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WO2018190544A1 - Compresseur à spirale - Google Patents

Compresseur à spirale Download PDF

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Publication number
WO2018190544A1
WO2018190544A1 PCT/KR2018/003817 KR2018003817W WO2018190544A1 WO 2018190544 A1 WO2018190544 A1 WO 2018190544A1 KR 2018003817 W KR2018003817 W KR 2018003817W WO 2018190544 A1 WO2018190544 A1 WO 2018190544A1
Authority
WO
WIPO (PCT)
Prior art keywords
sealing member
scroll
sealing
frame
insertion groove
Prior art date
Application number
PCT/KR2018/003817
Other languages
English (en)
Inventor
Howon Lee
Yongkyu Choi
Cheolhwan Kim
Original Assignee
Lg Electronics Inc.
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Lg Electronics Inc. filed Critical Lg Electronics Inc.
Publication of WO2018190544A1 publication Critical patent/WO2018190544A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/02—Lubrication
    • 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
    • F01C19/00—Sealing arrangements in rotary-piston machines or engines
    • F01C19/005—Structure and composition of sealing elements such as sealing strips, sealing rings and the like; Coating of these elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/02—Lubrication
    • F04B39/0223—Lubrication characterised by the compressor type
    • F04B39/023—Hermetic compressors
    • F04B39/0238—Hermetic compressors with oil distribution channels
    • F04B39/0246—Hermetic compressors with oil distribution channels in the rotating shaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C27/00—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids
    • F04C27/007—Sealings for working fluid between radially and axially moving parts
    • 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
    • F04C27/008—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids for other than working fluid, i.e. the sealing arrangements are not between working chambers of the machine
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/02—Lubrication; Lubricant separation
    • F04C29/023—Lubricant distribution through a hollow driving shaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/02—Lubrication; Lubricant separation
    • F04C29/028—Means for improving or restricting lubricant flow
    • 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
    • F04C2240/603—Shafts with internal channels for fluid distribution, e.g. hollow shaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • 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
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2225/00—Synthetic polymers, e.g. plastics; Rubber
    • F05C2225/04—PTFE [PolyTetraFluorEthylene]
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2253/00—Other material characteristics; Treatment of material
    • F05C2253/04—Composite, e.g. fibre-reinforced

Definitions

  • This specification relates to a scroll compressor, and more particularly, a scroll compressor where a compression part is disposed below a motor part.
  • a scroll compressor is a compressor forming a compression chamber made of a suction chamber, an intermediate pressure chamber, and a discharge chamber between both scrolls while the plurality of scrolls perform a relative orbiting motion in an engaged state.
  • Such a scroll compressor may obtain a relatively high compression ratio as compared with other types of compressors while smoothly connecting suction, compression, and discharge strokes of refrigerant, thereby obtaining stable torque. Therefore, the scroll compressor is widely used for compressing refrigerant in an air conditioner or the like. Recently, a high-efficiency scroll compressor having a lower eccentric load and an operation speed at 180 Hz or higher has been introduced.
  • the scroll compressor may be categorized into a low pressure type where a suction pipe is communicated with an inner space of a casing which forms a low pressure part, and a high pressure type where a suction pipe is directly communicated with a compression chamber. Accordingly, in case of the low pressure type, a driving unit is installed at a suction space, a low pressure part. On the other hand, in case of the high pressure type, a driving unit is installed at a discharge space, a high pressure part.
  • Such a scroll compressor may be categorized into an upper compression type and a lower compression type according to a position of a driving unit and a compression unit.
  • a compression unit In case of the upper compression type, a compression unit is positioned above a driving unit.
  • a compression unit In case of the lower compression type, a compression unit is positioned below a driving unit.
  • a gas force is applied in a direction that an orbiting scroll becomes far from a fixed scroll, as a pressure of a compression chamber is increased.
  • leakage from a space between compression chambers occurs as the orbiting scroll becomes far from the fixed scroll. This may cause a compression loss.
  • a tip seal method or a back pressure method has been applied to the scroll compressor.
  • the tip seal method is used to insert a sealing member to a fore end of a fixed wrap and an orbiting wrap.
  • the back pressure method is used to pressurize an orbiting scroll or a fixed scroll towards another scroll by a pressure of a back pressure chamber forming an intermediate pressure or a discharge pressure and formed on a rear surface of the orbiting scroll or the fixed scroll.
  • a sealing member is installed between a rear surface of the orbiting scroll (or a rear surface of the fixed scroll) and a corresponding frame, and a back pressure chamber is formed inside or outside the sealing member.
  • a ring-shaped groove is formed at one member which forms a thrust surface, and a ring-shaped sealing member having a quadrangular sectional surface is inserted into the ring-shaped groove.
  • a refrigerant of an intermediate pressure compressed in a compression chamber when the compressor is operated, is introduced into the ring-shaped groove.
  • the sealing member is upward moved by the intermediate pressure to thus be adhered to another member, thereby forming a back pressure chamber.
  • a high sealing effect may be obtained in an axial direction, as the sealing member is upward moved towards another member by an intermediate pressure and contacts the another member.
  • the sealing member is formed in a ring shape, refrigerant leakage occurs from a gap between an outer circumferential surface of the sealing member and an outer side wall surface of the ring-shaped groove, in a case where a back pressure chamber is formed inside the sealing member.
  • refrigerant leakage occurs from a gap between an inner circumferential surface of the sealing member and an inner side wall surface of the ring-shaped groove. This may cause the back pressure chamber not to be effectively formed. The reason is as follows.
  • a radial interval is required between an inner circumferential surface of the sealing member and an inner side wall surface of the ring-shaped groove, or between an outer circumferential surface of the sealing member and an outer side wall surface of the ring-shaped groove.
  • the sealing member is formed in a ring shape having a quadrangular sectional surface, the sealing member cannot be contracted in a radial direction.
  • the sealing member since the sealing member is formed to have a quadrangular sectional surface, the sealing member has an increased weight. This may cause the sealing member not to be rapidly upward-moved when the scroll compressor is initially driven, resulting in delaying in forming a back pressure chamber. Further, if an axial thickness of the sealing member is small, a radial sealing area may be reduced, and the sealing member may have a shortened lifespan due to abrasion with another member. On the other hand, if a radial width of the sealing member is small, an axial sealing area may be reduced, and an area of the sealing member where an upward-movement pressure is applied with respect to a weight may be reduced. This may cause delay of an upward movement of the sealing member.
  • an intermediate part of a ring-shaped sealing member is cut-out such that the sealing member is widened a little in a radial direction when it is upward moved.
  • a pressure of a back pressure chamber leaks through the cut-out part, resulting in a limitation that the pressure of the back pressure chamber is not constantly maintained. If the pressure of the back pressure chamber is not constant, the orbiting scroll may have an unstable behavior. This may lower a sealing force with respect to a compression chamber between the orbiting scroll and the fixed scroll, resulting in increasing a compression loss.
  • an aspect of the detailed description is to provide a scroll compressor capable of obtaining a high axial sealing force and a high radial sealing force, by forming a sealing member in a ring shape and by forming the sealing member to have a displacement in a radial direction.
  • Another aspect of the detailed description is to provide a scroll compressor capable of forming a sealing member in a ring shape, and capable of forming a back pressure chamber within a short time by rapidly upward-moving the sealing member.
  • Another aspect of the detailed description is to provide a scroll compressor capable of reducing a weight of a sealing member, obtaining a radial sealing area and an axial sealing area, and obtaining a thickness of the sealing member against abrasion.
  • Another aspect of the detailed description is to provide a scroll compressor capable of stabilizing a behavior of an orbiting scroll by enhancing a sealing effect of a sealing member, and capable of preventing refrigerant leakage from a compression chamber.
  • a scroll compressor including: a sealing member inserted into a ring-shaped groove formed at one of two members which perform a sliding motion with respect to each other, and configured to perform a sealing function between contact surfaces of the two members while being upward moved by a pressure difference, wherein the sealing member is formed in a ring shape and is formed to have a ' ⁇ '-shaped sectional surface, and wherein an outer diameter of the sealing member is smaller than that of the ring-shaped groove for inserting the sealing member.
  • the sealing member is formed as a single body having no cut-out portion.
  • the part ' ⁇ ' which forms a radial sealing portion contacting an outer side wall surface of the ring-shaped groove is formed to be relatively thinner than the part ' ⁇ ' which forms an axial sealing portion by contacting a thrust surface of an opposite member.
  • a scroll compressor comprising: a first scroll; a second scroll which forms a compression chamber together with the first scroll while performing an orbiting movement with respect to the first scroll; a frame configured to support the second scroll by being coupled to the first scroll; a sealing member insertion groove formed in a ring shape, on at least one of one side surface of the second scroll and one side surface of the frame contacting the second scroll; and a sealing member formed in a ring shape, inserted into the sealing member insertion groove, and configured to divide an interval between the second scroll and the frame in a radial direction, wherein the sealing member is formed such that a sectional surface of an inner circumferential surface thereof is smaller than that of an outer circumferential surface thereof, and such that a second gap between the outer circumferential surface of the sealing member and an outer side wall surface of the sealing member insertion groove is smaller than or equal to a first gap between the inner circumferential surface of the sealing member and an inner side wall surface of the sealing member insertion groove.
  • the second gap is formed to be 0.05 ⁇ 1.0% with respect to an outer diameter of the sealing member.
  • a first chamfering portion is formed on at least one of an outer edge of the sealing member insertion groove and an outer edge of the sealing member.
  • the sealing member includes: a first sealing portion formed in a ring shape, and having one surface forming an axial sealing surface with the frame; and a second sealing portion extended from another surface of the first sealing portion in a ring shape, and having an outer circumferential surface forming a radial sealing surface with the outer side wall surface of the sealing member insertion groove. And an axial height of the first chamfering portion is formed to be smaller than or equal to an axial thickness of the first sealing portion.
  • the sealing member includes: a first sealing portion formed in a ring shape, and having one surface forming an axial sealing surface with the frame; and a second sealing portion extended from another surface of the first sealing portion in a ring shape, and having an outer circumferential surface forming a radial sealing surface with the outer side wall surface of the sealing member insertion groove. And an outer diameter of the first sealing portion is formed to be equal to an outer diameter of the second sealing portion.
  • the sealing member includes: a first sealing portion formed in a ring shape, and having one surface forming an axial sealing surface with the frame; and a second sealing portion extended from another surface of the first sealing portion in a ring shape, and having an outer circumferential surface forming a radial sealing surface with the outer side wall surface of the sealing member insertion groove. And an outer diameter of the first sealing portion is formed to be different from an outer diameter of the second sealing portion.
  • the second gap is formed to be 0.05 ⁇ 1.0% with respect to an outer diameter of the sealing member.
  • the sealing member is formed of Teflon (PEFE) mixed with carbon fibers.
  • the sealing member further includes a graphite material.
  • the sealing member is formed to have a ' ⁇ '-shaped sectional surface, and a part of the sealing member contacting the frame has a larger thickness than a part of the sealing member contacting the sealing member insertion groove.
  • a gap between the second scroll and the frame is formed such that an inner interval is larger than an outer interval in a radius direction based on the sealing member insertion groove.
  • a first passage for communicating the inner interval and the outer interval with each other is formed at the second scroll or the frame.
  • a second passage for communicating the outer interval with the compression chamber is formed at the first scroll or the frame.
  • a scroll compressor comprising: a casing having an inner space where oil is stored; a driving motor provided at the inner space of the casing; a rotation shaft coupled to the driving motor; a frame provided below the driving motor; a first scroll provided below the frame, and having a first wrap on one side surface thereof; a second scroll having a sealing member insertion groove on a surface thereof contacting the frame, provided between the frame and the first scroll, having a second wrap engaged with the first wrap, eccentrically-coupled to the rotation shaft such that the rotation shaft is overlapped with the second wrap in a radial direction, and forming compression chambers at a space between the second scroll and the first scroll while performing an orbiting movement with respect to the first scroll; and a sealing member formed in a ring shape, inserted into the sealing member insertion groove, provided between the frame and the second scroll, and configured to divide an interval between the frame and the second scroll into an inner interval and an outer interval, wherein the sealing member is formed such that a section
  • a plurality of oil passages for guiding the oil stored in the casing to an outer circumferential surface of the rotation shaft are formed at the rotation shaft. And at least one of the plurality of oil passages is formed to be communicated with the inner interval separated from the outer interval by the sealing member.
  • the outer interval is communicated with a compression chamber which forms an intermediate pressure between a suction pressure and a discharge pressure, among the compression chambers.
  • a communication passage for communicating the inner interval and the outer interval with each other is further provided at the second scroll or the frame. And a depressurizing unit is provided at the communication passage.
  • the interval between the frame and the second scroll is formed such that the outer interval is smaller than the inner interval. And a chamfering portion inclined towards the sealing member insertion groove is formed at an edge of the sealing member insertion groove contacting the outer interval.
  • the sealing member is formed to have a ' ⁇ '-shaped sectional surface, and an outer diameter of the sealing member is smaller than that of the sealing member insertion groove by 0.05 ⁇ 1.0%.
  • the sealing member is formed of Teflon (PEFE) mixed with carbon fibers.
  • the sealing member further includes a graphite material.
  • the scroll compressor according to the present invention may have the following advantages.
  • the sealing member provided between the second scroll and the frame is formed in a ring shape as a single body, the sealing member has a displacement in a radial direction by a pressure. This may enhance not only an axial sealing force but also a radial sealing fore of the sealing member, thereby preventing an operation delay when the scroll compressor is driven.
  • the sealing member may be prevented from being excessively adhered to the sealing member insertion groove, and a radial sealing force may be obtained. This may allow a back pressure chamber to be formed within a short time as the sealing member is upward moved rapidly.
  • the sealing member may maintain a constant pressure.
  • the orbiting scroll may have a stable behavior, and refrigerant leakage from the compression chamber may be prevented. This may enhance compression efficiency.
  • the sealing member has no cut-out portion, damage of the sealing member occurring when the sealing member is applied to a high compression-ratio compressor may be prevented. This may enhance reliability.
  • the sealing member since the sealing member includes the first and second sealing portions and the second sealing portion is formed to be thinner than the first sealing portion, the sealing member may have a reduced weight. This may allow the sealing member to be rapidly upward-moved even when the scroll compressor is initially driven, thereby enhancing compression efficiency.
  • first sealing portion is formed to have a large thickness
  • second sealing portion is formed to have a small thickness
  • the second sealing portion may be rapidly bent even when the scroll compressor is initially driven, resulting in forming a radial sealing portion.
  • FIG. 1 is a longitudinal sectional view of a lower compression-type scroll compressor in accordance with the present invention
  • FIG. 2 is a horizontal sectional view of a compression unit in FIG. 1;
  • FIG. 3 is a front view illustrating a part of a rotating shaft for explaining a sliding portion in FIG. 1;
  • FIG. 4 is a longitudinal sectional view illustrating an oil supply passage (oil feeding path) between a back pressure chamber and a compression chamber in FIG. 1;
  • FIG. 5 is a perspective view showing a sealing member disassembled from a scroll in FIG. 1;
  • FIG. 6 is a planar view showing an inserted state of the sealing member of FIG. 5 into a sealing member insertion groove;
  • FIG. 7 is a sectional view taken along line 'V-V' in FIG. 6;
  • FIG. 8A is a graph showing a compression ratio according to a driving time when a scroll compressor having a sealing member according to this embodiment is normally operated;
  • FIG. 8B is a graph showing a compression ratio according to a driving time when an operation of the scroll compressor having a sealing member according to this embodiment is delayed;
  • FIG. 9 is a graph showing a change of a compression ratio according to a ratio (%) of a radial interval of a sealing member with respect to an outer diameter of a sealing member insertion groove, in a scroll compressor having a sealing member according to this embodiment;
  • FIG. 10 is a schematic view for explaining a size of a sealing member according to this embodiment.
  • FIG. 11 is a longitudinal sectional view showing an embodiment of a fitting prevention unit of a sealing member according to this embodiment
  • FIG. 12 is a longitudinal sectional view showing an embodiment of an oil guiding unit of a sealing member insertion groove according to this embodiment
  • FIGS. 13A and 13B are longitudinal sectional views showing a stopped state and a driving state of a compressor with respect to a sealing member according to this embodiment
  • FIGS. 14 and 15 are schematic views showing other embodiments of a sealing member according to this embodiment.
  • FIGS. 16 and 17 are longitudinal sectional views showing other embodiments of a sealing member according to the present invention.
  • FIG. 18 is a longitudinal sectional view showing another embodiment to upward-move a sealing member in a scroll compressor according to the present invention.
  • a scroll compressor may be divided into a low pressure type in which a suction pipe communicates with an internal space of a casing constituting a low pressure portion and a high pressure type in which a suction pipe directly communicates with a compression chamber. Accordingly, in the low pressure type, a drive unit is provided in a suction space which is the low pressure portion, whereas in the high pressure type, a drive unit is provided in a discharge space which is the high pressure portion.
  • Such a scroll compressor may be divided into an upper compression type and a lower compression type according to positions of the drive unit and the compression unit.
  • a compressor in which the compression unit is located above the drive unit is referred to as an upper compression type
  • a compressor in which the compression unit is located below the drive unit is referred to as a lower compression type.
  • a scroll compressor of a type in which a rotating shaft overlaps an orbiting wrap on the same plane will be exemplarily described as a lower compression type scroll compressor.
  • This type of scroll compressor is known to be suitable for application to a refrigeration cycle under high temperature and high compression ratio conditions.
  • FIG. 1 is a longitudinal sectional view of a lower compression-type scroll compressor in accordance with the present invention
  • FIG. 2 is a horizontal sectional view of a compression unit of FIG. 1
  • FIG. 3 is a front view illustrating a part of a rotating shaft for illustrating a sliding portion in FIG. 1
  • FIG. 4 is a longitudinal sectional view illustrating an oil supply passage (oil feeding path) between a back pressure chamber and a compression chamber in FIG. 1.
  • a lower compression type scroll compressor may be provided with a motor unit 20 having a driving motor within a casing 10 to generate a rotational force, and a compression unit 30 located below the motor unit 20 and having a predetermined space (hereinafter, referred to as an intermediate space) 10a to compress refrigerant by receiving the rotational force of the motor unit 20.
  • a motor unit 20 having a driving motor within a casing 10 to generate a rotational force
  • a compression unit 30 located below the motor unit 20 and having a predetermined space (hereinafter, referred to as an intermediate space) 10a to compress refrigerant by receiving the rotational force of the motor unit 20.
  • the casing 10 may include a cylindrical shell 11 forming a hermetic container, an upper shell 12 forming the hermetic container by covering an upper portion of the cylindrical shell 11, and a lower shell 13 forming the hermetic container by covering a lower portion of the cylindrical shell 11 and simultaneously forming an oil storage space 10c.
  • a refrigerant suction pipe 15 may directly communicate with a suction chamber of the compression unit 30 through a lateral surface of the cylindrical shell 11, and a refrigerant discharge pipe 16 communicating with an upper space 10b of the casing 10 may be provided through a top of the upper shell 12.
  • the refrigerant discharge pipe 16 may correspond to a path through which compressed refrigerant discharged from the compression unit 30 to the upper space 10b of the casing 10 is discharged to outside.
  • the refrigerant discharge pipe 16 may be inserted up to a middle of the upper space 10b of the casing 10 to allow the upper space 10b to form a kind of oil separation space.
  • an oil separator (not shown) for separating oil mixed with refrigerant may be connected to the refrigerant suction pipe 15 within the casing 10 including the upper space 10b or within the upper space 10b.
  • the motor unit 20 may include a stator 21 and a rotor 22 rotating within the stator 21.
  • the stator 21 is provided with teeth and slots forming a plurality of coil winding portions (not shown) on an inner circumferential surface thereof along a circumferential direction, such that a coil 25 is wound therearound.
  • a second refrigerant passage P G2 is formed by combining a gap between the inner circumferential surface of the stator 21 and an outer circumferential surface of the rotor 22 with the coil winding portions.
  • a plurality of D-cut faces 21a are formed on an outer circumferential surface of the stator 21 along the circumferential direction.
  • the plurality of D-cut face 21a may form a first oil passage P O1 together with an inner circumferential surface of the cylindrical shell 11 to allow a flow of oil.
  • oil separated from refrigerant in the upper space 10b flows to the lower space 10c through the first oil passage P O1 and a second oil passage P O2 which will be described later.
  • a frame 31 forming the compression unit 30 may be fixedly coupled to an inner circumferential surface of the casing 10 with a predetermined interval below the stator 21.
  • An outer circumferential surface of the frame 31 may be shrink-fitted to or fixedly welded on an inner circumferential surface of the cylindrical shell 11.
  • a frame sidewall portion (first sidewall portion) 311 in an annular shape is formed at an edge of the frame 31, and a plurality of communication grooves 311b are formed on an outer circumferential surface of the first sidewall portion 311 along a circumferential direction.
  • the communication grooves 311b form a second oil passage P O2 together with a communication groove 322b of the first scroll 32 which will be described later.
  • a first bearing 312 for supporting a main bearing 51 of a rotating shaft 50 which will be described later is formed in a center of the frame 31, and a first bearing hole 312a may be formed through the first bearing 312 in an axial direction such that the main bearing 51 of the rotating shaft 50 is rotatably inserted and supported in a radial direction.
  • a fixed scroll hereinafter, referred to as a first scroll
  • a second scroll which is eccentrically connected to the rotating shaft 50.
  • the first scroll 32 may be fixedly coupled to the frame 31, but may also be movably coupled to the frame 31 in the axial direction.
  • the first scroll 32 may be provided with a fixed disk portion (hereinafter, referred to as a first disk portion 321) formed in a substantially disk shape, and a scroll sidewall portion (hereinafter, referred to as a second sidewall portion) 322 formed at an edge of the first disk portion 321 and coupled to a lower edge of the frame 31.
  • a fixed disk portion hereinafter, referred to as a first disk portion 321
  • a scroll sidewall portion hereinafter, referred to as a second sidewall portion
  • a suction port 324 through which the refrigerant suction pipe 15 and a suction chamber communicate with each other may be formed through one side (or portion) of the second sidewall portion 322, and a discharge port 325 which communicates with a discharge chamber and through which compressed refrigerant is discharged may be formed through a central portion of the first disk portion 321.
  • the discharge port 325 may be provided with a first discharge port 325a and a second discharge port 325b to independently communicate with a first compression chamber V1 and a second compression chamber V2 to be explained later. These discharge ports will be described in detail later.
  • the communication groove 322b is formed on an outer circumferential surface of the second sidewall portion 322, and forms a second oil passage P O2 for guiding collected oil to the lower space 10c, together with the communication grooves 311b of the first sidewall portion 311.
  • a discharge cover 34 for guiding refrigerant discharged from the compression chamber V to a refrigerant passage which will be described later may be coupled to a lower side of the first scroll 32.
  • An inner space of the discharge cover 34 may receive the first discharge port 325a and the second discharge port 325b and simultaneously receive an inlet of the first refrigerant passage P G1 for guiding refrigerants discharged from the compression chamber V through the discharge ports 325a and 325b to the upper space 10b of the casing 10, more particularly, a space between the motor unit 20 and the compression unit 30.
  • the first refrigerant passage P G1 may be formed sequentially through the second sidewall portion 322 of the fixed scroll 32 and the first sidewall portion 311 of the frame 31 from an inside of a passage separation unit 40, namely, from a side of the rotating shaft 50, which is located at an inside based on the passage separation unit 40.
  • the second oil passage P O2 is formed at an outside of the passage separation unit 40 to communicate with the first oil passage P O1 .
  • a fixed wrap (hereinafter, referred to as a first wrap) 323 forming the compression chamber V in engagement with an orbiting wrap (hereinafter, referred to as a second wrap) 33 which will be described later may be formed on an upper surface of the first disk portion 321.
  • the first wrap 323 will be described later together with the second wrap 332.
  • a second bearing 326 for supporting a sub-bearing 52 of the rotating shaft 50 which will be described later may be formed in the center of the first disk portion 321, and a second bearing hole 326a may be formed through the second bearing 326 in an axial direction to support the sub-bearing 52 in a radial direction.
  • the first disk portion 321 is provided with a bypass hole 381 for bypassing a part of refrigerant to be compressed in advance, and a bypass valve 385 is installed at an outlet end of the bypass hole 381.
  • the bypass hole 381 may be provided by one or more in number at an appropriate position along a moving direction of the compression chamber V so as to be located between the suction chamber and the discharge chamber. And the bypass hole 381 may be formed such that its interval may become narrow towards a discharge side from the second compression chamber V2 having a large compression gradient.
  • the second scroll 33 may be provided with an orbiting disk portion (hereinafter, referred to as second disk portion) 331 formed in a substantially disk shape.
  • a second wrap 332 forming a compression chamber in engagement with the first wrap 331 may be formed on a lower surface of the second disk portion 331.
  • the second wrap 332 may be formed in an involute shape together with the first wrap 323, but may also be formed in various other shapes.
  • the second wrap 332 may have a shape in which a plurality of arcs having different diameters and origins are connected, and the outermost curve may be formed in a substantially elliptical shape having a major axis and a minor axis.
  • the first wrap 323 may be formed in a similar manner.
  • a rotating shaft coupling portion 333 which forms an inner end portion of the second wrap 332 and to which an eccentric portion 53 of the rotating shaft 50 to be described later is rotatably inserted may be formed through a central portion of the second disk portion 331 in an axial direction.
  • An outer circumferential portion of the rotating shaft coupling portion 333 is connected to the second wrap 332 to form the compression chamber V together with the first wrap 322 during a compression process.
  • the rotating shaft coupling portion 333 may be formed at a height overlapping with the second wrap 332 on the same plane, and thus the eccentric portion 53 of the rotating shaft 50 may be formed at a height overlapping with the second wraps 332 on the same plane. Accordingly, a repulsive force and a compressive force of refrigerant offset each other while being applied to the same plane based on the second disk portion, thereby preventing an inclination of the second scroll 33 due to an action of the compressive force and repulsive force.
  • the rotating shaft coupling portion 333 is provided with a concave portion 335 formed on an outer circumferential portion facing an inner end portion of the first wrap 323 and engaged with a protruding portion 328 of the first wrap 323 which will be described later.
  • an increasing portion 335a having a thickness increasing from an inner circumferential portion to an outer circumferential portion of the rotating shaft coupling portion 333 at an upstream side along the forming direction of the compression chamber V. Accordingly, a compression path of the first compression chamber V1 immediately before discharge may extend and thus a compression ratio of the first compression chamber V1 may be increased to be similar to a compression ratio of the second compression chamber V2.
  • the first compression chamber V1 is a compression chamber formed between an inner surface of the first wrap 323 and an outer surface of the second wrap 332, and will be described later separately from the second compression chamber V2.
  • an arcuate compression surface 335b having an arcuate shape.
  • a diameter of the arcuate compression surface 335b is decided by a thickness of the inner end portion of the first wrap 323 (i.e., a thickness of the discharge end) and an orbiting radial of the second wrap 332.
  • a thickness of the inner end portion of the first wrap 323 increases, a diameter of the arcuate compression surface 335b increases.
  • a thickness of the second wrap around the arcuate compression surface 335b may increase to ensure durability, and the compression path may extend to increase the compression ratio of the second compression chamber V2 to that extent.
  • the protruding portion 328 protruding toward the outer circumferential portion of the rotating shaft coupling portion 333 may be formed adjacent to an inner end portion (a suction end or starting end) of the first wrap 323 corresponding to the rotating shaft coupling portion 333.
  • the protruding portion 328 may be provided with a contact portion 328a protruding therefrom and engaged with the concave portion 335.
  • the inner end portion of the first wrap 323 may be formed to have a larger thickness than other portions.
  • the compression chamber V may be formed between the first disk portion 321 and the first wrap 323, and between the second wrap 332 and the second disk portion 331, and have a suction chamber, an intermediate pressure chamber, and a discharge chamber which are formed sequentially along a proceeding direction of the wrap.
  • the compression chamber V may include the first compression chamber V1 formed between an inner surface of the first wrap 323 and an outer surface of the second wrap 332, and the second compression chamber V2 formed between an outer surface of the first wrap 323 and an inner surface of the second wrap 332.
  • the first compression chamber V1 includes a compression chamber formed between two contact points P11 and P12 generated in response to the inner surface of the first wrap 323 being brought into contact with the outer surface of the second wrap 332, and the second compression chamber V2 includes a compression chamber formed between two contact points P21 and P22 generated in response to the outer surface of the first wrap 323 being brought into contact with the inner surface of the second wrap 332.
  • ⁇ a large angle of angles formed between two lines, which connect a center of the eccentric portion, namely, a center O of the rotation shaft coupling portion to the two contact points P11 and P12, respectively, is defined as ⁇ within the first compression chamber V2 just before discharge
  • the angle ⁇ at least just before the discharge is larger than 360° (i.e., ⁇ ⁇ 360°)
  • a distance ll between normal vectors at the two contact points (P11, P12) also has a value greater than zero.
  • the first compression chamber immediately before the discharge may have a smaller volume as compared to a case where a fixed wrap and an orbiting wrap have a shape of an involute curve. Therefore, the compression ratios of the first and second compression chambers V1 and V2 can all be improved even without increasing the sizes of the first wrap 323 and the second wrap 332.
  • the second scroll 33 may be orbitally provided between the frame 31 and the fixed scroll 32.
  • An Oldham ring 35 for preventing rotation of the second scroll 33 may be provided between an upper surface of the second scroll 33 and a lower surface of the frame 31, and a sealing member 36 for forming a back pressure chamber S1 to be explained later may be provided at an inner side rather than the Oldham ring 35.
  • An intermediate pressure space is formed by an oil feeding hole 321a provided on the second scroll 32 at an outside of the sealing member 36.
  • the intermediate pressure space communicates with an intermediate compression chamber V and thus is filled with refrigerant of intermediate pressure, so as to serve as a back pressure chamber. Therefore, a back pressure chamber formed at an inside with respect to the sealing member 36 may be referred to as a first back pressure chamber S1, and an intermediate pressure space formed at an outside may be referred to as a second back pressure chamber S2.
  • the back pressure chamber S1 is a space formed by a lower surface of the frame 31 and an upper surface of the second scroll 33 based on the sealing member 36, and will be described later again along with the sealing member.
  • the passage separation unit 40 is provided in the intermediate space 10a, which is a via space formed between a lower surface of the motor unit 20 and an upper surface of the compression unit 30, to play the role of preventing refrigerant discharged from the compression unit 30 from interfering with oil flowing from the upper space 10b of the motor unit 20 which is an oil separation space to the lower space 10c of the compression unit 30 which is an oil storage space.
  • the passage separation unit 40 includes a passage guide for dividing the first space 10a into a space through which refrigerant flows (hereinafter, referred to as a refrigerant flow space) and a space through which oil flows (hereinafter, referred to as an oil flow space).
  • the first space 10a may be divided into the refrigerant flow space and the oil flow space by only the passage guide, but according to circumstances, a plurality of passage guides may be combined to perform the role of the passage guide.
  • the passage separation unit 40 includes a first passage guide 410 provided in the frame 31 and extending upward, and a second passage guide 420 provided in the stator 21 and extending downward.
  • the first passage guide 410 and the second passage guide 420 may overlap each other in an axial direction to divide the intermediate space 10a into the refrigerant flow space and the oil flow space.
  • first passage guide 410 may be formed in an annular shape and fixedly coupled to the upper surface of the frame 31, and the second passage guide 420 may extend from an insulator which is inserted into the stator 21 and for insulating winding coils.
  • the first passage guide 410 may include a first annular wall portion 411 extending upward from an outer side, a second annular wall portion 412 extending upward from an inner side, and an annular surface portion 413 extending in a radial direction to connect the first annular wall portion 411 and the second annular wall portion 412.
  • the first annular wall portion 411 may be formed higher than the second annular wall portion 412, and the annular surface portion 413 may be provided with a refrigerant through hole formed from the compression unit 30 to the intermediate space 10a in a communicating manner.
  • a balance weight 26 is located at an inside of the second annular wall portion 412, namely, in a rotational shaft direction, and coupled to the rotor 22 or the rotating shaft 50 to rotate. At this time, refrigerant may be stirred while the balance weight 26 rotates, but the second annular wall portion 412 may prevent the refrigerant from moving toward the balance weight 26 to suppress the refrigerant from being stirred by the balance weight 26.
  • the second flow guide 420 may include a first extending portion 421 extending downward from the outside of the insulator and a second extending portion 422 extending downward from the inside of the insulator.
  • the first extending portion 421 is formed to overlap the first annular wall portion 411 in the axial direction to play a role of separating the refrigerant flow space from the oil flow space.
  • the second extending portion 422 may not be formed as necessary. Even when it is formed, the second extending portion 422 is preferably formed not to overlap the second annular wall portion 412 in the axial direction, or formed at a sufficient distance from the second annular wall portion 412 in a radial direction, such that the refrigerant can sufficiently flow even if it overlaps the second annular wall portion 412.
  • an upper portion of the rotating shaft 50 is press-fitted into the center of the rotor 22 while a lower portion thereof is coupled to the compression unit 30 to be supported in the radial direction. Accordingly, the rotating shaft 50 transfers the rotational force of the motor unit 20 to the orbiting scroll 33 of the compression unit 30. Then, the second scroll 33 eccentrically coupled to the rotating shaft 50 performs an orbiting motion with respect to the first scroll 32.
  • a main bearing (hereinafter, referred to as a first bearing) 51 may be formed at a lower portion of the rotating shaft 50 to be inserted into the first bearing hole 312a of the frame 31 and supported in a radial direction
  • a sub-bearing (hereinafter, referred to as a second bearing) 52 may be formed at a lower side of the first bearing 51 to be inserted into the second bearing hole 326a of the first scroll 32 and supported in a radial direction.
  • the eccentric portion 53 may be provided between the first bearing 51 and the second bearing 52 in a manner of being inserted into the rotating shaft coupling portion 333.
  • the first bearing 51 and the second bearing 52 may be coaxially formed to have the same axial center, and the eccentric portion 53 may be eccentrically formed in the radial direction with respect to the first bearing 51 or the second bearing 52.
  • the second bearing 52 may be eccentrically formed with respect to the first bearing 51.
  • the eccentric portion 53 should be formed in such a manner that its outer diameter is smaller than an outer diameter of the first bearing 51 and larger than an outer diameter of the second bearing 52 to be advantageous in coupling the rotating shaft 50 through the respective bearing holes 312a and 326a and the rotating shaft coupling portion 333.
  • the rotating shaft 50 may be inserted even when the outer diameter of the second bearing 52 is not smaller than the outer diameter of the eccentric portion 53.
  • an oil supply passage 50a for supplying oil to each bearing and the eccentric portion may be formed within the rotating shaft 50 along the axial direction.
  • the oil supply passage 50a may be formed from a lower end of the rotating shaft 50 to approximately a lower end or a middle height of the stator 21 or a position higher than an upper end of the first bearing 31 in a grooving manner.
  • the oil supply passage 50a may also be formed by penetrating through the rotating shaft 50 in an axial direction.
  • an oil feeder 60 for pumping up oil filled in the lower space 10c may be coupled to the lower end of the rotating shaft 50, namely, a lower end of the second bearing 52.
  • the oil feeder 60 may include an oil supply pipe 61 inserted into the oil supply passage 50a of the rotating shaft 50, and a blocking member 62 for blocking an introduction of foreign materials by receiving the oil supply pipe 61 therein.
  • the oil supply pipe 61 may be located to be immersed in oil of the lower space 10c through the discharge cover 34.
  • a sliding portion oil supply path F1 connected to the oil supply passage 50a to supply oil to each sliding portion is formed in each bearing 51 and 52 and the eccentric portion 53 of the rotating shaft 50.
  • the sliding portion oil supply path F1 may include a plurality of oil supply holes 511, 521 and 531 formed through the oil supply passage 50a toward an outer circumferential surface of the rotating shaft 50, and a plurality of oil supply grooves 512, 522 and 532 communicating with the oil supply holes 511, 521 and 531, respectively, to lubricate each bearing 51, 52 and the eccentric portion 53.
  • first oil supply hole 511 and the first oil supply groove 512 are formed in the first bearing 51, and the second oil supply hole 521 and the second oil supply groove 522 are formed in the second bearing 52. Also, the third oil supply hole 531 and the third oil supply groove 532 are formed in the eccentric portion 53.
  • Each of the first oil supply groove 512, the second oil supply groove 522, and the third oil supply groove 532 is formed in a slot shape extending in an axial or inclined direction.
  • a first connection groove 541 and a second connection groove 541 each formed in an annular shape may be formed between the first bearing 51 and the eccentric portion 53 and between the eccentric portion 53 and the second bearing 52, respectively.
  • the first connection groove 541 communicates with a lower end of the first oil supply groove 512 and the second oil supply groove 522 is connected with the second connection groove 542. Accordingly, a part of oil that lubricates the first bearing 51 through the first oil supply groove 512 flows down to be collected into the first connection groove 541, and then introduced into the first back pressure chamber s1, thereby forming back pressure of discharge pressure.
  • oil that lubricates the second bearing 52 through the second oil supply groove 522 and oil that lubricates the eccentric portion 53 through the third oil supply groove 532 are collected into the second connection groove 542, and then introduced into the compression unit 30 through a space between a front end surface of the rotating shaft coupling portion 333 and the first disk portion 321.
  • a small amount of oil sucked up toward an upper end of the first bearing 51 flows out of a bearing surface from an upper end of the first bearing portion 312 of the frame 31 and flows down toward an upper surface 31a of the frame 31 along the first shaft bearing portion 312. Afterwards, the oil is collected into the lower space 10c through the oil passages P O1 and P O2 consecutively formed on an outer circumferential surface of the frame 31 (or a groove communicated from the upper surface to the outer circumferential surface) and an outer circumferential surface of the first scroll 32.
  • oil discharged from the compression chamber V to the upper space 10b of the casing 10 together with refrigerant is separated from the refrigerant in the upper space 10b of the casing 10 and collected into the lower space 10c through the first oil passage P O1 formed on an outer circumferential surface of the motor unit 20 and the second oil passage P O2 formed on an outer circumferential surface of the compression unit 30.
  • the passage separation unit 40 is provided between the motor unit 20 and the compression unit 30.
  • oil which is separated from refrigerant in the upper space 10b may flow toward the lower space 10c along the passages P O1 and P O2 , without being re-mixed with refrigerant which is discharged from the compression unit 20 and flows toward the upper space 10b, and the refrigerant moving toward the upper surface 10b may flow toward the upper pace 10b along the passages P G1 and P G2 .
  • the second scroll 33 is provided with a compression chamber oil supply path F2 for supplying oil sucked up through the oil supply passage 50a into the compression chamber V.
  • the compression chamber oil supply path F2 is connected to the sliding portion oil supply path F1.
  • the compression chamber oil supply path F2 may include a first oil supply path 371 communicating the oil supply passage 50a with the second back pressure chamber S2 forming an intermediate pressure space, and a second oil supply path 372 communicating the second back pressure chamber S2 with the intermediate pressure chamber of the compression chamber V.
  • the compression chamber oil supply path may also be formed to communicate directly with the intermediate pressure chamber from the oil supply passage 50a without passing through the second back pressure chamber S2.
  • a refrigerant passage for communicating the second back pressure chamber S2 with the intermediate pressure chamber V should be separately provided, and an oil passage for supplying oil to the Oldham ring 35 located in the second back pressure chamber S2 should be separately provided.
  • the first oil supply path 371 is provided with a first orbiting passage portion 371a formed from an upper surface down to a middle of the second disk portion 331 in a thickness direction, a second orbiting passage portion 371b formed from the first orbiting passage portion 371a toward an outer circumferential surface of the second disk portion 331, and a third orbiting passage portion 371c formed through the upper surface of the second disk portion 331 from the second orbiting passage portion 371b.
  • the first orbiting passage portion 371a is located at a position belonging to the first back pressure chamber S1
  • the third orbiting passage portion 371c is located at a position belonging to the second back pressure chamber S2.
  • a pressure reducing rod 375 is inserted into the second orbiting passage portion 371b to reduce pressure of oil which flows from the first back pressure chamber S1 to the second back pressure chamber S2 through the first oil supply passage 371. Accordingly, a sectional area of the second orbiting passage portion 371b excluding the pressure reducing rod 375 is formed to be smaller than that of the first orbiting passage portion 371a or the third orbiting passage portion 371c.
  • a fourth orbiting passage portion 371d may be formed from the end portion of the third orbiting passage portion 371c toward an outer circumferential surface of the second disk portion 331.
  • the fourth orbiting passage portion 371d may be formed as a groove on an upper surface of the second disk portion 331 as illustrated in FIG. 4, or may be formed as a hole within the second disk portion 331.
  • the second oil supply passage 372 is provided with a first fixed passage portion 372a on an upper surface of the second sidewall portion 322 in a thickness direction, a second fixed passage portion 372b formed from the first fixed passage portion 372a in a radial direction, and a third fixed passage portion 372c communicating the second fixed passage portion 372b with the intermediate pressure chamber V.
  • an unexplained reference numeral 70 denotes an accumulator.
  • a lower compression type scroll compressor according to the present embodiment operates as follows.
  • refrigerant supplied from an outside of the casing 10 through the refrigerant suction pipe 15 is introduced into the compression chamber V, and compressed as a volume of the compression chamber V is reduced by the orbiting motion of the orbiting scroll 33.
  • the refrigerant is then discharged into an inner space of the discharge cover 34 through the first discharge port 325a and the second discharge port 325b.
  • noise is reduced from the refrigerant discharged into the inner space of the discharge cover 34 while the refrigerant circulates within the inner space of the discharge cover 34.
  • the noise-reduced refrigerant flows to a space between the frame 31 and the stator 21, and then is introduced into an upper space of the motor unit 20 through a gap between the stator 21 and the rotor 22.
  • Oil is separated from the refrigerant in the upper space of the motor unit 20. Accordingly, the refrigerant is discharge out of the casing 10 through the refrigerant discharge pipe 16, while the oil is collected back into the lower space 10c as the oil storage space of the casing 10 through a passage between the inner circumferential surface of the casing 10 and the stator 21 and a passage between the inner circumferential surface and the outer circumferential surface of the compression unit 30. This series of processes is repeated.
  • the oil in the lower space 10c is sucked up through the oil supply passage 50a of the rotating shaft 50, so as to lubricate the first bearing 51, the second bearing 52, and the eccentric portion 53 through the oil supply holes 511, 521 and 531 and the oil supply grooves 512, 522 and 532, respectively.
  • oil that lubricates the first bearing 51 through the first oil supply hole 511 and the first oil supply groove 512 is collected into the first connection groove 51 between the first bearing 51 and the eccentric portion 53, and then introduced into the first back pressure chamber S1.
  • This oil forms substantial discharge pressure, and thus the first back pressure chamber S1 is also filled with substantial discharge pressure. Therefore, a center portion of the second scroll 33 may be supported by the discharge pressure in an axial direction.
  • the oil in the first back pressure chamber S1 is moved to the second back pressure chamber S2 through the first oil supply passage 371 due to a pressure difference from the second back pressure chamber S2.
  • the pressure reducing rod 375 provided in the second orbiting passage portion 371b forming the first oil supply passage 371 allows pressure of the oil flowing toward the second back pressure chamber S2 to be reduced to intermediate pressure.
  • the oil flowing to the second back pressure chamber (intermediate pressure space) S2 supports an edge portion of the second scroll 33 and simultaneously moves to the intermediate pressure chamber V through the second oil supply passage 372 due to a pressure difference from the intermediate pressure chamber V.
  • the second oil supply passage 372 plays a role of a passage through which the refrigerant and the oil alternatively flow according to the pressure difference between the second back pressure chamber S2 and the intermediate pressure chamber V.
  • the back pressure chamber is formed on a rear surface of the second scroll, i.e., an upper surface of the second scroll, in order to prevent the second scroll from being spaced apart from the first scroll by being pushed by a pressure of the compression chamber.
  • the sealing member is provided on a lower surface of the frame and on an upper surface of the second scroll
  • the first back pressure chamber is formed between the second scroll and the frame
  • the second back pressure chamber is formed between the second scroll and the first scroll.
  • the sealing member preferably has an excellent sealing force between the frame and the second scroll, and an excellent abrasion resistance with consideration of a friction by an orbiting movement of the second scroll.
  • the sealing member is preferably formed of a material which can be rapidly upward-moved even at a low pressure since it performs a sealing function in an axial direction while being upward moved by a pressure, in an inserted state into a sealing member insertion groove of the second scroll.
  • FIG. 5 is a disassembled perspective view of a sealing member according to this embodiment
  • FIG. 6 is a planar view showing an inserted state of the sealing member of FIG. 5 into a sealing member insertion groove
  • FIG. 7 is a sectional view taken along line 'V-V' in FIG. 6.
  • the sealing member according to this embodiment 36 may be formed as a ring-shaped single body having no cut-out portion at a middle part thereof.
  • the sealing member 36 is preferably formed of a material which is light and bendable by a pressure (e.g., teflon).
  • the sealing member 36 may include a first sealing portion 361 formed in a ring shape and forming an axial sealing surface as its upper surface contacts a lower surface of the frame 31, and a second sealing portion 362 downward-extended from an edge of a lower surface of the first sealing portion 361 in a ring shape, and forming a radial sealing surface as its outer circumferential surface contacts an outer side wall surface of a sealing member insertion groove 336.
  • the sealing member 36 may be formed to entirely have a ' ⁇ '-shaped sectional surface. Accordingly, the first sealing portion 361 forms a free end at an inner circumferential surface 36a of the sealing member 36, i.e., an opposite end to an end from which the second sealing portion 362 is extended, whereas the second sealing portion 362 forms a free end at a lower end 362a, i.e., an opposite end to an end from which the first sealing portion 361 is extended.
  • the second sealing portion 362 forms a radial sealing portion by being adhered to an outer side wall surface 336b of the sealing member insertion groove 336.
  • the sealing member 36 (precisely, the first sealing portion) may be formed such that its inner diameter (D1) may be larger than an inner diameter (D2) of the sealing member insertion groove 336 by a first gap (G1), and the sealing member 36 (precisely, the second sealing portion) may be formed such that its outer diameter (D3) may be smaller than an outer diameter (D4) of the sealing member insertion groove 336 by a second gap (G2).
  • high-pressure fluid (refrigerant and oil) inside the sealing member 36 is introduced into the sealing member insertion groove 336 through the first gap (G1) formed between an inner side wall surface 336a of the sealing member insertion groove 336 and the inner circumferential surface 36a of the sealing member 36. And the sealing member 36 may be upward moved by a pressure of the fluid. Further, as the second gap (G2) is formed between the outer side wall surface 336b of the sealing member insertion groove 336 and an outer circumferential surface 36b of the sealing member 36, the sealing member 36 may be rapidly upward moved without interference with the sealing member insertion groove 336, through a non-contact or a slidable contact.
  • the sealing member 36 As the sealing member 36 according to this embodiment is formed in a ring-shape, a movement of the sealing member 36 in upper and lower directions is restricted by the size of the first gap (G1, G2), i.e., a gap between the inner circumferential surface 36a of the sealing member 36 and the inner side wall surface 336a of the sealing member insertion groove 336, and a gap between the outer circumferential surface 36b of the sealing member 36 and the outer side wall surface 336b of the sealing member insertion groove 336.
  • G1, G2 a gap between the inner circumferential surface 36a of the sealing member 36 and the inner side wall surface 336a of the sealing member insertion groove 336
  • the sealing member 36 may not be smoothly upward-moved because the inner circumferential surface 36a and the outer circumferential surface 36b of the sealing member 36 contact the sealing member insertion groove 336.
  • the sealing member 36 according to this embodiment is adhered to the outer side wall surface 336b of the sealing member insertion groove 336, thereby performing a sealing function. Accordingly, if the second gap (G2) is too narrow, the second sealing portion 362 is excessively adhered to the outer side wall surface 336b of the sealing member insertion groove 336.
  • sealing member 36 may be slowly upward-moved or to be abraded, or may cause the outer circumferential surface 36b of the sealing member 36 to be fitted into a space between the frame 31 and the second scroll 33. If the second gap (G2) is too large, refrigerant leakage may occur because a space between the outer circumferential surface 36b of the second sealing portion 362 and the outer side wall surface 336b of the sealing member insertion groove 336 does not have a sufficient sealing area.
  • the first and second gaps (G1, G2) are formed to be within a predetermined range such that the sealing member 36 is rapidly and smoothly operated with effectively restricting refrigerant leakage.
  • the sealing member 36 may be preferably formed such that the first gap (G1) may be larger than the second gap (G2), and the second gap (G2) may be 0.05 ⁇ 1.0% of the outer diameter (D3) of the sealing member 36.
  • FIG. 8A is a graph showing a compression ratio according to a driving time when a scroll compressor having a sealing member according to this embodiment is normally operated
  • FIG. 8B is a graph showing a compression ratio according to a driving time when an operation of the scroll compressor having a sealing member according to this embodiment is delayed.
  • FIG. 8A shows that a discharge pressure ratio is increased up to a preset pressure as a predetermined time lapses when the sealing member 36 is normally operated, and the increased discharge pressure ratio is maintained.
  • FIG. 8B shows that a discharge pressure ratio is increased up to a value near a preset pressure when the sealing member 36 is abnormally operated, and the increased discharge pressure ratio is drastically lowered without being maintained.
  • FIG. 8A shows that an intermediate pressure ratio is constantly increased when the compressor is driven, and the increased intermediate pressure ratio is maintained during an operation time.
  • FIG. 8B shows that an intermediate pressure ratio is excessively increased and lowered when the compressor is driven, and the intermediate pressure ratio is drastically lowered with the discharge pressure ratio after being maintained for a predetermined time.
  • the reason why a pressure of the second back pressure chamber (S2) which forms an intermediate pressure space is temporarily increased is as follows. Firstly, high-pressure oil is introduced into the second back pressure chamber (S2) as the first back pressure chamber (S1) is not formed, and a pressure of the second back pressure chamber (S2) is temporarily increased due to the high-pressure oil. During this process, a back pressure force is generated to some degree. However, since the pressure of the back pressure chamber is lower than a discharge pressure of the compression chamber, leakage occurs from a space between the compression chambers.
  • FIG. 9 is a graph showing a change of a compression ratio according to a ratio (%) (hereinafter, an interval ratio) of a radial interval (especially, a second interval) of the sealing member, with respect to an outer diameter of the sealing member insertion groove.
  • the interval ratio is preferably formed to be within a range of 0.05 ⁇ 1.0%.
  • An operation of the sealing member according to this embodiment is variable according to a shape of the sealing member.
  • first sealing portion 361 if the first sealing portion 361 is too thin, reliability may be lowered due to a low abrasion resistance. On the other hand, if the first sealing portion 361 is too thick, an operation delay may occur due to a heavy weight.
  • the second sealing portion 362 is too thin, reliability may be lowered, and a sealing force may be lowered because the sealing member is excessively sensitive to a pressure change of the first back pressure chamber (S1). On the other hand, if the second sealing portion 362 is too thick, a sealing force may be lowered as a transformation due to a pressure difference between inside and outside of the sealing member 36 is not smooth.
  • FIG. 10 is a schematic view for explaining a size of the sealing member according to this embodiment.
  • the first sealing portion 361 of the sealing member according to this embodiment may be formed such that a radial width (L1) may be larger than or equal to an axial thickness (t1).
  • the second sealing portion 362 may be formed such that a radial thickness (t2) may be smaller than or equal to an axial length (L2).
  • the axial thickness (t1) of the first sealing portion 361 may be greater than the radial thickness (t2) of the second sealing portion 362.
  • the axial thickness (t1) of the first sealing portion 361 may be formed to be larger than or equal to a maximum interval (generally, an interval when the compressor is stopped) (G4) between the frame 31 and the second scroll 33 outside the sealing member 36 (at the second back pressure chamber side).
  • a maximum interval generally, an interval when the compressor is stopped
  • the sealing member 36 (precisely, an outer circumferential surface of the first sealing portion) may be pushed to be bent towards the second back pressure chamber, by oil of the first back pressure chamber (S1). This may cause an edge of the outer circumferential surface 36b of the sealing member 36 to be positioned between the frame 31 and the second scroll 33.
  • a fitting prevention unit 336c which forms a first chamfering portion is formed at an edge of the sealing member insertion groove 336, thereby preventing the sealing member 36 from being positioned between the frame 31 and the second scroll 33.
  • the fitting prevention unit 336c may be formed to have a stair-stepped surface or a curved surface. However, the fitting prevention unit 336c may be formed to be inclined with consideration of a processability, etc.
  • the fitting prevention unit 336c is preferably formed such that a height (H3) of its lower end, i.e., a region contacting the outer side wall surface 336b of the sealing member insertion groove 336, is within a range of the first sealing portion 361 at least when the sealing member 36 contacts the frame 31.
  • H3 a height of its lower end, i.e., a region contacting the outer side wall surface 336b of the sealing member insertion groove 336
  • the fitting prevention unit 336c may be formed at an edge of an outer circumferential surface of the sealing member, or may be formed at an edge of the sealing member insertion groove and an edge of the sealing member, respectively.
  • the sealing member 36 is formed to have a ' ⁇ '-shaped sectional surface as aforementioned, the first sealing portion 361 which forms a frictional surface has a smaller thickness than the conventional sealing member having a quadrangular sectional surface. Accordingly, the sealing member 36 is preferably formed of a material having an abrasion resistance.
  • the sealing member 36 may be formed of Teflon (PEFE) to which an abrasion-resistant additive is added.
  • PEFE Teflon
  • powder particles or carbon fibers may be used.
  • carbon fibers not powder particles may be preferably used. The reason is because it is easier for powder particles to be separated from Teflon, than for carbon fibers to be broken.
  • the sealing member 36 may further include a lubricant additive such as graphite.
  • a lubricant additive such as graphite.
  • the sealing member 36 may have its abrasion degree significantly reduced due to an enhanced lubricity.
  • the first back pressure chamber (S1) is formed between a lower surface of the frame 31 and an upper surface of the second disk portion 331 of the second scroll 33.
  • a stair-stepped surface for forming the first back pressure chamber (S1) is formed on the lower surface of the frame 31 or on the upper surface of the second disk portion 331 (on the second disk portion in the drawings).
  • a second scroll height (H1) inside the sealing member insertion groove 336 i.e., a height of a side where the first gap (G1) is formed
  • a second scroll height (H2) outside the sealing member insertion groove 336 i.e., a height of a side where the second gap (G2) is formed.
  • an inner side surface 331b positioned at an inner side than the sealing member insertion groove 336 on a rear surface of the second disk portion 331, is lower than an outer side surface 331c positioned at an outer side than the sealing member insertion groove 336 and forming a thrust bearing surface.
  • a third gap (G3) between the frame 31 and the second scroll 33 inside the sealing member insertion groove 336 which is directly connected to the first gap (G1) is formed to be larger than a fourth gap (G4) between the frame 31 and the second scroll 33 outside the sealing member insertion groove 336 which is directly connected to the second gap (G2)
  • a space where the first back pressure chamber (S1) is formed may be provided on the inner side surface 331b of the second disk portion 331. Further, high-pressure fluid may be rapidly introduced to the first gap (G1).
  • an oil guiding portion 336d which forms a second chamfering portion and configured to guide oil to the sealing member insertion groove 336, may be formed at an edge of the sealing member insertion groove 336.
  • the oil guiding portion 336d forms a chamfering portion at an edge where the inner side surface 331b of the second scroll 33 is connected to the inner side wall surface 336a of the sealing member insertion groove 336, thereby rapidly introducing a high-pressure fluid into the sealing member insertion groove 336.
  • the compression unit 30 sucks and compresses a refrigerant, and discharges the high-pressure refrigerant to the intermediate space 10a of the casing 10.
  • the high-pressure refrigerant is introduced into the sealing member insertion groove 336 via a space between the frame 31 and the orbiting scroll 33, together with oil. And the high-pressure refrigerant pressurizes a lower surface of the first sealing portion 361 of the sealing member 36, and an inner circumferential surface of the second sealing portion 362.
  • the sealing member 36 As shown in FIG. 13B, as the sealing member 36 is upward moved by a pressure applied to a lower surface of the first sealing portion 361, an upper surface of the first sealing portion 361 and a lower surface of the frame 310 are adhered to each other. As a result, the sealing member 36 performs a sealing function in an axial direction. As the orbiting scroll 33 performs an orbiting movement, the first sealing portion 361 performs an orbiting movement as its upper surface slidably-contacts a lower surface of the frame 31 (a thrust bearing surface). This may cause the first sealing portion 361 to have a lowered reliability due to abrasion occurring between the first sealing portion 361 and the frame 31 when the scroll compressor is operated for a long time. However, since the axial thickness (t1) of the first sealing portion 361 is larger than the radial thickness (T2) of the second sealing portion 362 at least, the sealing member 36 may have a long lifespan.
  • the second sealing portion 362 is outward bent by a pressure applied to an inner circumferential surface of the second sealing portion 362, thereby being adhered to the outer side wall surface 336b of the sealing member insertion groove 336.
  • the sealing member 36 performs a sealing function in a radial direction.
  • the second sealing portion 362 is formed as a ring-shaped single body having no cut-out portion, and is upward moved by a pressure of the sealing member insertion groove 336. Accordingly, if the radial thickness (t2) of the second sealing portion 362 is too large, the second sealing portion 362 may not be bent when the compressor is driven, resulting in leakage in a radial direction.
  • the second sealing portion 362 may be rapidly bent when the compressor is driven, thereby performing a sealing function in a radial direction of the sealing member insertion groove 336. This may enhance performance of the compressor.
  • the sealing member is formed such that an outer diameter of the first sealing portion is the same as an outer diameter of the second sealing portion.
  • the outer diameter of the first sealing portion is formed to be different from the outer diameter of the second sealing portion.
  • the outer diameter (D31) of the first sealing portion 361 may be formed to be larger than the outer diameter (D32) of the second sealing portion 362.
  • a stair-stepped surface 36c is formed at a contact region between an outer circumferential surface 361b of the first sealing portion 361 and an outer circumferential surface 362b of the second sealing portion 362.
  • an outer circumferential surface 361c of the first sealing portion 361 forms a frictional surface with respect to the outer side wall surface 336b of the sealing member insertion groove 336.
  • an axial length (L21) of the sealing member 36 which forms a radial frictional surface of the sealing member 36 may be reduced to the axial thickness (t1) of the first sealing portion 361. This may reduce an operation delay of the sealing member 36 to some degree even if the second gap (G2) is more reduced than in the aforementioned embodiment.
  • the outer diameter (D31) of the first sealing portion 361 may be formed to be much smaller than the outer diameter (D32) of the second sealing portion 362. This is opposite to the case according to the aforementioned embodiment shown in FIG. 14.
  • the stair-stepped surface 36c is formed at a contact region between the outer circumferential surface 361b of the first sealing portion 361 and the outer circumferential surface 362b of the second sealing portion 362.
  • a substantial frictional surface is mainly formed on the outer circumferential surface 362b of the second sealing portion 362.
  • an axial length (L22) of the sealing member 36 which forms a radial frictional surface of the sealing member 36 may be reduced to a length except for most of the axial thickness (t1) of the first sealing portion 361. This may reduce an operation delay of the sealing member 36 to some degree even if the second gap (G2) is more reduced than in the aforementioned embodiment.
  • each of the first sealing portion and the second sealing portion is formed to have the same sectional surface.
  • the second sealing portion is formed to have a different sectional surface in an axial direction.
  • an inclined surface 362c may be formed on an inner circumferential surface of the second sealing portion 362 such that a sectional surface may be reduced towards a lower end from an upper end of the second sealing portion 362.
  • a pressing portion 362d may be formed at a contact region between an inner circumferential surface of the second sealing portion 362 and a lower surface of the first sealing portion 361.
  • thicknesses (t21)(t22) of a lower end of the second sealing portion 362 in a radial direction are preferably formed to be smaller than the axial thickness (t1) of the first sealing portion 361.
  • the sealing member according to these embodiments has a basic configuration and an operation effect which are similar to those of the aforementioned embodiment, and thus detailed explanations thereof will be omitted.
  • the thickness (t21) of the lower end of the second sealing portion 362 in a radial direction is formed to be smaller than that shown in FIG. 10, and the second sealing portion 362 may obtain an area where a pressure can be applied in an axial direction, at a lower end thereof. This may allow not only a radial sealing force but also an axial sealing force, to be obtained.
  • the thickness (t22) of the lower end of the second sealing portion 362 in a radial direction is formed to be significantly small to enhance a radial sealing effect. As a result, an area where a pressure can be applied in an axial direction by the pressing portion 362d may be obtained, and thus an axial sealing force may be obtained.
  • the sealing member is upward moved by a pressure of a fluid introduced into the sealing member insertion groove.
  • an elastic member 365 is installed at the sealing member insertion groove 336 such that the sealing member 36 is upward moved by an elastic force of the elastic member 365.
  • the sealing member 36 may be rapidly upward-moved even when the compressor is driven, thereby enhancing an axial sealing force.
  • a region between a lower surface of the first sealing portion and an inner circumferential surface of the second sealing portion may be formed to have a curved surface. This may prevent damage of a region between the first and second sealing portions.

Landscapes

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

Abstract

La présente invention porte sur un compresseur à spirale comprenant: un cadre configuré pour supporter une seconde volute en étant couplé à une première volute; une rainure d'insertion d'élément d'étanchéité formée en forme d'anneau, sur au moins l'une d'une surface latérale de la seconde volute et d'une surface latérale du cadre en contact avec la seconde volute; et un élément d'étanchéité formé en forme d'anneau, inséré dans la rainure d'insertion d'élément d'étanchéité, et conçu pour diviser un intervalle entre la seconde volute et le cadre dans une direction radiale, l'élément d'étanchéité étant formé de telle sorte qu'une surface de section d'une surface circonférentielle interne de celui-ci est inférieure à celle d'une surface circonférentielle externe de celui-ci, et de telle sorte qu'un second espace entre la surface circonférentielle externe de l'élément d'étanchéité et une surface de paroi latérale externe de la rainure d'insertion d'élément d'étanchéité est inférieur ou égal à un premier espace entre la surface circonférentielle interne de l'élément d'étanchéité et une surface de paroi latérale interne de la rainure d'insertion d'élément d'étanchéité.
PCT/KR2018/003817 2017-04-10 2018-03-30 Compresseur à spirale WO2018190544A1 (fr)

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KR10-2017-0046201 2017-04-10
KR1020170046201A KR102303544B1 (ko) 2017-04-10 2017-04-10 스크롤 압축기

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Publication number Priority date Publication date Assignee Title
CN111237188A (zh) * 2018-11-29 2020-06-05 艾默生环境优化技术(苏州)有限公司 涡旋压缩机及用于涡旋压缩机的静涡旋部件的定位方法
CN114072993A (zh) * 2019-10-15 2022-02-18 翰昂汽车零部件有限公司 用于压缩气态流体的设备以及用于操作这种设备的方法

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KR102181922B1 (ko) * 2019-07-01 2020-11-24 엘지전자 주식회사 압축기

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JPH11182462A (ja) * 1997-12-19 1999-07-06 Mitsubishi Electric Corp スクロール圧縮機
KR20050082632A (ko) * 2004-02-19 2005-08-24 엘지전자 주식회사 고압식 스크롤 압축기의 배압 실링 장치
JP2009097356A (ja) * 2007-10-12 2009-05-07 Mayekawa Mfg Co Ltd 密閉形スクロール圧縮機
KR20160022146A (ko) * 2014-08-19 2016-02-29 엘지전자 주식회사 스크롤 압축기
KR20160074301A (ko) * 2014-12-18 2016-06-28 엘지전자 주식회사 스크롤 압축기

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KR100869930B1 (ko) 2007-04-03 2008-11-24 엘지전자 주식회사 스크롤 압축기

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JPH11182462A (ja) * 1997-12-19 1999-07-06 Mitsubishi Electric Corp スクロール圧縮機
KR20050082632A (ko) * 2004-02-19 2005-08-24 엘지전자 주식회사 고압식 스크롤 압축기의 배압 실링 장치
JP2009097356A (ja) * 2007-10-12 2009-05-07 Mayekawa Mfg Co Ltd 密閉形スクロール圧縮機
KR20160022146A (ko) * 2014-08-19 2016-02-29 엘지전자 주식회사 스크롤 압축기
KR20160074301A (ko) * 2014-12-18 2016-06-28 엘지전자 주식회사 스크롤 압축기

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN111237188A (zh) * 2018-11-29 2020-06-05 艾默生环境优化技术(苏州)有限公司 涡旋压缩机及用于涡旋压缩机的静涡旋部件的定位方法
CN111237188B (zh) * 2018-11-29 2024-04-26 谷轮环境科技（苏州）有限公司 涡旋压缩机及用于涡旋压缩机的静涡旋部件的定位方法
CN114072993A (zh) * 2019-10-15 2022-02-18 翰昂汽车零部件有限公司 用于压缩气态流体的设备以及用于操作这种设备的方法

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KR20180114437A (ko) 2018-10-18

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