing wrap 323 .
  • FIG. 6 is a view showing a second fixed avoidance skin according to an embodiment of the present invention.
  • the avoidance part 360 may include a second fixing avoidance skin 362 formed on the outer surface of the fixing wrap 323 .
  • the second fixed avoidance skin 362 may be formed such that the fixed end of the fixed wrap 323 has a larger cross-sectional area than the free end of the fixed wrap 323 .
  • the second fixed avoidance skin 362 may be provided to be inclined from the outer surface of the fixed wrap 323 toward the center of the rotation shaft 230 .
  • the cross-sectional area of the fixing lap 323 from a specific point on the outer surface of the fixing lap 323 to the end of the fixing lap 323 may be reduced in the central direction of the rotation shaft 230 .
  • a specific point on the outer surface of the fixing wrap 323 and the inclination of the second fixing avoidance 362 are the main operating pressure, operating speed, operating temperature, operating environment, and generated fixing wrap 323 of the compressor 10 . It can be determined in consideration of the amount of deformation of
  • the second fixed avoidance skin 362 may be provided so as to be stepped from the outer surface of the fixed wrap 323 toward the center of the rotation shaft 230 .
  • the cross-sectional area of the fixing wrap 323 may be depressed to decrease in the central direction of the rotation shaft 230 . That is, the second fixed avoidance skin 362 may be provided in a stepped shape.
  • a specific point on the outer surface of the fixed wrap 323 and the reduced cross-sectional area of the fixed wrap 323 are the main operating pressure, operating speed, operating temperature, operating environment, and generated fixed wrap 323 of the compressor 10 . It may be determined in consideration of the amount of deformation.
  • the second fixed avoidance skin 362 may determine the interval between the fixed wrap 323 and the orbital wrap 333 .
  • the fixed wrap 323 even if thermal deformation of the fixed head plate 321 , the turning mirror plate 331 , the fixed wrap 323 and the turning wrap 333 occurs when the compressor 10 is operated, the fixed wrap 323 and It is possible to prevent contact with the orbital wrap 333, thereby reducing noise.
  • the fixed wrap 323 and the orbital wrap 333 are not entirely processed, a reduction in compression efficiency and a decrease in efficiency due to refrigerant leakage can be prevented.
  • the second fixed avoidance skin 362 may be provided on the fixed wrap 323 facing the rotation shaft 230 . That is, it may be provided in the fixing wrap 323 positioned in the first high-temperature region B.
  • the fixing wrap 323 facing the fixing side plate 322 may be thermally deformed in the central direction of the rotation shaft 230 .
  • the rotating lap 333 positioned between the fixed lap 323 and the fixed side plate 322 facing the outer surface of the fixed lap 323 facing the rotating shaft 230 is the rotating shaft 230 . Thermal deformation may occur in the direction opposite to the center.
  • the free end of the fixing lap 323 facing the rotation shaft 230 and the fixing side plate 322 and the outer surface of the fixing lap 323 facing the rotation shaft 230 face the fixing lap 323 .
  • the fixed end of the orbiting wrap 333 positioned between the fixed side plate 322 may be in contact.
  • the second fixed avoidance skin 362 is provided on the fixed wrap 323 facing the rotating shaft 230 to face the outer surface of the fixed wrap 323 facing the rotating shaft 230 and the fixed wrap ( 323 ) and the fixed end of the orbiting wrap 333 positioned between the fixed side plate 322 can be prevented from coming into contact with each other.
  • the second fixed evaporative skin 362 is only partially processed in the fixed wrap 323 while preventing the contact between the fixed wrap 323 and the orbiting wrap 333, thereby reducing the compression efficiency due to leakage of the refrigerant. can be prevented
  • the avoiding part 360 may include a fourth fixing evasion skin (not shown) formed on the inner surface of the fixing wrap 323 .
  • the fourth fixed avoidance skin may be formed such that the fixed end of the fixed wrap 323 has a larger cross-sectional area than the free end of the fixed wrap 323 .
  • the fourth fixed avoidance may be inclined or stepped from the inner surface of the fixed wrap 323 in a direction opposite to the center of the rotation shaft 230 .
  • FIG. 7 is a view showing a first turning skin according to an embodiment of the present invention.
  • the avoidance part 360 may include a first turning skin 363 formed on the inner surface of the turning wrap 333 .
  • the first turning skin 363 may be formed such that the fixed end of the orbiting wrap 333 has a larger cross-sectional area than the free end of the turning wrap 333 .
  • the first turning skin 363 may be inclined in a direction opposite to the center of the rotation shaft 230 on the inner surface of the turning wrap 333 .
  • the cross-sectional area of the orbiting wrap 333 from a specific point on the inner surface of the orbiting wrap 333 to the end of the orbiting wrap 333 may be reduced in a direction opposite to the center of the rotational shaft 230 .
  • a specific point on the inner surface of the orbiting wrap 333 and the inclination of the first turning skin 363 are the main operating pressure, operating speed, operating temperature, operating environment, and generated orbiting wrap 333 of the compressor 10 . It can be determined in consideration of the amount of deformation of
  • first turning skin 363 may be provided so as to be stepped from the inner surface of the turning wrap 333 in a direction opposite to the center of the rotation shaft 230 .
  • the cross-sectional area of the orbiting wrap 333 may be reduced in a direction opposite to the center of the rotational shaft 230 . That is, the first turning skin 363 may be provided in a stepped shape.
  • a specific point on the inner surface of the orbiting wrap 333 and the reduced cross-sectional area of the orbiting wrap 333 are the main operating pressure, operating speed, operating temperature, operating environment, and generated fixed wrap 323 of the compressor 10 . It may be determined in consideration of the amount of deformation.
  • the first turning skin 363 may determine the interval between the fixed wrap 323 and the turning wrap 333 .
  • the fixed wrap 323 even if thermal deformation of the fixed head plate 321 , the turning mirror plate 331 , the fixed wrap 323 and the turning wrap 333 occurs when the compressor 10 is operated, the fixed wrap 323 and It is possible to prevent contact with the orbital wrap 333, thereby reducing noise.
  • the fixed wrap 323 and the orbital wrap 333 are not entirely processed, a reduction in compression efficiency and a decrease in efficiency due to refrigerant leakage can be prevented.
  • the first turning skin 363 may be provided in the turning wrap 333 positioned between the fixed side plate 322 and the fixed lap 323 facing the fixed side plate 322 . That is, it may be provided in the orbiting wrap 333 located in the low-temperature region A.
  • the fixing wrap 323 facing the fixing side plate 322 may be thermally deformed in the central direction of the rotation shaft 230 .
  • the orbiting wrap 333 positioned between the fixed side plate 322 and the fixed lap 323 facing the fixed side plate 322 may be thermally deformed in the central direction of the rotation shaft 230 . have.
  • the orbiting wrap is positioned between the fixed end of the fixed lap 323 facing the fixed side plate 322 and the fixed lap 323 facing the fixed side plate 322 and the fixed side plate 322 .
  • the free ends of (333) can be contacted.
  • the first turning skin 363 is provided in the turning wrap 333 positioned between the fixed side plate 322 and the fixed lap 323 facing the fixed side plate 322, the fixed side plate ( Contact with the fixed end of the fixing wrap 323 facing the 322 can be prevented.
  • the first turning skin 363 is only partially processed in the turning wrap 333 while preventing contact between the fixed wrap 323 and the turning wrap 333, thereby reducing the compression efficiency due to leakage of the refrigerant. can be prevented
  • the avoiding part 360 may include a third turning skin (not shown) formed on the outer surface of the turning wrap 333 .
  • the third revolving skin may be formed such that a fixed end of the revolving wrap 333 has a larger cross-sectional area than the free end of the revolving wrap 333 .
  • the third turning skin may be provided to be inclined or stepped from the outer surface of the turning wrap 333 toward the center of the rotation shaft 230 .
  • FIG. 8 is a view showing a second turning skin according to an embodiment of the present invention.
  • the avoiding part 360 may include a second turning skin 364 formed on the inner surface of the turning wrap 333 .
  • the second turning skin 364 may be formed such that the fixed end of the orbiting wrap 333 has a smaller cross-sectional area than the free end of the orbiting wrap 333 .
  • the second turning skin 364 may be provided to be inclined in a direction opposite to the center of the rotation shaft 230 on the inner surface of the turning wrap 333 .
  • the cross-sectional area of the orbiting wrap 333 may be reduced in a direction opposite to the center of the rotational shaft 230 .
  • the specific point on the inner surface of the orbiting wrap 333 and the inclination of the second turning skin 364 are the main operating pressure, operating speed, operating temperature, operating environment, and generated orbiting wrap 333 of the compressor 10 . It can be determined in consideration of the amount of deformation of
  • the second turning skin 364 may be provided so as to be stepped from the inner surface of the turning wrap 333 in a direction opposite to the center of the rotation shaft 230 .
  • the cross-sectional area of the orbiting wrap 333 may be reduced in a direction opposite to the center of the rotational shaft 230 . That is, the second turning skin 364 may be provided in a stepped shape.
  • a specific point on the inner surface of the orbiting wrap 333 and the reduced cross-sectional area of the orbiting wrap 333 are the main operating pressure, operating speed, operating temperature, operating environment, and generated fixed wrap 323 of the compressor 10 . It may be determined in consideration of the amount of deformation.
  • the second turning skin 364 may determine the interval between the fixed wrap 323 and the turning wrap 333 .
  • the fixed wrap 323 even if thermal deformation of the fixed head plate 321 , the turning mirror plate 331 , the fixed wrap 323 and the turning wrap 333 occurs when the compressor 10 is operated, the fixed wrap 323 and It is possible to prevent contact with the orbital wrap 333, thereby reducing noise.
  • the fixed wrap 323 and the orbital wrap 333 are not entirely processed, a reduction in compression efficiency and a decrease in efficiency due to refrigerant leakage can be prevented.
  • the second turning skin 364 faces the outer surface of the fixed wrap 323 facing the rotation shaft 230 and the turning positioned between the fixed wrap 323 and the fixed side plate 322 . It may be provided in the wrap 333 . That is, it may be provided in the orbiting wrap 333 adjacent to the first high-temperature region B.
  • the fixing wrap 323 facing the rotation shaft 230 may be thermally deformed in a direction opposite to the center of the rotation shaft 230 .
  • the rotating lap 333 positioned between the fixed lap 323 and the fixed side plate 322 facing the outer surface of the fixed lap 323 facing the rotating shaft 230 is the rotating shaft 230 . Thermal deformation may occur in the direction opposite to the center of
  • the fixing lap 323 and the fixing side plate 322 face the free end of the fixing lap 323 facing the rotation shaft 230 and the outer surface of the fixing lap 323 facing the rotation shaft 230 .
  • the fixed end of the orbiting wrap 333 located between may be in contact.
  • the second turning skin 364 faces the outer surface of the fixed lap 323 facing the fixed side plate 322 and the rotating shaft 230 and is positioned between the fixed lap 323 and the fixed side plate 322 . It is provided in the orbital wrap 333 located in the position to prevent contact with the free end of the fixed wrap 323 facing the rotation shaft 230 .
  • the second turning skin 364 is only partially processed in the turning wrap 333 while preventing the contact between the fixed wrap 323 and the turning wrap 333, thereby reducing the compression efficiency due to leakage of the refrigerant. can be prevented
  • the avoiding part 360 may include a fourth turning skin (not shown) formed on the outer surface of the turning wrap 333 .
  • the fourth revolving skin may be formed such that the fixed end of the revolving wrap 333 has a smaller cross-sectional area than the free end of the revolving wrap 333 .
  • the fourth turning skin may be inclined or stepped from the outer surface of the turning wrap 333 in the central direction of the rotation shaft 230 .
  • 9 is a view showing that the avoidance portion is provided in consideration of the contact point between the fixed wrap and the orbiting wrap according to an embodiment of the present invention.
  • the compressor 10 may include the above-described first fixed evacuation part 361 and the first swiveling part 363 together.
  • the first fixed circumferential skin 361 is provided on the fixed wrap 323 facing the fixed side plate 322
  • the first turning skin 363 includes the fixed side plate 322 and the fixed side plate. It may be provided in the orbiting wrap 333 positioned between the fixing wrap 323 facing the 322 .
  • the fixed end of the fixed lap 323 facing the fixed side plate 322 and the fixed side plate 322 and the fixed end are provided with both the first fixed circumferential skin 361 and the first turning skin 363 .
  • the contact of the free end of the orbiting wrap 333 positioned between the fixing wraps 323 facing the side plate 322 can be prevented more effectively.
  • first fixed evasion skin 361 and the first pivot skin 363 When both the first fixed evasion skin 361 and the first pivot skin 363 are provided, only the first fixed evasion skin 361 is provided as shown in FIG. This reduced area may be provided to be properly distributed to the first fixed circumferential skin 361 and the first turning skin 363 .
  • first fixed turning skin 361 and the first turning skin 363 are provided, only the first turning skin 363 is provided as shown in FIG. It may be provided so that the reduced area of the end is properly distributed to the first fixed evacuation skin 361 and the first swiveling skin 363 .
  • the reduced area can ensure the structural stability of the fixed wrap 323 and the orbiting wrap 333, and can prevent the breakage of the recessed or processed part by centrifugal force.
  • the compressor 10 may include the above-described second fixed evacuation part 362 and the second swiveling part 364 together.
  • the second pivoting skin 362 is provided on the fixed wrap 323 facing the rotation shaft 230
  • the second turning skin 364 is the fixed wrap facing the rotation shaft 230 . It may be provided in the orbiting wrap 333 facing the outer surface of the 323 and positioned between the fixing wrap 323 and the fixing side plate 322 .
  • the free end of the fixing lap 323 facing the rotation shaft 230 and the fixing facing the rotation shaft 230 are provided with both the second fixed evacuation skin 362 and the second swiveling skin 364 . It is possible to more effectively prevent contact between the fixed end of the orbiting wrap 333 facing the outer surface of the wrap 323 and positioned between the fixed wrap 323 and the fixed side plate 322 .
  • the second fixed evasion skin 362 and the second pivot skin 364 are provided, only the second fixed evasion skin 362 is provided as shown in FIG.
  • the area of the free end may be provided so as to be properly distributed between the second fixed evacuation skin 362 and the second swiveling skin 364 .
  • both the second fixed circumferential skin 362 and the second revolving skin 364 are provided, as shown in FIG. 8 , only the second turning skin 364 is provided and the reduced orbital wrap 333 is provided. ) may be provided such that the area of the fixed end is properly distributed to the second fixed evaporating skin 362 and the second swiveling skin 364 .
  • the reduced area can ensure the structural stability of the fixed wrap 323 and the orbiting wrap 333, and can prevent the breakage of the recessed or processed part by centrifugal force.
  • the compressor 10 includes the first fixed evasion skin 361 , the second fixed evasion skin 362 , and the first pivot skin 363 . ) and the second turning skin 364 may both be provided.
  • the contact between the fixed wrap 323 and the orbital wrap 333 due to thermal deformation that appears differently depending on the region where the fixed wrap 323 and the orbiting wrap 333 is located is reduced with the orbiting wrap 333. It can be effectively prevented through processing of a portion of the fixing wrap 323 .

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

Abstract

Un compresseur selon des modes de réalisation de la présente invention peut comprendre une partie d'évitement qui est fournie par constriction ou formation d'un évidement sur une zone partielle de l'enveloppe de fixation et/ou de l'enveloppe de rotation et est conçue pour étendre un espace entre l'enveloppe de fixation et l'enveloppe de rotation. Par conséquent, la présente invention peut empêcher le contact entre l'enveloppe de fixation et l'enveloppe de rotation en raison d'une déformation thermique lorsque le compresseur fonctionne. De plus, étant donné que seule une zone partielle de l'enveloppe de fixation et de l'enveloppe de rotation est traitée, la présente invention peut empêcher au maximum la fuite d'un fluide frigorigène et peut ainsi empêcher une réduction de l'efficacité de compression.
PCT/KR2021/002816 2020-04-20 2021-03-08 Compresseur WO2021215652A1 (fr)

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Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH084669A (ja) * 1994-06-20 1996-01-09 Tokico Ltd スクロール式流体機械
KR20150090164A (ko) * 2013-02-27 2015-08-05 가부시키가이샤 히다치 산키시스템 스크롤식 유체 기계
KR20170122015A (ko) * 2016-04-26 2017-11-03 엘지전자 주식회사 스크롤 압축기
KR20170122016A (ko) * 2016-04-26 2017-11-03 엘지전자 주식회사 스크롤 압축기
KR20200007548A (ko) * 2018-07-13 2020-01-22 엘지전자 주식회사 압축기

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR102481368B1 (ko) 2016-04-26 2022-12-26 엘지전자 주식회사 스크롤 압축기

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH084669A (ja) * 1994-06-20 1996-01-09 Tokico Ltd スクロール式流体機械
KR20150090164A (ko) * 2013-02-27 2015-08-05 가부시키가이샤 히다치 산키시스템 스크롤식 유체 기계
KR20170122015A (ko) * 2016-04-26 2017-11-03 엘지전자 주식회사 스크롤 압축기
KR20170122016A (ko) * 2016-04-26 2017-11-03 엘지전자 주식회사 스크롤 압축기
KR20200007548A (ko) * 2018-07-13 2020-01-22 엘지전자 주식회사 압축기

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