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WO2025220758A1 - Compresseur à spirale - Google Patents

Compresseur à spirale

Info

Publication number
WO2025220758A1
WO2025220758A1 PCT/KR2024/005023 KR2024005023W WO2025220758A1 WO 2025220758 A1 WO2025220758 A1 WO 2025220758A1 KR 2024005023 W KR2024005023 W KR 2024005023W WO 2025220758 A1 WO2025220758 A1 WO 2025220758A1
Authority
WO
WIPO (PCT)
Prior art keywords
oil
passage
discharge
pump
scroll compressor
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
PCT/KR2024/005023
Other languages
English (en)
Korean (ko)
Inventor
문제현
한미쁨
이재하
최중선
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
LG Electronics Inc
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
Priority to PCT/KR2024/005023 priority Critical patent/WO2025220758A1/fr
Publication of WO2025220758A1 publication Critical patent/WO2025220758A1/fr
Pending legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C11/00—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations
    • 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
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • 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
    • 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

Definitions

  • the present invention relates to a scroll compressor.
  • Compressors used in refrigeration cycles such as refrigerators and air conditioners compress refrigerant gas and transmit it to the condenser.
  • Air conditioners primarily use rotary or scroll compressors.
  • Scroll compressors are increasingly being used not only in air conditioners but also in compressors for water heaters, which require even higher pressure ratios.
  • a scroll compressor can be classified into a hermetic scroll compressor if the drive unit (or electric unit) and the compression unit are contained in a single casing, and an open scroll compressor if they are provided independently.
  • This embodiment uses a hermetic compressor as an example, but the same principle can be applied to an open type.
  • scroll compressors can be classified as upper compression scroll compressors when the compression part is located above the driving part, and lower compression scroll compressors when it is located below the driving part.
  • This embodiment uses an upper compression scroll compressor as an example, but the same can be applied to a lower compression scroll compressor.
  • scroll compressors can be classified into orbital back-pressure type and fixed back-pressure type depending on the back-pressure method.
  • the orbital back-pressure type is a method in which a back-pressure space is formed on the back surface of the orbiting scroll
  • the fixed back-pressure type is a method in which a back-pressure space is formed on the back surface of the fixed scroll.
  • This embodiment describes a scroll compressor of the orbital back-pressure type as an example, but the same can be applied to a scroll compressor of the fixed back-pressure type.
  • scroll compressors can be classified as low-pressure scroll compressors if the space housing the driving unit is suction pressure, and as high-pressure scroll compressors if the space housing the driving unit is discharge pressure.
  • the present embodiment can be applied to high-pressure scroll compressors. However, if an oil pump is applied, the same can be applied to low-pressure scroll compressors.
  • the oil recovered from the oil separator moves to the oil reservoir of the casing, and the oil in the oil reservoir is supplied to the back pressure space through the oil passage of the rotating shaft due to the differential pressure between the oil reservoir and the back pressure space.
  • this is practically limited to lubrication using differential pressure even though an oil pump is used, so the lubrication effect is halved, so not only is the back pressure of the back pressure space insufficient under low pressure ratio operating conditions, but also the back pressure of the back pressure space may not be quickly secured in the early stage of operation when the differential pressure has not been formed. This may cause leakage between compression chambers, which may lower compression efficiency and limit the operating range.
  • the oil supply pipe connected to the oil passage of the rotating shaft can be arranged to be connected to the variable volume on the suction side of the oil pump, but this may cause oil leakage due to the pressure difference between the oil return pipe and the variable volume on the suction side of the oil pump to which it is connected.
  • the oil returned to the oil storage space flows back toward the oil return pipe, increasing the pressure in the oil separator, which in turn increases the pressure in the discharge space of the casing, increasing the discharge resistance and causing input loss, which may lower the compressor performance.
  • the purpose of the present invention is to provide a scroll compressor that can quickly and smoothly secure an appropriate pressure in a back pressure space while simultaneously quickly and smoothly supplying oil to a bearing surface.
  • Another object of the present invention is to provide a scroll compressor capable of supplying oil to a back pressure space and/or a bearing surface by using differential pressure and pumping force.
  • Another object of the present invention is to provide a scroll compressor that improves compressor performance by supplying oil to a back pressure space and/or a bearing surface using differential pressure and pumping force while suppressing an increase in discharge resistance for refrigerant in a compression chamber.
  • Another object of the present invention is to provide a scroll compressor capable of supplying oil to a back pressure space and/or a bearing surface using differential pressure and pumping force while preventing oil in a low pressure space from flowing back into an oil separator and a discharge space of a casing.
  • the present invention comprises a casing, a compression unit, a rotating shaft, an oil separator, an oil pump, a frame, a pump cover, and a lubricating unit, wherein the casing may be provided with a discharge space and an oil storage space.
  • the compression unit may be provided on one side of the oil storage space inside the casing and may compress a refrigerant.
  • the rotating shaft may be coupled to the compression unit, and an oil passage may be formed in a hollow shape.
  • the oil separator may be provided on the outside of the casing and may be connected to the discharge space through a refrigerant discharge pipe.
  • the oil pump may be coupled to the rotating shaft.
  • the frame may be rotatably inserted into the rotating shaft.
  • the pump cover may be coupled to the frame with the oil pump interposed therebetween.
  • the lubricating unit may include a first lubricating unit and a second lubricating unit separated from each other, and may guide oil separated from the oil separator into the oil passage of the rotating shaft.
  • the first oil supply unit guides oil from the oil reservoir to the oil passage
  • the second oil supply unit can guide oil discharged from the oil pump to the oil passage by connecting the discharge side of the oil pump and the oil passage.
  • the second oil supply unit may be connected to the middle of the oil passage by penetrating the frame. This allows the oil pumped by the oil pump to quickly move toward the oil passage of the rotating shaft.
  • the frame may be formed with a support hole into which the rotary shaft is rotatably inserted
  • the second oil supply unit may be formed with an oil pumping passage and at least one pumping communication hole.
  • the oil pumping passage may be connected to the discharge side of the oil pump and may penetrate through the inner surface of the support hole, and the at least one pumping communication hole may penetrate between the outer surface of the rotary shaft and the inner surface of the oil passage, thereby connecting the oil pumping passage to the oil passage of the rotary shaft.
  • the second oil supply unit may be easily processed while the path length of the second oil supply unit may be formed as short as possible, so that the oil pumped by the oil pump can be quickly supplied to the oil passage of the rotary shaft.
  • the pump cover may be provided with an oil discharge chamber that is connected to the discharge side of the oil pump, and an oil discharge passage that is connected between the oil discharge chamber and the oil storage space.
  • the cross-sectional area of the oil pumping passage may be formed to be greater than or equal to the cross-sectional area of the oil discharge passage.
  • the first oil supply unit may be connected to an end of the oil passage facing the pump cover by penetrating both sides of the pump cover. This can prevent the first oil supply unit from being connected to the oil return pipe, thereby preventing oil in the storage space from flowing back into the oil return pipe.
  • an oil suction chamber communicating with the suction side of the oil pump may be formed on one side of the pump cover facing the oil pump, and an oil discharge chamber may be formed that is separated from the oil suction chamber and communicates with the discharge side of the oil pump.
  • the first oil supply unit may include an oil pressure differential passage provided in the pump cover and having one end open toward the oil storage space. Through this, oil in the oil storage space can quickly move toward the oil passage of the rotating shaft.
  • an oil differential pressure chamber is provided on one side of the pump cover, and the oil differential pressure chamber can be separated from the oil suction chamber and the oil discharge chamber inside the oil suction chamber and the oil discharge chamber.
  • the other end of the oil differential pressure passage can be connected to the oil differential pressure chamber.
  • an oil suction passage connected to the oil separator may be formed on one side of the pump cover, and an oil discharge passage connected to the oil storage space and spaced apart from the oil suction passage may be formed on the other side of the pump cover.
  • the cross-sectional area of the oil discharge passage may be formed to be smaller than the cross-sectional area of the oil suction passage.
  • an oil pumping passage may be formed in the frame so as to be connected to the discharge side of the oil pump.
  • the cross-sectional area of the oil pumping passage may be formed to be smaller than the cross-sectional area of the oil suction passage and larger than the cross-sectional area of the oil discharge passage.
  • the oil pumping passage may be formed to be located upstream of the oil discharge passage relative to the rotational direction of the rotary shaft. This allows most of the oil pumped by the oil pump to quickly move toward the oil path of the rotary shaft through the oil pumping passage before moving to the oil storage space through the oil discharge passage.
  • the pump cover may be formed with an oil discharge chamber that is connected to the discharge side of the oil pump.
  • An oil discharge passage formed in the pump cover and opened toward the oil storage space may be connected to one side of the oil discharge chamber, and an oil pumping passage formed in the frame and opened toward the oil path may be formed on the other side of the oil discharge chamber.
  • the pump cover may be formed so that a first oil discharge chamber and a second oil discharge chamber, which are connected to the discharge side of the oil pump, are separated from each other.
  • An oil discharge passage formed in the pump cover and opened toward the oil storage space may be connected to the first oil discharge chamber, and an oil pumping passage formed in the frame and opened toward the oil passage may be connected to the second oil discharge chamber.
  • the volume of the second oil discharge chamber may be formed to be greater than or equal to the volume of the first oil discharge chamber.
  • the second oil discharge chamber may be formed to be located upstream of the first oil discharge chamber with respect to the rotational direction of the rotating shaft.
  • the oil passage may be formed as a single passage so as to be connected to the first oil supply section and the second oil supply section. This can simplify processing of the oil passage.
  • a backflow prevention part may be provided between the oil storage space of the casing and the oil passage of the rotating shaft, and a differential pressure communication hole communicating between the oil storage space and the oil passage may be formed in the backflow prevention part.
  • the cross-sectional area of the differential pressure communication hole may be formed to be smaller than the cross-sectional area of the second oil supply part.
  • the oil path may include a first oil path having one end connected to the first oil supply unit and a second oil path having one end connected to the second oil supply unit. The other end of the second oil path may be connected to the first oil path. This allows separation of the first and second oil paths, thereby preventing oil from flowing backwards in the oil paths, and simplifying the processing of the oil paths.
  • the first oil passage may be formed diagonally with respect to the axial direction of the rotation shaft, and the second oil passage may be formed axially of the rotation shaft so as to be connected to the middle portion of the first oil passage.
  • the amount of oil supplied through the first oil passage may be increased, while the length of the second oil passage may be shortened as much as possible, thereby improving the processability of the second oil passage.
  • a backflow prevention part may be provided between the oil storage space of the casing and the first oil passage, and a differential pressure communication hole communicating between the oil storage space and the first oil passage may be formed in the backflow prevention part.
  • the cross-sectional area of the differential pressure communication hole may be formed to be smaller than the cross-sectional area of the second oil passage.
  • the oil path may include a first oil path having one end connected to the first refueling unit and a second oil path having one end connected to the second refueling unit.
  • the other end of the first oil path and the other end of the second oil path may be separated from each other. This allows the first and second oil paths to be separated from each other and independently supply oil to the corresponding parts, thereby further increasing the amount of oil supplied to the part connected to the first oil path.
  • first oil passage may be formed diagonally with respect to the axial direction of the rotation shaft, and the second oil passage may be formed axially of the rotation shaft so as to be separated from the first oil passage. This allows for increasing the amount of oil supplied through the first oil passage, thereby enabling rapid and smooth supply of oil to the back pressure space and/or bearing surface.
  • a backflow prevention part may be provided between the oil storage space of the casing and the first oil passage, and a differential pressure communication hole communicating between the oil storage space and the first oil passage may be formed in the backflow prevention part.
  • the cross-sectional area of the differential pressure communication hole may be formed to be smaller than the cross-sectional area of the second oil passage.
  • the scroll compressor of the present invention comprises a casing, a compression unit, a rotating shaft, an oil separator, an oil pump, a frame, a pump cover, and an oil supply unit, wherein the oil supply unit may be composed of a first oil supply unit that guides oil in an oil storage space to an oil passage, and a second oil supply unit that is separated from the first oil supply unit and communicates between the discharge side of the oil pump and the oil passage and guides oil discharged from the oil pump to the oil passage.
  • the oil recovered from the oil separator can be smoothly supplied to the back pressure space and/or the bearing surface, thereby improving the compression efficiency and expanding the operating range of the compressor.
  • the input loss of the drive motor can be suppressed, thereby improving the compressor performance.
  • the first oil supply section can be connected to the end of the oil passage facing the pump cover by penetrating both sides of the pump cover. Through this, the first oil supply section can be prevented from being connected to the oil return pipe, thereby preventing oil in the oil storage space from flowing back into the oil return pipe.
  • the cross-sectional area of the oil discharge passage connected to the oil storage space can be formed to be smaller than the cross-sectional area of the oil suction passage connected to the oil separator.
  • the scroll compressor of the present invention may be provided with an oil discharge passage opening toward a storage space on one side of an oil discharge chamber, and an oil pumping passage opening toward an oil flow path on the other side of the oil discharge chamber. This simplifies the processing of the oil discharge chamber, while allowing most of the oil pumped by the oil pump to quickly move toward the oil flow path of the rotating shaft through the oil pumping passage.
  • a first oil discharge chamber and a second oil discharge chamber are formed in a pump cover so as to be separated from each other, and an oil discharge passage opening toward a storage space is connected to the first oil discharge chamber, and an oil pumping passage opening toward an oil flow path is connected to the second oil discharge chamber.
  • the scroll compressor of the present invention can be formed with a single oil passage so that the oil passage is connected to the first oil supply section and the second oil supply section. This simplifies processing of the oil passage.
  • the scroll compressor of the present invention comprises a plurality of oil channels within a rotating shaft, wherein the plurality of oil channels may be formed such that one end is separated from the other end and the other end is connected to the other end. This can simplify processing of the oil channels while suppressing the backflow of oil from the oil channels.
  • the scroll compressor of the present invention comprises a plurality of oil passages within a rotating shaft, wherein the plurality of oil passages may be formed so that their ends are separated from each other. This allows the first and second oil passages to be separated from each other, independently supplying oil to the corresponding portions, thereby further increasing the amount of oil supplied to the portion connected to the first oil passage.
  • Fig. 1 is a cross-sectional view showing a scroll compressor according to the present embodiment.
  • Fig. 2 is a perspective view showing an exploded view of an oil supply unit that supplies oil to an oil passage of a rotating shaft in a scroll compressor according to the present embodiment.
  • Fig. 3 is a perspective view showing the subframe and pump cover in Fig. 2 in an exploded view.
  • Figure 4 is a plan view of the pump cover in Figure 3.
  • Fig. 5 is a plan view showing the relationship between the oil recovery unit and the oil pump in the pump cover of Fig. 2.
  • Fig. 6 is a cross-sectional view showing the process of supplying oil toward the oil passage of the rotating shaft in 5.
  • Figure 7 is a cross-sectional view taken along line “VII-VII” of Figure 6.
  • Fig. 8 is a perspective view showing another embodiment of an oil recovery unit.
  • Figure 9 is a plan view of Figure 8.
  • Fig. 10 is a plan view showing the relationship between the oil recovery unit and the oil pump in the pump cover of Fig. 8.
  • Fig. 11 is a cross-sectional view showing another embodiment of an oil path.
  • Fig. 12 is a cross-sectional view showing another embodiment of an oil path.
  • the term "upper side” used in the following description means a direction away from a support surface supporting a scroll compressor according to an embodiment of the present invention, i.e., the upper side toward the compression section when viewed from the center of the drive motor and the compression section.
  • the term “lower side” means a direction approaching the support surface, i.e., the lower side toward the drive motor when viewed from the center of the drive motor and the compression section.
  • axial refers to the longitudinal direction of the axis of rotation.
  • Axial can be understood as the vertical direction.
  • Diadial refers to the direction intersecting the axis of rotation.
  • the scroll compressor according to the present embodiment may be provided with a drive motor (120) that generates rotational force in the internal space (110a) of the casing (110), and a compression unit that operates by the rotational force generated by the drive motor (120) and compresses the refrigerant may be provided on one side of the drive motor (120). Accordingly, the scroll compressor according to the present embodiment forms a type of sealed scroll compressor by providing the drive motor (120) and the compression unit together in the internal space (110a) of the casing (110).
  • the internal space (110a) of the casing (110) can form a discharge space (110b) on the upper side of the compression section, an oil separation space (110c) between the compression section and the drive motor (120), and an oil storage space (110d) on the lower side of the drive motor (more precisely, a subframe) (120).
  • the refrigerant suction pipe (115) can be coupled so as to pass through the discharge space (110b) and be directly connected to the compression section, and the refrigerant discharge pipe (116) can be coupled so as to pass through the casing (110) and be connected to the oil separation space (110c).
  • the scroll compressor according to the present embodiment can form a type of high-pressure scroll compressor by filling the internal space (110a) of the casing (110), or more precisely, the oil separation space (110c) in which the driving motor (120) is provided, with the refrigerant at the discharge pressure discharged from the compression unit.
  • An oil separator (117) may be provided on the outside of the casing (110) to separate oil from the refrigerant discharged from the internal space (110a) of the casing (110).
  • One end of the oil separator (117) may be connected to the internal space of the casing (110), more precisely, the discharge space (110b), via a refrigerant discharge pipe (116), and the other end of the oil separator (117) may be connected to the oil storage space (110d) of the casing (110), more precisely, to an oil pump (126) to be described later, via an oil return pipe (118).
  • oil discharged together with the refrigerant from the internal space (110a) of the casing (110) may be separated in the oil separator (117) and recovered to the internal space (oil storage space) (110a) of the casing (110) via the oil pump (126).
  • a driving motor (120) may include a stator (121) and a rotor (122).
  • the stator (121) may be fixed to the inner surface of the casing (110) by hot pressing, and the rotor (122) may be rotatably provided inside the stator (121).
  • a rotational shaft (125) may be press-fitted and coupled to the center of the rotor (122).
  • the upper part (more precisely, the eccentric part) of the rotation shaft (125) is rotatably inserted into the main frame (130) to be described later and supported radially, and the lower part of the rotation shaft (125) is rotatably inserted into the subframe (140) to be described later and supported radially and axially. Accordingly, the rotation shaft (125) is supported at both ends by the main frame (130) and the subframe (140) with the drive motor (120) in between, and rotates stably.
  • an eccentric portion (1251) is provided at the top of the rotary shaft (125), and a rotary shaft insertion portion (163) of a later-described orbiting scroll (160) can be rotatably inserted and coupled thereto.
  • the eccentric portion (1251) can be inserted into and coupled to the rotary shaft insertion portion (163), or the rotary shaft insertion portion (163) can be inserted into and coupled to the eccentric portion (1251).
  • This embodiment illustrates an example in which the rotary shaft insertion portion (163) is inserted into and coupled to the eccentric portion (1251) of the rotary shaft (125).
  • an extension pin portion (1252) extending axially toward an oil pump (126) to be described later may be formed at the lower end of the rotation shaft (125).
  • the lower end of the rotation shaft (125) may be rotatably inserted into a sub-support hole (143) of a sub-frame (140) to be described later
  • the extension pin portion (1252) may be extended from the lower end of the rotation shaft (125) and rotatably inserted into a pin receiving portion (1432) of a sub-frame (140) to be described later.
  • the extension pin portion (1252) may be composed of a first pin portion (1252a) and a second pin portion (1252b).
  • the first pin portion (1252a) is a portion that is rotatably inserted into a pin receiving portion (1432) of a subframe (140) to be described later
  • the second pin portion (1252b) is a portion that is coupled to an inner gear (1261) of an oil pump (126) to be described later.
  • the outer circumference of the first pin portion (1252a) may be formed in a circular cross-section shape
  • the outer circumference of the second pin portion (1252b) may be formed in a cut shape to correspond to the inner circumference of the oil pump (126). Accordingly, the rotational force of the rotational shaft (125) may be smoothly transmitted to the oil pump (126) through the extension pin portion (1252).
  • the oil pump (126) may be provided between a subframe (140) supporting a rotating shaft (125) and a pump cover (145) coupled to one side of the subframe (140).
  • a pump receiving groove (144) may be formed on one side of the subframe (140), and the pump cover (145) may be coupled to the subframe (140) by axially supporting the oil pump (126) accommodated in the pump receiving groove (144). Accordingly, the oil pump (126) may be stably supported between the subframe (140) and the pump cover (145).
  • the oil pump (126) may be a volumetric pump that pumps oil while having a variable volume.
  • the oil pump (126) may be a trochoidal gear pump in which an inner gear (1261) and an outer gear (1262) are meshed with each other to form a variable volume on the suction side (hereinafter, may be abbreviated as the suction side) (126a) and a variable volume on the discharge side (hereinafter, may be abbreviated as the discharge side) (126b).
  • the inner gear (1261) may be eccentrically coupled to the rotation shaft (125), and the outer gear (1262) may be fixedly coupled to the pump receiving groove (144) of the subframe. Accordingly, the inner gear (1261) can continuously form a suction-side variable volume (126a) and a discharge-side variable volume (126b) while eccentrically rotating with respect to the outer gear (1262).
  • the suction-side variable volume (126a) of the oil pump (126) is connected to the oil separator (117) through the oil recovery pipe (118), and the discharge-side variable volume (126b) of the oil pump (126) can be connected to the oil path (1255) of the rotating shaft (125) through the differential pressure oil supply unit (hereinafter, may be abbreviated as the first oil supply unit) (180) to be described later and the pumping oil supply unit (hereinafter, may be abbreviated as the second oil supply unit) (190) to be described later.
  • the differential pressure oil supply unit hereinafter, may be abbreviated as the first oil supply unit) (180) to be described later
  • the pumping oil supply unit hereinafter, may be abbreviated as the second oil supply unit) (190) to be described later.
  • the oil separated from the oil separator (117) and recovered into the internal space (110a) of the casing (110) can be supplied to the oil path (1255) of the rotating shaft (125) by the differential pressure oil supply unit (180) and the pumping oil supply unit (190) described later.
  • the oil pump (126) will be described again later together with the first oil supply unit and the second oil supply unit.
  • an oil passage (1255) may be formed between the ends of the rotating shaft (125) inside the rotating shaft (125), and a pumping communication hole (192), which will be described later, may be formed by penetrating the outer circumference in the middle of the oil passage (1255). Accordingly, some of the oil in the oil storage space (110d) may be introduced into the oil passage (1255) through the differential pressure oil supply unit (180), which will be described later, and some of the oil pumped by the oil pump (126) may be introduced into the oil passage (1255) through the pumping oil supply unit (190), which will be described later, and may be supplied to the back pressure space (S) and/or the bearing surface (B).
  • the main frame (130) is provided on the upper side of the driving motor (120) and may be fixed by hot pressing or welding to the inner surface of the casing (110).
  • the main frame (130) may include a main flange portion (131), a main support protrusion portion (132), and a back pressure space portion (133).
  • the upper surface of the main flange portion (131) may be formed with a scroll support surface (134) that forms a thrust bearing surface (hereinafter, a first thrust bearing surface). Accordingly, the lower surface (or back surface) of the pivot plate portion (161) described later may be slidably placed on the scroll support surface (134) and supported in the axial direction.
  • the main support protrusion (132) extends from the center of the main flange portion (131) toward the driving motor (120), and a main support hole (1321) may be formed on the inside of the main support protrusion (132). Accordingly, the upper end of the rotation shaft may be rotatably inserted into the main support hole of the main frame and supported in the radial direction.
  • the back pressure space (133) is a portion that forms a back pressure space (S2) together with the fixed thrust surface (152a) to be described later, and may be formed in an annular shape by being sunken to a preset depth from the edge of the scroll support surface (134).
  • the back pressure space (133) may be connected to the intermediate pressure chamber of the compression chamber (V) through a back pressure passage (not shown) to form a back pressure that forms an intermediate pressure between the suction pressure and the discharge pressure. Accordingly, the orbiting scroll (160) is pushed upward toward the fixed scroll (150) by the pressure (back pressure) of the back pressure space (S) and comes into close contact with the fixed scroll (150) to suppress leakage between the compression chambers (V1) (V2).
  • the subframe (140) may be fixed by hot pressing or welding to the inner surface of the casing (110) on the lower side of the driving motor (120).
  • the subframe (140) may include a sub-fixing protrusion (141) and a sub-supporting protrusion (142).
  • the sub-fixing protrusion (141) can be extended radially from the outer surface of the sub-supporting protrusion (142) and hot-pressed or welded to the inner surface of the casing (110). Accordingly, the sub-frame (140) can be firmly fixed to the casing (110).
  • the sub-support protrusion (142) may be formed in a cylindrical shape with the center thereof penetrating in the axial direction.
  • the sub-support protrusion (142) may have a sub-support hole (143) formed in the center thereof into which the lower end of the rotation shaft (125) is rotatably inserted.
  • a shaft receiving portion (1431) forming a sub-bearing surface together with the rotation shaft (125) may be formed in the upper half of the sub-support hole (143) and a pin receiving portion (1432) into which the extension pin portion (1252) of the rotation shaft (125) is rotatably inserted may be formed in the lower half of the sub-support hole (143) so as to be in communication with each other.
  • the inner diameter of the pin receiving portion (1432) may be formed to be smaller than the inner diameter of the shaft receiving portion (1431). Accordingly, a gap is formed between the shaft receiving portion (1431) and the pin receiving portion (1432), so that a thrust bearing surface (not shown) that supports the rotation axis in the axial direction can be formed.
  • a sub-bearing (not shown) made of a bushing bearing is inserted and fixed into the inner surface of the shaft receiving portion (1431), and an oil pumping passage (191) that communicates between the discharge-side variable volume (or oil discharge chamber) of the oil pump and the pumping communication hole (192) of the rotary shaft (125) can be formed on the inner surface of the pin receiving portion (1432). Accordingly, the oil pumping passage (191) can form a pumping oil supply portion (190) together with the pumping communication hole (192) of the rotary shaft (125).
  • the oil pumping passage (191) may be formed in the shape of a bent hole that penetrates between the inner circumference of the pin receiving portion (1432) on the lower surface of the subframe (140), that is, on the lower surface of the sub-support protrusion (142) facing the discharge-side variable volume (126b) of the oil pump (126). Accordingly, the oil pumping passage (191) can be easily processed while optimizing and/or minimizing the path length, so that the oil pumped by the oil pump (126) can quickly move toward the oil path (1255) of the rotating shaft (125).
  • the oil pumping passage (191) may also be formed to be inclined. In this case, the path length of the oil pumping passage (191) can be further shortened. The oil pumping passage (191) will be described later together with the pumping oil supply portion (190).
  • a fixed pump receiving groove (144) for receiving an oil pump (126) may be formed on the lower surface of the sub-support protrusion (142), that is, on the lower surface of the pin receiving portion (1432).
  • the inner diameter of the pump receiving groove (144) may be formed to be the same as the outer diameter of the outer gear (1262) forming part of the oil pump (126). Accordingly, the outer gear (1262) of the oil pump (126) may be firmly coupled to the pump receiving groove (144).
  • a pump cover (145) that covers the pump receiving groove (144) is coupled to the lower surface of the subframe (140), that is, the lower surface of the sub-support protrusion (142), and an oil pump (126) can be accommodated between the subframe (140) and the pump cover (145). Accordingly, the pump cover (145) can form a type of pump housing together with the subframe (140).
  • the oil recovery pipe (118) described above may be connected to one side of the pump cover (145), and the oil storage space (110d) described above may be connected to the other side of the pump cover (145).
  • the pump cover (145) may be provided with an oil recovery unit (170) that connects the oil separator (117) and the oil storage space (110d) to recover oil separated from the oil separator (117) to the oil storage space (110d).
  • the oil recovery unit (170) will be described later together with the differential pressure oil supply unit (180) and the pumping oil supply unit (190).
  • the fixed scroll (150) may include a fixed plate portion (151), a fixed side wall portion (152), and a fixed wrap (153).
  • the fixed plate portion (151) is formed in a disc shape and can be in close contact with the inner surface of the casing (110) forming the discharge space (110b) or can be spaced apart from the inner surface of the casing (110).
  • An inlet (1511) is formed at the edge of the fixed plate (151) in the axial direction and communicates with a suction pressure chamber (not shown), and a refrigerant suction pipe (115) penetrating the discharge space (110b) of the casing (110) can be inserted and connected to the inlet (1511). Accordingly, the refrigerant suction pipe (115) can pass through the discharge space (110b) of the casing (110) and be directly connected to the inlet (1511) of the fixed scroll (150).
  • a discharge port (1512) and a bypass hole (not shown) are formed in the center of the fixed plate portion (151), and a discharge valve (155) for opening and closing the discharge port (1512) and a bypass valve (not shown) for opening and closing the bypass hole may be installed on the back surface of the fixed plate portion (151). Accordingly, the refrigerant compressed in the first compression chamber (V1) and the second compression chamber (V2) can be discharged from the upper side of the fixed scroll (150) to the discharge space (110b) formed in the casing (110).
  • the compression chamber formed between the outer surface of the rotating wrap (162) and the inner surface of the fixed wrap (153) facing it is defined as the first compression chamber (V1)
  • the compression chamber formed between the inner surface of the rotating wrap (162) and the outer surface of the fixed wrap (153) facing it is defined as the second compression chamber (V2).
  • the fixed side-wall portion (152) can extend in an annular shape from the edge of the fixed plate portion (151) toward the main frame (130). Accordingly, the fixed side-wall portion (152) can be bolted so that its lower surface is in close contact with the upper surface of the main frame (130), i.e., the upper surface of the main flange portion (131).
  • the fixed wrap (153) can extend from the lower surface of the fixed plate portion (151) toward the orbiting scroll (160).
  • the fixed wrap (153) can be formed in various shapes, such as an involute.
  • the fixed wrap (153) can be formed in a logarithmic spiral or in a plurality of circular arc curves.
  • the fixed wrap (153) may be formed with the same wrap height along the wrap formation direction, or may be formed with different heights. In this embodiment, an example in which the wrap heights of the fixed wrap (153) are the same is shown.
  • the rotary scroll (160) may include a rotary plate portion (161), a rotary wrap (162), and a rotary shaft insert portion (163).
  • the pivot plate (161) is formed in a circular shape and can be axially supported by the main frame (130) to perform pivotal movement between the main frame (130) and the fixed scroll (150).
  • the orbiting wrap (162) can extend from the upper surface (compression surface) of the orbiting plate (161) toward the fixed scroll (150). Accordingly, the orbiting wrap (162) can be interlocked with the fixed wrap (153) to form two pairs of compression chambers (V1) (V2).
  • the orbital wrap (162) can be formed in various shapes, such as an involute, to correspond to the fixed wrap (153).
  • the orbital wrap (162) can be formed in a logarithmic spiral or in a plurality of circular arc curves.
  • the turning wrap (162) may be formed with the same wrap height along the wrap formation direction, or may be formed with different heights. In this embodiment, an example is shown in which the wrap height of the turning wrap (162) is the same along the wrap formation direction.
  • the rotary shaft insertion portion (163) extends from the geometric center of the orbiting scroll (160) toward the eccentric portion (1251) of the rotary shaft (125).
  • the rotary shaft insertion portion (163) can be rotatably inserted into the eccentric portion (1251) of the rotary shaft (125). Accordingly, the orbiting scroll (160) is rotated by the eccentric portion (1251) of the rotary shaft (125) and the rotary shaft insertion portion (163).
  • the scroll compressor according to the present embodiment is provided with an oil separator (117) on the outside of the casing (110) as described above, and the oil separator (117) is connected to the internal space (110a) of the casing (110) through an oil return pipe (118).
  • An oil return unit (170) connected to the oil return pipe (118) in the internal space (110a) of the casing (110) is provided at the lower end of the rotating shaft (125), and a differential pressure oil supply unit (first oil supply unit) (180) and a pumping oil supply unit (second oil supply unit) (190) can be connected to each other separately.
  • the differential pressure oil supply unit (180) is a supply unit that guides oil from the oil storage space (110d) to the oil passage (1255) by utilizing the pressure difference between the oil storage space (110d) and the oil passage (1255), and the pumping oil supply unit (190) is a supply unit that guides oil from the oil recovery unit (170) to the oil passage (1255) by utilizing the pumping power of the oil pump (126) accommodated in the oil recovery unit (170). Accordingly, the oil recovered from the oil separator (117) is smoothly supplied to the back pressure space (S) and/or the bearing surface (B), thereby suppressing compression loss and/or friction loss and improving compression efficiency. This can expand the operating range of the compressor by suppressing the compression loss and/or friction loss described above under both high pressure ratio and low pressure ratio operating conditions, thereby improving compression efficiency.
  • the differential pressure oil supply unit (180) is formed to be connected to the discharge-side variable volume (126b) of the oil pump (126), the oil in the oil storage space (110d) can be prevented from flowing back toward the oil separator (117). Accordingly, the internal pressure of the oil separator (117) and the casing (110) is prevented from increasing, thereby suppressing the input loss of the drive motor (120), and thereby improving the compressor performance.
  • the oil recovery unit (170) may include an oil suction passage (171), an oil suction chamber (172), an oil discharge chamber (173), and an oil discharge passage (174).
  • the oil suction passage (171) and the oil suction chamber (172) may be connected to each other
  • the oil discharge chamber (173) and the oil discharge passage (174) may be connected to each other
  • the oil suction chamber (172) and the oil discharge chamber (173) may be separated from each other.
  • the oil suction passage (171) and the oil suction chamber (172) form a first oil recovery unit (170
  • the oil discharge chamber (173) and the oil discharge passage (174) form a second oil recovery unit (170) separated from the first oil recovery unit (170).
  • the oil suction chamber (172) and the oil discharge chamber (173) are connected to each other by the oil pump (126), so that the first oil recovery unit (170) and the second oil recovery unit (170) eventually form one oil recovery passage.
  • the oil suction passage (171) is a portion where the oil return pipe (118) is connected, and can be formed in the shape of a hole sunken in the radial direction to a preset depth on the outer surface of the pump cover (145). Accordingly, the oil return pipe (118) can be easily connected to the oil suction passage (171).
  • the cross-sectional area (e.g., inner diameter) (A11) of the oil suction passage (171) may be formed to be larger than the cross-sectional area (e.g., inner diameter) (A21) of the oil discharge passage (174) to be described later. Accordingly, a portion of the oil recovered through the oil return pipe (118) may not be recovered to the oil storage space (110d) through the oil discharge passage (174) but may be smoothly supplied to the oil passage (1255) of the rotating shaft (125) through the oil pumping passage (191) to be described later.
  • the oil suction passage (171) may be formed to be sunken in the surface facing the subframe (140). In this case, not only can the oil suction passage (171) be easily processed, but also the oil resistance between it and the oil suction chamber (172) is reduced, so that the oil in the oil suction passage (171) can smoothly move to the oil suction chamber (172).
  • the oil suction chamber (172) is a portion connected to the oil suction passage (171), and may be formed in a groove shape that is sunken in the axial direction to a preset depth on one side of the pump cover (145) facing the oil pump (126). Accordingly, the oil suction chamber (172) is opened toward the oil pump (126), so that oil flowing into the oil suction chamber (172) can quickly move to the oil pump (126).
  • the oil suction chamber (172) may be formed in an arc shape by extending in both circumferential directions from the oil suction passage (171). Accordingly, it may be widely communicated with the suction-side variable volume (126a) of the oil pump (126) formed of a trochoid gear pump.
  • the oil suction chamber (172) may be formed so that the cross-sectional areas (A12')(A12") of the chambers (172)(173) on both sides are different based on the oil suction passage (171).
  • the oil suction chamber (172) may be formed so that the cross-sectional area (A12') of the oil suction chamber (172) located in the forward direction with respect to the rotational direction of the rotational shaft (125) based on the oil suction passage (171) is larger than the cross-sectional area (A12") of the oil suction chamber (172) located in the reverse direction. Accordingly, while the oil in the oil suction chamber (172) moves quickly to the oil discharge chamber (173), the oil in the oil discharge chamber (173) can be prevented from flowing back to the oil suction chamber (172).
  • a suction-side sealing surface (183a) may be formed between the oil suction chamber (172) and the oil differential pressure chamber (182) to be described later. Accordingly, the oil suction chamber (172), which forms part of the oil recovery unit (170), may be separated from the differential pressure oil supply unit (180).
  • the oil discharge chamber (173) is a portion connected to the oil discharge passage (174), and may be formed in the shape of a groove that is sunken in the axial direction to a preset depth on one side of the pump cover (145) facing the oil pump (126). Accordingly, the oil discharge chamber (173) is opened toward the oil pump (126), so that the oil of the oil pump (126) can smoothly move to the oil discharge chamber (173).
  • the oil discharge chamber (173) may be formed in an arc shape by extending in both circumferential directions from the oil discharge passage (174). Accordingly, it may be widely connected with the discharge-side variable volume (126b) of the oil pump (126) formed of a trochoid gear pump.
  • the oil discharge chamber (173) may be formed to have different cross-sectional areas (A22') (A22") on both sides based on the oil discharge passage (174).
  • the oil discharge chamber (173) may be formed to have a cross-sectional area (A22") larger than the cross-sectional area (A22') of the oil discharge chamber (173) positioned in the forward direction with respect to the rotational direction of the rotation shaft (125). Accordingly, the oil in the oil suction chamber (172) can be quickly introduced into the oil discharge chamber (173), while the oil in the oil discharge chamber (173) can be prevented from flowing back into the oil suction chamber (172).
  • a discharge side sealing surface (183b) may be formed between the oil discharge chamber (173) and the oil differential pressure chamber (182) to be described later. Accordingly, the oil discharge chamber (173), which forms part of the oil recovery unit (170), may be separated from the differential pressure oil supply unit (180).
  • the oil discharge passage (174) is a portion that is connected to the oil storage space (110d), and may be formed in the shape of a hole sunken in the radial direction by a preset depth from the outer circumferential surface of the pump cover (145). Accordingly, the oil discharge passage (174) can be formed as small as possible while being connected to the lowest end of the oil discharge chamber (173), so that the oil in the oil discharge chamber (173) can be smoothly discharged into the oil storage space (110d).
  • the oil discharge passage (174) may be formed to be located downstream of the oil pumping passage (191) to be described later based on the rotational direction of the rotary shaft (125). Accordingly, the oil moving from the oil pump (126) to the oil discharge chamber (173) first moves to the oil pumping passage (191) and then moves to the oil discharge passage (174). Through this, the oil recovered through the oil pump (126) can quickly and in large quantities move to the oil path (1255) of the rotary shaft (125) through the oil pumping passage (191), thereby increasing the amount of oil supplied to the back pressure space (S) and/or the bearing surface (B).
  • the cross-sectional area (e.g., inner diameter) (A21) of the oil discharge passage (174) may be formed smaller than the cross-sectional area (e.g., inner diameter) (A11) of the oil suction passage (171) as described above and the cross-sectional area (e.g., inner diameter) (A3) of the oil pumping passage (191) to be described later. Accordingly, a portion of the oil recovered toward the internal space (110a) of the casing (110) through the oil return pipe (118) may not be recovered to the oil storage space (110d) through the oil discharge passage (174) but may be smoothly supplied toward the oil passage (1255) of the rotating shaft (125) through the oil pumping passage (191) to be described later.
  • the oil discharge passage (174) may be formed to be sunken in the surface facing the subframe (140). In this case, not only can the oil discharge passage (174) be easily processed, but also the flow resistance between it and the oil discharge chamber (173) is reduced, so that the oil in the oil discharge chamber (173) can smoothly move to the oil discharge passage (174).
  • the differential pressure oil supply unit (180) may include an oil differential pressure passage (181) and an oil differential pressure chamber (182).
  • the oil differential pressure passage (181) is a portion that is connected to the oil storage space (110d)
  • the oil differential pressure chamber (182) is a portion that is connected to the oil passage (1255) of the rotating shaft (125). Accordingly, the oil storage space (110d) and the oil passage (1255) of the rotating shaft (125) may be connected to each other through the oil differential pressure passage (181) and the oil differential pressure chamber (182).
  • the oil pressure differential passage (181) may be formed to penetrate between both sides of the pump cover (145).
  • the oil pressure differential passage (181) may be formed to penetrate the oil supply pipe section (1452) forming part of the pump cover (145).
  • the pump cover (145) is composed of a cover plate section (1451) equipped with the oil recovery section (170) described above and an oil supply pipe section (1452) extending from the cover plate section (1451) toward the oil storage space (110d), and the oil pressure differential passage (181) may be formed to penetrate between the lower end of the oil supply pipe section (1452) and the bottom surface of the cover plate section (1451).
  • the oil pressure differential passage (181) may be formed as a single body in the pump cover (145) or may be formed by post-assembly.
  • the oil pressure differential passage (181) may be formed by penetrating the oil supply pipe section (1452) that extends as a single body from the cover plate section (1451), or may be formed by penetrating the oil supply pipe section (1452) that is post-assembled to the cover plate section (1451).
  • This embodiment illustrates an example in which the oil pressure differential passage (181) is formed as a single body inside the pump cover (145) as the oil supply pipe section (1452) is formed as a single body in the cover plate section (1451).
  • the cross-sectional area (e.g., inner diameter) (A6) of the oil pressure differential passage (181) may be formed to be smaller than or equal to the cross-sectional area (e.g., inner diameter) (A4) of the oil passage (1255).
  • a backflow prevention unit (184) that partially blocks the oil pressure differential passage (181) and/or the oil passage (1255) of the rotary shaft (125) may be provided inside the oil pressure differential passage (181), and a backflow prevention unit (1841) that communicates between the pressure differential passage (1841) and the oil passage (1255) may be formed in the backflow prevention unit (184). Accordingly, it is possible to prevent oil flowing into the oil passage (1255) of the rotating shaft (125) through the pumping communication hole (192) described later from flowing back into the oil storage space (110d).
  • the backflow prevention unit (184) may be manufactured separately and inserted into the oil pressure differential passage (181) and/or the oil passage (1255), or may be formed as a single body in the oil pressure differential passage (181) and/or the oil passage (1255).
  • the backflow prevention unit (184) may be inserted into and combined with the oil passage (1255) of the rotary shaft (125) so as not to interfere with the pumping communication hole (192) described later. Accordingly, the backflow prevention unit (184) may be easily formed in the oil pressure differential passage (181) and/or the oil passage (1255) forming the differential pressure oil supply unit (180).
  • the differential pressure oil supply unit (180) may be formed so that the differential pressure chamber (182) is excluded and the differential pressure oil supply passage (181) is directly connected to the oil passage (1255) of the rotating shaft (125).
  • the structure of the pump cover (145) is simplified, so that not only can the pump cover (145) be easily processed, but also the differential pressure oil supply unit (180) and the pumping oil supply unit (190) can be more tightly sealed.
  • the pumping oil supply unit (190) may include an oil pumping passage (191) and a pumping communication hole (192).
  • the oil pumping passage (191) is a portion that is connected to the discharge-side variable volume (126b) of the oil pump (126)
  • the pumping communication hole (192) is a portion that is connected to the oil passage (1255) of the rotating shaft (125). Accordingly, a portion of the oil recovered from the oil separator (117) by the oil pump (126) can be quickly supplied to the oil passage (1255) of the rotating shaft (125) through the pumping oil supply unit (190) without being recovered to the oil storage space (110d).
  • the oil pumping passage (191) may be formed by penetrating through the inner surface of the sub-support hole (143) on one side of the sub-frame (140) facing the discharge-side variable volume (126b) of the oil pump (126).
  • one end of the oil pumping passage (191) may be formed by opening to the upper surface of the pump receiving groove (144) to face the discharge-side variable volume (126b) of the oil pump (126)
  • the other end of the oil pumping passage (191) may be formed by opening to the inner surface of the pin receiving portion (1432) forming part of the sub-support hole (143) to face the first pin portion (1252a) of the rotating shaft (125).
  • the oil pumping passage (191) may be bent and penetrated through the inner surface of the sub-support hole (143) at the lower end of the sub-frame (140).
  • the oil pumping passage (191) may be formed to be located upstream of the oil discharge passage (174) of the differential pressure oil supply unit (180) with respect to the rotational direction of the rotating shaft (125). Accordingly, the oil recovered by the oil pump (126) moves toward the oil pumping passage (191) forming the pumping oil supply unit (190) before being discharged to the oil storage space (110d) through the oil discharge passage (174) connected to the differential pressure oil supply unit (180). Through this, a large amount of oil can be supplied to the oil passage (1255) of the rotating shaft (125) through the pumping oil supply unit (190).
  • the cross-sectional area (e.g., inner diameter) (A3) of the oil pumping passage (191) may be formed to be larger than or equal to the cross-sectional area (e.g., inner diameter) (A21) of the oil discharge passage (174).
  • the cross-sectional area (e.g., inner diameter) (A3) of the oil pumping passage (191) may be formed to be larger than the cross-sectional area (e.g., inner diameter) (A21) of the oil discharge passage (174).
  • the oil pumping passage (191) may be formed to be axially recessed on the inner surface of the pin receiving portion (1432). In this case, the oil pumping passage (191) can be formed easily and widely.
  • the pumping communication hole (192) may be formed to penetrate from the outer surface of the rotating shaft (125) to the inner surface of the oil passage (1255).
  • the pumping communication hole (192) may be formed to be positioned radially on the same line from the outer surface of the extension pin portion (1252) facing the oil pumping passage (191) toward the inner surface of the oil passage (1255).
  • the cross-sectional area (e.g., inner diameter) (not shown) of the pumping communication hole (192) may be formed to be larger than or equal to the cross-sectional area (e.g., inner diameter) (A3) of the oil pumping passage (191). Accordingly, the oil pumped by the oil pump (126) can quickly move to the oil passage (1255) of the rotating shaft (125) through the oil pumping passage (191) and the pumping communication hole (192).
  • only one pumping communication hole (192) may be formed, or a plurality of pumping communication holes (192) may be formed at predetermined intervals along the circumferential direction.
  • the present embodiment illustrates an example in which a plurality of pumping communication holes (192) are formed at equal intervals along the circumferential direction. Accordingly, a large amount of oil pumped by the oil pump (126) can be introduced into the oil passage (1255) of the rotating shaft (125) through the pumping oil supply unit (190).
  • the volume of the first compression chamber (V1) and the second compression chamber (V2) gradually narrows as the orbiting scroll (160) moves from the suction port (or suction pressure chamber) (1511) toward the discharge port (or discharge pressure chamber) (1512) while performing the orbiting motion.
  • the refrigerant is introduced into the first compression chamber (V1) and the second compression chamber (V2) through the refrigerant suction pipe (115) and the suction port (1511) of the fixed scroll (150), and the refrigerant is compressed while moving toward the final compression chamber by the orbiting scroll (160).
  • the refrigerant is discharged from the final compression chamber to the discharge space (110b) of the casing (110) through the discharge port (1512) of the fixed scroll (150), and the refrigerant moves to the oil separation space (110c) or/and the oil storage space (110d) of the casing (110) through the discharge passage (not shown) provided in the fixed scroll (150) and the main frame (130).
  • the refrigerant circulates through the oil separation space (110c) of the casing (110), and oil is separated from the refrigerant.
  • the refrigerant from which the oil has been separated is discharged to the oil separator (117) provided on the outside of the casing (110) through the refrigerant discharge pipe (116), while the oil separated from the refrigerant is recovered to the oil storage space (110d) of the casing (110).
  • oil is separated from the refrigerant discharged through the oil separator (117), and the refrigerant moves to the refrigeration cycle through the refrigerant circulation pipe (not shown), while the oil moves toward the internal space (110a) of the casing (110) through the oil return pipe (118).
  • the oil moving to the internal space (110a) of the casing (110) is recovered to the oil storage space (110d) of the casing (110) through the oil suction passage (171), oil suction chamber (172), oil discharge chamber (173), and oil discharge passage (174) forming the oil recovery unit (170), and the oil recovered to the oil storage space (110d) moves to the oil passage (1255) of the rotating shaft (125) through the oil differential pressure passage (181) and the oil differential pressure chamber (182) forming the differential pressure oil supply unit (180).
  • the back pressure of the back pressure space (S) can be appropriately maintained to suppress leakage between the compression chambers (V1) and (V2) while reducing friction loss at the bearing surface (B), thereby increasing the compression effect and expanding the operating range of the compressor.
  • the differential pressure oil supply unit (180) is formed to be in communication with the discharge-side variable volume (126b) of the oil pump (126), the oil supplied to the oil path (1255) of the rotating shaft (125) through the differential pressure oil supply unit (180) can be suppressed from flowing back toward the oil recovery pipe (118) and the oil separator (117) connected to the oil recovery unit (170). Accordingly, the internal pressure of the oil separator (117) and/or the internal pressure of the casing (more precisely, the discharge space) (110) can be suppressed from increasing, thereby suppressing the discharge resistance of the compressed refrigerant in the compression chamber (V) from increasing. Through this, the input loss of the drive motor (120) can be suppressed, thereby improving the compressor performance.
  • the differential pressure oil supply unit and the pumping oil supply unit are connected to each other in one oil discharge chamber, but in some cases, the differential pressure oil supply unit and the pumping oil supply unit may be connected independently in a plurality of oil discharge chambers.
  • an oil separator (117) communicating with a refrigerant discharge pipe (116) is provided on the outside of the casing (110), and the oil separator (117) can be connected to the suction side of the oil recovery unit (170) provided in the internal space (110a) of the casing (110) through an oil recovery pipe (118).
  • the discharge side of the oil recovery unit (170), that is, the discharge side variable volume (126b) of the oil pump (126), can be separated into a differential pressure oil supply unit (180) and a pumping oil supply unit (190), and can be independently connected to the oil passage (1255) of the rotating shaft (125). Accordingly, a portion of the oil recovered through the oil recovery unit (170) is supplied to the oil passage (1255) of the rotary shaft (125) through the differential pressure oil supply unit (180) after passing through the oil storage space (110d), while another portion of the oil can be supplied directly to the oil passage (1255) of the rotary shaft (125) through the pumping oil supply unit (190) without passing through the oil storage space (110d).
  • the oil discharge chamber (173) forming part of the oil recovery unit (170) may be separated into a first oil discharge chamber (1731) and a second oil discharge chamber (1732).
  • the first oil discharge chamber (1731) may be independently communicated with the differential pressure oil supply unit (180), and the second oil discharge chamber (1732) may be independently communicated with the pumping oil supply unit (190).
  • the first oil discharge chamber (1731) may be communicated with an oil discharge passage (174) opened toward the oil storage space (110d), and the second oil discharge chamber (1732) may be communicated with an oil pumping passage (191) forming the pumping oil supply unit (190).
  • the discharge-side variable volume (126b) of the oil pump (126) is independently connected to the pumping oil supply unit (190), even if the pumping oil supply unit (190) is located axially higher than the oil pump (126), the amount of oil moving to the pumping oil supply unit (190) can be appropriately secured.
  • a relatively large amount of oil is supplied to the oil passage (1255) of the rotating shaft (125) through the pumping oil supply unit (190), thereby securing the amount of oil supplied to the back pressure space (S) and/or the bearing surface (B).
  • the volume (e.g., cross-sectional area) (A52) of the second oil discharge chamber (1732) may be formed to be greater than or equal to the volume (e.g., cross-sectional area) (A51) of the first oil discharge chamber (1731).
  • the volume (e.g., cross-sectional area) (A52) of the second oil discharge chamber (1732) may be formed to be greater than the volume (e.g., cross-sectional area) (A51) of the first oil discharge chamber (1731).
  • the second oil discharge chamber (1732) may be formed to be located upstream of the first oil discharge chamber (1731) based on the rotational direction of the rotary shaft (125). Accordingly, the oil recovered by the oil pump (126) may move a larger amount of oil toward the oil path (1255) of the rotary shaft (125) through the oil pumping passage (191) forming the pumping oil supply section (190) before moving to the oil storage space (110d) through the oil discharge passage (174) connected to the differential pressure oil supply section (180).
  • the differential pressure oil supply unit and the pumping oil supply unit are connected to each other in one oil path, but in some cases, the differential pressure oil supply unit and the pumping oil supply unit may be connected independently in multiple oil paths.
  • an oil separator (117) communicating with a refrigerant discharge pipe (116) is provided on the outside of the casing (110), and the oil separator (117) can be connected to the suction side of an oil recovery unit (170) provided in the internal space (110a) of the casing (110) through an oil recovery pipe (118).
  • the discharge side of the oil recovery unit (170) can be separated into a differential pressure oil supply unit (180) and a pumping oil supply unit (190), which can be independently connected to the oil passage (1255) of the rotating shaft (125).
  • a portion of the oil recovered through the oil recovery unit (170) passes through the oil storage space (110d) and is then supplied to the oil passage (1255) of the rotary shaft (125) through the differential pressure oil supply unit (180), while another portion of the oil may be supplied directly to the oil passage (1255) of the rotary shaft (125) through the pumping oil supply unit (190) without passing through the oil storage space (110d).
  • the basic configurations and the resulting operational effects of the oil recovery unit (170), differential pressure oil supply unit (180), and pumping oil supply unit (190) are almost similar to those of the above-described embodiments, and therefore, a description thereof will be provided instead of the above-described embodiments.
  • the oil path (1255) of the rotating shaft (125) may be separated into a first oil path (1255a) and a second oil path (1255b).
  • the first oil path (1255a) may be connected to a differential pressure oil supply unit (180), and the second oil path (1255b) may be connected to a pumping oil supply unit (190).
  • one end of the first oil path (1255a) may be connected to an oil pressure chamber (182) forming a differential pressure oil supply unit (180), and one end of the second oil path (1255b) may be connected to an oil pumping passage (191) forming a pumping oil supply unit (190).
  • oil passing through the differential pressure oil supply unit (180) can flow into the first oil channel (1255a), and oil passing through the pumping oil supply unit (190) can flow into the second oil channel (1255b).
  • oil backflow between the first oil channel (1255a) and the second oil channel (1255b) can be suppressed, thereby increasing the amount of oil supplied to the back pressure space (S) and/or the bearing surface (B).
  • first oil channel (1255a) and the second oil channel (1255b) may be connected to each other in the middle of the rotation shaft (125) to form a single oil channel at the outlet side, or the first oil channel (1255a) and the second oil channel (1255b) may be separated at both ends to form independent oil channels.
  • first oil passage (1255a) and the second oil passage (1255b) are partially separated, thereby partially suppressing the backflow between the first oil passage (1255a) and the second oil passage (1255b), thereby increasing the amount of oil supplied to the back pressure space (S) and/or the bearing surface (B) while simplifying the processing of the oil passage (1255).
  • first oil passage (1255a) and the second oil passage (1255b) are completely separated, thereby more effectively suppressing the backflow between the first oil passage (1255a) and the second oil passage (1255b), thereby further increasing the amount of oil supplied to the back pressure space (S) and/or the bearing surface (B).
  • At least one of the first oil channel (1255a) and the second oil channel (1255b) may be formed at least partially diagonally to increase the amount of oil supplied to the corresponding oil channel.
  • the first oil passage (1255a) connected to the differential pressure oil supply unit (180) may be formed diagonally with respect to the axial direction of the rotating shaft (125), and the second oil passage (1255b) connected to the pumping oil supply unit (190) may be formed in the axial direction of the rotating shaft (125) so as to be merged into the first oil passage (1255a). Accordingly, while increasing the amount of oil supplied through the first oil passage (1255a), the length of the second oil passage (1255b) may be shortened as much as possible to improve the machinability of the second oil passage (1255b).
  • a backflow prevention part (184) having a differential pressure communication hole (1841) as in the embodiment of FIG. 6 described above may be formed at one end of the first oil passage (1255a) facing the pump cover (e.g., oil pressure chamber) (145). Accordingly, even if the second oil passage (1255b) is merged into the middle of the first oil passage (1255a), the oil can be prevented from flowing back toward the storage space (110d) through the first oil passage (1255a).
  • the cross-sectional area (e.g., inner diameter) of the first oil passage (1255a) may be formed to be smaller than or equal to the cross-sectional area (e.g., inner diameter) of the second oil passage (1255b).
  • the cross-sectional area (e.g., inner diameter) of the differential pressure communication hole (1841) of the backflow prevention unit (184) may be formed to be smaller than the cross-sectional area (e.g., inner diameter) of the second oil passage (1255b).
  • the first oil passage (1255a) connected to the differential pressure oil supply unit (180) may be formed diagonally with respect to the axial direction of the rotating shaft (125), and the two ends of the second oil passage (1255b) connected to the pumping oil supply unit (190) may be formed along the axial direction of the rotating shaft (125) so that they are separated from the two ends of the first oil passage (1255a). Accordingly, the oil of the second oil passage (1255b) may be prevented from flowing backward toward the first oil passage (1255a), thereby increasing the amount of oil supplied through the first oil passage (1255a).
  • the first oil passage (1255a) may penetrate through the outer surface of the eccentric portion (1251) forming the bearing surface (B) together with the main support hole (1321) of the main frame (130), and the second oil passage (1255b) may penetrate through the upper end of the rotary shaft (125) connected to the back pressure space (S), that is, the bottom surface of the eccentric portion (1251).
  • the first oil passage (1255a) may appropriately supply oil in an amount necessary for lubrication at the bearing surface (B) with the main frame (130) to suppress friction loss at the bearing surface (B), while the second oil passage (1255b) may appropriately supply oil at a pressure necessary for back pressure in the back pressure space (S), thereby effectively suppressing leakage between compression chambers even under low pressure ratio operating conditions.
  • a backflow prevention part (184) having a differential pressure communication hole (1841) may be formed at one end of the first oil channel (1255a) facing the pump cover (e.g., oil differential pressure chamber) (145) as in the embodiment of FIG. 6 described above, but in some cases, the backflow prevention part (184) described above may be excluded.
  • the backflow prevention part (184) described above may be excluded.
  • oil in the second oil channel (1255b) is prevented from flowing into the first oil channel (1255a), so that oil backflow in the first oil channel (1255a) may not occur significantly.
  • the cross-sectional area (e.g., inner diameter) of the first oil passage (1255a) may be formed to be smaller than or equal to the cross-sectional area (e.g., inner diameter) of the second oil passage (1255b).
  • the cross-sectional area (e.g., inner diameter) of the differential pressure communication hole (1841) of the backflow prevention unit (184) may be formed to be smaller than the cross-sectional area (e.g., inner diameter) of the second oil passage (1255b).
  • the focus has been on a high-pressure scroll compressor in which the driving motor is provided in the discharge space, but the same can be applied to a low-pressure scroll compressor in which the driving motor is provided in the suction space but the discharge space is provided on the discharge side of the compression section.

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

Abstract

L'invention divulgue un compresseur à spirale. Le compresseur à spirale comprend : un boîtier ; une unité de compression ; un arbre rotatif ; un séparateur d'huile ; une pompe à huile ; un cadre ; un couvercle de pompe ; et une unité d'alimentation en huile, l'unité d'alimentation en huile pouvant inclure : une première unité d'alimentation en huile qui guide l'huile dans un espace de stockage vers un trajet d'écoulement d'huile ; et une seconde unité d'alimentation en huile qui est distincte de la première unité d'alimentation en huile et qui communique entre un côté d'évacuation de la pompe à huile et le trajet d'écoulement d'huile et qui guide l'huile évacuée de la pompe à huile vers le trajet d'écoulement d'huile. Grâce à cette configuration, l'huile récupérée dans le séparateur d'huile peut être fournie de façon régulière à un espace de contre-pression et/ou à une surface d'appui, ce qui permet d'améliorer l'efficacité de compression et d'étendre la plage de fonctionnement du compresseur. De plus, l'huile présente dans l'espace de stockage est empêchée de refluer vers le séparateur d'huile afin de réduire la perte d'entrée d'un moteur d'entraînement, améliorant ainsi la performance du compresseur.
PCT/KR2024/005023 2024-04-15 2024-04-15 Compresseur à spirale Pending WO2025220758A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PCT/KR2024/005023 WO2025220758A1 (fr) 2024-04-15 2024-04-15 Compresseur à spirale

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/KR2024/005023 WO2025220758A1 (fr) 2024-04-15 2024-04-15 Compresseur à spirale

Publications (1)

Publication Number Publication Date
WO2025220758A1 true WO2025220758A1 (fr) 2025-10-23

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Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/KR2024/005023 Pending WO2025220758A1 (fr) 2024-04-15 2024-04-15 Compresseur à spirale

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Country Link
WO (1) WO2025220758A1 (fr)

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2003106268A (ja) * 2001-09-28 2003-04-09 哲哉 ▲荒▼田 スクロール流体機械の逆転阻止機構
JP2009127464A (ja) * 2007-11-21 2009-06-11 Panasonic Corp 容積型膨張機、膨張機一体型圧縮機および冷凍サイクル装置
JP2011163227A (ja) * 2010-02-10 2011-08-25 Nippon Soken Inc 圧縮機
JP2017106377A (ja) * 2015-12-09 2017-06-15 株式会社デンソー 圧縮機
KR20230081922A (ko) * 2021-11-30 2023-06-08 엘지전자 주식회사 스크롤 압축기

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2003106268A (ja) * 2001-09-28 2003-04-09 哲哉 ▲荒▼田 スクロール流体機械の逆転阻止機構
JP2009127464A (ja) * 2007-11-21 2009-06-11 Panasonic Corp 容積型膨張機、膨張機一体型圧縮機および冷凍サイクル装置
JP2011163227A (ja) * 2010-02-10 2011-08-25 Nippon Soken Inc 圧縮機
JP2017106377A (ja) * 2015-12-09 2017-06-15 株式会社デンソー 圧縮機
KR20230081922A (ko) * 2021-11-30 2023-06-08 엘지전자 주식회사 스크롤 압축기

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