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WO2025198159A1 - Compresseur à spirale - Google Patents

Compresseur à spirale

Info

Publication number
WO2025198159A1
WO2025198159A1 PCT/KR2025/000582 KR2025000582W WO2025198159A1 WO 2025198159 A1 WO2025198159 A1 WO 2025198159A1 KR 2025000582 W KR2025000582 W KR 2025000582W WO 2025198159 A1 WO2025198159 A1 WO 2025198159A1
Authority
WO
WIPO (PCT)
Prior art keywords
shaft
passage
pin
oil
sectional area
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/KR2025/000582
Other languages
English (en)
Korean (ko)
Inventor
이경재
서정기
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.)
Hanon Systems Corp
Original Assignee
Hanon Systems Corp
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 Hanon Systems Corp filed Critical Hanon Systems Corp
Publication of WO2025198159A1 publication Critical patent/WO2025198159A1/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
    • 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
    • F04C27/00—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/02—Lubrication; Lubricant separation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet

Definitions

  • the present invention relates to a scroll compressor, and more particularly, to a scroll compressor capable of supplying oil from a back pressure chamber to a suction chamber and shaft bearing through a crank pin and a shaft in a structure in which a shaft bearing is arranged on the suction chamber side.
  • A/C air conditioning
  • A/C systems as a component of the cooling system, include a compressor that compresses low-temperature, low-pressure gaseous refrigerant drawn from the evaporator into high-temperature, high-pressure gaseous refrigerant and sends it to the condenser.
  • Compressors can be divided into reciprocating types, which compress refrigerant through the reciprocating motion of a piston, and rotary types, which compress through a rotary motion.
  • Reciprocating types depending on the method of transmission of the drive source, include crank types, which transmit refrigerant to multiple pistons using a crank, and swash plate types, which transmit refrigerant through a rotating shaft with a swash plate installed.
  • Rotary types include vane rotary types, which use a rotating rotary shaft and vanes, and scroll types, which use an orbiting scroll and a fixed scroll.
  • Scroll compressors are widely used for refrigerant compression in air conditioning systems because they can achieve a relatively high compression ratio compared to other types of compressors, and because the suction, compression, and discharge cycles of the refrigerant are smoothly connected to obtain stable torque.
  • Scroll compressors may be implemented as electric compressors, in which case they may be named electric compressors and fall under the category of scroll compressors.
  • the refrigerant is compressed through the interaction between the orbiting scroll and the fixed scroll.
  • the orbiting scroll is connected to an eccentric bush located at the end of a drive shaft connected to a motor, and as the drive shaft rotates, the rotational force transmitted by the eccentric bush forms a compression region with the fixed scroll.
  • the compressed refrigerant is then discharged through a discharge port formed in the fixed scroll.
  • FIG. 1 shows a scroll compressor (10) structure in which a shaft bearing (15a) is arranged adjacent to the conventional back pressure chamber (B).
  • the fixed scroll (13) and the orbiting scroll (12) are interlocked to compress the refrigerant, and the shaft (17) connected to the driving unit is connected to an eccentric bush (19) by a pin (18).
  • the eccentric bush (19) is supported by a bush bearing (15b) and rotates to orbit the orbiting scroll (12).
  • An oil recovery line is connected to the discharge chamber where the refrigerant is discharged, and a first pressure reducing nozzle (14a) and a second pressure reducing nozzle (14b) are arranged in the oil recovery line.
  • the oil is depressurized as it passes through the first pressure reducing nozzle (14a), and some of the oil (E) flows into the suction chamber (A) and some of the oil (D) flows into the back pressure chamber (B).
  • the oil flowing into the suction chamber (A) passes through the second pressure reducing nozzle (14b) and is depressurized once more.
  • a sealing member (16) is placed between the shaft (17) and the center housing (11), so that oil does not flow into the suction chamber (A) but fills the back pressure chamber (B), and the oil flowing into the back pressure chamber (B) flows into the bush bearing (15b) and shaft bearing (15a) to lubricate them.
  • the sealing member (16) is positioned closer to the back pressure chamber (B), and the shaft bearing (15a) is positioned closer to the suction chamber (A).
  • oil (D) flowing into the back pressure chamber (B) can lubricate the bush bearing (15b), but cannot be supplied toward the shaft bearing (15a) because the back pressure chamber (B) is blocked by the sealing member (16). As a result, the shaft bearing (15a) cannot be lubricated, which may result in damage to the parts.
  • a scroll compressor which may include a casing including a seating portion into which a shaft connected to a driving portion is inserted and supported; a suction chamber into which refrigerant is introduced into the interior of the casing; a compression mechanism including an orbiting scroll and a fixed scroll that engages with the orbiting scroll and compresses the refrigerant; an eccentric bush connecting the shaft and the orbiting scroll; a crank pin connecting the shaft and the eccentric bush; a shaft bearing disposed in the seating portion and supporting rotation of the shaft; a sealing member disposed between the inner surface of the seating portion and the shaft; a back pressure chamber formed between the sealing member and the orbiting scroll; and an oil supply means penetrating the crank pin and the shaft and supplying oil in the back pressure chamber to the suction chamber.
  • the sealing member divides the suction chamber and the back pressure chamber, and the shaft bearing is disposed on the suction chamber side of the mounting portion with respect to the sealing member, a scroll compressor.
  • the oil supply means can supply oil from the back pressure chamber to the shaft bearing.
  • the oil supply means may include a pin passage part arranged in the longitudinal direction (X) inside the crank pin and into which oil from the back pressure chamber flows; and a shaft passage part arranged inside the shaft and connected to the pin passage part and supplying oil to the shaft bearing and suction chamber.
  • the shaft flow path may include a first shaft flow path arranged in a longitudinal direction (X) inside the shaft; and a second shaft flow path arranged in a radial direction inside the shaft.
  • the shaft flow path may further include a communication path that connects the first shaft flow path and the second shaft flow path and whose cross-sectional area gradually increases from the first shaft flow path toward the second shaft flow path.
  • the sum of the length of the shaft pin hole formed in the shaft and the length of the bush pin hole formed in the eccentric bush is longer than the length of the crank pin, and a tapered portion whose cross-sectional area gradually decreases from the pin passage portion toward the shaft passage portion may be formed at the end of the shaft pin hole.
  • the first shaft passage may be formed to have a cross-sectional area smaller than that of the shaft pin hole and a cross-sectional area larger than that of the pin passage portion.
  • the second shaft path may form a predetermined inclination angle ( ⁇ ) based on the vertical direction (Z) and may be tilted in the direction of the shaft bearing.
  • the cross-sectional area of the pin passage when oil enters the first shaft passage from the pin passage, the cross-sectional area of the pin passage may be formed to be larger than the cross-sectional area of the first shaft passage so that the pressure of the oil is reduced.
  • the pin passage part includes a first pin passage that is arranged inside the crank pin and communicates with the back pressure chamber; and a second pin passage that is arranged inside the crank pin and communicates the first pin passage and the first shaft passage; wherein the cross-sectional area of the first pin passage may be larger than the cross-sectional area of the second pin passage.
  • the shaft flow path may further include an intermediate region formed to extend radially from the inside of the shaft and arranged between the pin flow path and the first shaft flow path.
  • the pin oil section and the first shaft oil section connected to the intermediate region may be connected to each other in an intersecting manner with respect to the longitudinal direction (X).
  • the mounting portion may have a shape that is open toward the suction chamber so that the shaft bearing can be inserted in a direction from the suction chamber side toward the back pressure chamber side.
  • a stopper block supporting the sealing member may be formed on the outer surface of the shaft.
  • the sum of the length of the shaft pin hole formed in the shaft and the length of the bush pin hole formed in the eccentric bush is longer than the length of the crank pin, and a tapered portion whose cross-sectional area gradually decreases from the pin passage portion toward the shaft passage portion may be formed at the end of the shaft pin hole.
  • oil from a back pressure chamber can be supplied to the shaft bearing and the suction chamber through a passage formed in the crank pin and shaft, thereby lubricating various parts including the shaft bearing.
  • the pressure in the back pressure chamber forms an intermediate pressure that is higher than that in the suction chamber but lower than that in the discharge chamber.
  • This intermediate pressure allows oil to be smoothly supplied from the back pressure chamber to the suction chamber through the passages formed in the crank pin and shaft. This allows the compressor to be designed without the need for a conventional pressure reducing nozzle, thereby reducing the manufacturing cost and weight of the compressor.
  • Figure 1 is a partial cross-sectional view showing a scroll compressor structure in which a shaft bearing is arranged adjacent to a conventional back pressure chamber.
  • Figure 2 is a partial cross-sectional view showing a scroll compressor structure in which a shaft bearing is arranged adjacent to the suction chamber side.
  • Fig. 3 is a cross-sectional view showing a scroll compressor structure according to an embodiment of the present invention.
  • Fig. 4 is a cross-sectional view showing a first embodiment of an oil supply means according to the present invention.
  • Fig. 5 is a cross-sectional view showing a second embodiment of an oil supply means according to the present invention.
  • Fig. 6 is a cross-sectional view showing a third embodiment of an oil supply means according to the present invention.
  • Fig. 7 is a cross-sectional view showing a fourth embodiment of an oil supply means according to the present invention.
  • Fig. 8 is a cross-sectional view showing a fifth embodiment of an oil supply means according to the present invention.
  • the compressor of the present invention may be an electric compressor or a scroll compressor, and the structure of the electric compressor or the scroll compressor will be examined below.
  • an electric compressor or scroll compressor to which the present invention is applied may include a casing (110), a driving unit (120) that generates driving force inside the casing (110), a shaft (130) that is rotated by the driving unit (120), and a compression mechanism (140) that is driven by the shaft (130) to compress refrigerant.
  • the casing (110) may include a center housing (111) that accommodates the driving unit (120), a front housing (112) that accommodates an inverter (150) that controls the driving unit (120), a compression mechanism (140) including a rotating scroll (142) coupled to a shaft (130) and a fixed scroll (141) that compresses refrigerant by engaging the rotating scroll (142), and a rear housing (113) coupled to the fixed scroll (141) of the compression mechanism (140) and forming a discharge chamber (T).
  • a center housing (111) that accommodates the driving unit (120)
  • a front housing (112) that accommodates an inverter (150) that controls the driving unit (120
  • a compression mechanism (140) including a rotating scroll (142) coupled to a shaft (130) and a fixed scroll (141) that compresses refrigerant by engaging the rotating scroll (142)
  • a rear housing (113) coupled to the fixed scroll (141) of the compression mechanism (140) and forming a discharge chamber (T
  • the rotary scroll (142) of the compression mechanism (140) may be connected to the shaft (130) by an eccentric bush (149), and the rear housing (113) may be fastened to the fixed scroll (141).
  • the rear housing (113) may accommodate the compression mechanism (140) and may be fastened to the center housing (111).
  • the above driving unit (120) may be a motor and include a stator (122) fixed to the center housing (111) and a rotor (121) that rotates inside the stator (122) through interaction with the stator (122).
  • One end of the shaft (130) may be rotatably supported on a support bearing (171).
  • the other end of the shaft (130) may be rotatably supported on a shaft bearing (172) and may be connected to the compression mechanism (140) by an eccentric bush (149).
  • the eccentric bush (149) and the shaft (130) can be connected with their centers of rotation eccentrically by the crank pin (190).
  • eccentric bush (149) can be rotatably supported on a bush bearing (173) provided in the compression mechanism (140). And, in conjunction with the bush bearing (173), it transmits rotational force to the rotating scroll (142).
  • the above compression mechanism (140) may include a fixed scroll (141) arranged on the opposite side of the driving unit (120) and a rotating scroll (142) that is engaged with the fixed scroll (141) to form a compression chamber (C) and rotates by the shaft (130).
  • a discharge port (141d) for discharging the refrigerant compressed in the compression chamber (C) may be formed at the center side of the fixed scroll (141).
  • the discharge port (141d) may be communicated with a discharge room (T) formed between the fixed scroll (141) and the rear housing (113).
  • an opening/closing valve (141a) for opening and closing the discharge port (141d) according to the discharge pressure may be arranged in the fixed scroll (141).
  • an oil recovery unit may be formed that is connected to the discharge chamber (T) and penetrates the fixed scroll (141) and the center housing (111).
  • a pressure reducing device (160) may be arranged in the oil recovery unit. Oil recovered from the discharge chamber (T) may be supplied to the back pressure chamber after passing through the pressure reducing device (160).
  • a scroll compressor according to this configuration can transmit rotational force to the orbiting scroll (142) when power is applied to the driving unit (120) so that the shaft (130) rotates together with the rotor (121). Then, the orbiting scroll (142) performs a rotational movement by the shaft (130), so that the compression chamber (C) can continuously move toward the center and reduce its volume. Then, the refrigerant can be introduced into the driving unit receiving space through the refrigerant inlet (not shown) formed in the center housing (111). Then, the refrigerant in the driving unit receiving space can be sucked into the compression chamber (C) through the refrigerant passage hole (not shown) formed in the center housing (111).
  • the refrigerant sucked into the compression chamber (C) can be compressed and discharged into the discharge chamber (T) through the discharge port (141d) while moving toward the center along the movement path of the compression chamber (C).
  • a series of processes are repeated in which the refrigerant discharged into the discharge chamber (T) is discharged to the outside of the scroll compressor through the refrigerant discharge port (113a) formed in the rear housing (113).
  • the shaft (130) is rotatably supported by the support bearing (171) and the shaft bearing (172), and the orbiting scroll (142) is rotatably supported with respect to the shaft (130) by the bush bearing (173).
  • the bush bearing (173) may be formed as a bearing different from the support bearing (171) and the shaft bearing (172) in order to reduce the weight and size of the assembly (hereinafter, the orbiting body) of the bush bearing (173) and the orbiting scroll (142).
  • the support bearing (171) and the shaft bearing (172) fixed to the casing (110) may each be formed as ball bearings to minimize friction loss.
  • the bush bearing (173) which is proportional to the weight and size of the rotating body as it rotates together with the rotating scroll (142) can be formed as a needle roller bearing or slide bush bearing which is smaller in weight and size and cheaper than a ball bearing.
  • the above shaft bearing (172) is arranged on the inner surface of the mounting portion (111b), comes into contact with the outer surface of the shaft (130), and can support the rotation of the shaft (130).
  • a stopper block (135) that protrudes radially and supports the sealing member (180) can be formed on the outer surface of the shaft (130).
  • crank pin (190) can connect the shaft (130) and the eccentric bush (149). At this time, the crank pin (190) can be connected so that the center of rotation between the shaft (130) and the eccentric bush (149) is eccentric.
  • the shaft passage part (220) can be placed inside the shaft (130) and connected to the pin passage part (210).
  • the shaft passage part (220) can supply oil introduced from the pin passage part (210) to the shaft bearing (172) and the suction chamber (A).
  • the above shaft passage (220) may include a first shaft passage (221), a second shaft passage (223), and a communication passage (26).
  • the first shaft passage (221) may be arranged in the longitudinal direction (X) inside the shaft (130), and the second shaft passage (223) may be arranged in the radial direction inside the shaft (130).
  • the pin-shaped portion (210) according to the first embodiment of the present invention can be formed in the shape of an orifice having a very small cross-sectional area inside the crank pin (190).
  • the length of the shaft pin hole (130a) and bush pin hole (149a) into which the crank pin (190) is inserted can be formed to be longer than the crank pin.
  • a first shaft passage (221) having a cross-sectional area smaller than that of the shaft pin hole (130a) and a cross-sectional area larger than that of the pin passage (210) can be formed.
  • the oil recovery line and pressure reducing nozzle connecting the back pressure chamber (B) and the suction chamber (A) on the inner wall of the center housing (111) are removed.
  • a second pressure reducing nozzle (14b) is arranged between the back pressure chamber (B) and the suction chamber (A), but in an embodiment of the present invention, this pressure reducing nozzle can be removed.
  • the scroll compressor (100) can remove the pressure reducing nozzle and the inner wall portion of the center housing (111) where the pressure reducing nozzle is arranged, so that it is expected to have the effect of contributing to cost reduction and weight reduction.
  • the oil supply means (200) may include a pin passage part (210) and a shaft passage part (220).
  • the cross-sectional area of the pin oil passage (210) can be formed to be larger than the cross-sectional area of the first shaft oil passage (221).
  • an oil supply means (200) according to a third embodiment of the present invention is disclosed.
  • the oil supply means (200) may include a pin passage part (210) and a shaft passage part (220).
  • the above pin oil portion (210) can be arranged in the longitudinal direction (X) inside the crank pin (190), and oil from the back pressure chamber (B) can be introduced.
  • the shaft passage part (220) can be placed inside the shaft (130) and connected to the pin passage part (210).
  • the shaft passage part (220) can supply oil introduced from the pin passage part (210) to the shaft bearing (172) and the suction chamber (A).
  • the above shaft passage (220) may include a first shaft passage (221) and a second shaft passage (223).
  • the first shaft passage (221) may be arranged in the longitudinal direction (X) within the shaft (130), and the second shaft passage (223) may be arranged in the radial direction within the shaft (130).
  • the pin passage (210) may include a first pin passage (211) and a second pin passage (213).
  • the first pin passage (211) may be arranged inside the crank pin (190) and may be connected to the back pressure chamber (B).
  • the second pin passage (213) may be arranged inside the crank pin (190) and may be connected to the first pin passage (211) and the first shaft passage (221).
  • the cross-sectional area of the first pin channel (211) and the cross-sectional area of the second pin channel (213) may be designed differently.
  • the cross-sectional area of the first pin channel (211) may be formed to be larger than the cross-sectional area of the second pin channel (213) so that the pressure of the oil is reduced when the oil enters the second pin channel (213) from the first pin channel (211).
  • crank pin (190) when the crank pin (190) is coupled to the shaft (130), a difference can be generated between the cross-sectional area of the first pin passage (211) and the cross-sectional area of the second pin passage (213).
  • the cross-sectional area of the bush pin hole (149a) formed in the eccentric bush (149) is designed to be the same as the cross-sectional area of the crank pin (190), and the cross-sectional area of the shaft pin hole (130a) formed in the shaft (130) is designed to be smaller than the cross-sectional area of the crank pin (190).
  • crank pin (190) When inserting a crank pin (190) into a bush pin hole (149a) during the process step, the crank pin (190) is inserted with ease, but when inserting the crank pin (190) into a shaft pin hole (130a), force must be applied to press it in. During this process, the press-in portion (190a) of the crank pin (190) is deformed.
  • the cross-sectional area of the pin passage (210) was the same, but in the process step of pressing the crank pin (190) into the shaft (130), a first pin passage (211) and a second pin passage (213) with a reduced cross-sectional area due to pressing were created.
  • the difference between the cross-sectional area of the first pin path (211) and the cross-sectional area of the second pin path (213) can be reflected through the manufacturing process during the design of the initial pin path section.
  • the cross-sectional area of the second pin oil passage (213) may be formed to be the same as the cross-sectional area of the first shaft oil passage (221). In this case, when the oil enters the second pin oil passage (213) from the first pin oil passage (211), a primary decompression occurs, and when it enters the first shaft oil passage (221) from the second pin oil passage (213), no decompression occurs.
  • the cross-sectional area of the second pin passage (213) may be formed to be larger than the cross-sectional area of the first shaft passage (221), in which case additional secondary decompression occurs when oil enters the first shaft passage (221) from the second pin passage (213).
  • the oil (D) can be supplied from the back pressure chamber (B) to the suction chamber (A) through the pin passage (210) and the shaft passage (220) due to the pressure difference.
  • the depressurized oil (D) passing through the first and second pin passages (211, 213) passes through the first shaft passage (221) and then disperses radially through the second shaft passage (223) and is supplied to the suction chamber (A). Since the shaft (130) rotates by the driving unit (120), the oil (D) can be dispersed radially by centrifugal force and sprayed into the suction chamber (A). Then, it is supplied to various parts of the suction chamber (A) and the shaft bearing (172) and lubricates the shaft bearing (172).
  • an oil supply means (200) according to a fourth embodiment of the present invention is disclosed.
  • the oil supply means (200) may include a pin oil passage part (210) and a shaft oil passage part (220).
  • the above pin oil portion (210) can be arranged in the longitudinal direction (X) inside the crank pin (190), and oil (D) from the back pressure chamber (B) can be introduced.
  • the above shaft passage part (220) may include a first shaft passage (221), a second shaft passage (223), and an intermediate region (225).
  • the first shaft passage (221) may be arranged in the longitudinal direction (X) inside the shaft (130), and the second shaft passage (223) may be arranged radially inside the shaft (130).
  • the intermediate region (225) may be formed to extend radially inside the shaft (130), and may be arranged between the pin passage part (210) and the first shaft passage (221).
  • the pin oil section (210) and the first shaft oil section (221) connected to the intermediate region (225) can be connected to each other in an intersecting manner based on the axial direction (X) of the shaft (130).
  • oil (D) flows from the pin passage (210) into the intermediate region (225), flows radially from the intermediate region (225), and flows into the first shaft passage (221) spaced apart based on the axial direction (X) of the shaft (130).
  • the oil (D) is distributed radially in the second shaft passage (223), and various parts of the suction chamber (A) and the shaft bearing (172) can be supplied with oil (D) for lubrication.
  • an oil supply means (200) according to a fifth embodiment of the present invention is disclosed.
  • the oil supply means (200) may include a pin passage part (210) and a shaft passage part (220).
  • the above shaft passage part (220) may include a first shaft passage (221) and a second shaft passage (223), and the above pin passage part (210) may include a first pin passage (211) and a second pin passage (213).
  • the second shaft passage (223) can form a predetermined inclination angle ( ⁇ ) with respect to the vertical direction (Z). At this time, the second shaft passage (223) can be arranged to be inclined toward the shaft bearing (172).
  • This structure can improve the lubrication of the shaft bearing (172) by allowing the oil (D) sprayed from the second shaft oil passage (223) to be concentrated on the shaft bearing (172).
  • the present invention can smoothly lubricate various parts including the shaft bearing by supplying oil from the back pressure chamber to the shaft bearing and the suction chamber through a passage formed in the crank pin and the shaft in a structure in which the shaft bearing is arranged on the suction chamber side through the above-described embodiments.
  • These embodiments can stably perform lubrication of various parts using back pressure chamber oil of an electric compressor.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)

Abstract

La présente invention se rapporte à un compresseur à spirale. Le compresseur à spirale peut comprendre : un carter comprenant une unité de siège dans laquelle un arbre est inséré et supporté ; une chambre d'aspiration par laquelle un réfrigérant est introduit dans le carter ; un mécanisme de compression comprenant une spirale rotative et une spirale fixe en prise avec la spirale rotative pour comprimer le réfrigérant ; une chambre de contre-pression formée entre l'unité de siège et la spirale rotative ; un arbre relié à une unité d'entraînement et ayant une extrémité insérée dans l'unité de siège ; une douille excentrique reliant l'arbre à la spirale rotative ; un maneton reliant l'arbre à la douille excentrique ; un palier d'arbre disposé sur l'unité de siège et supportant la rotation de l'arbre ; un élément d'étanchéité disposé entre la surface interne de l'unité de siège et l'arbre ; et un moyen d'alimentation en huile passant à travers le maneton et l'arbre et faisant passer l'huile de la chambre de contre-pression à la chambre d'aspiration. Selon la présente invention, de l'huile peut être fournie à partir de la chambre de contre-pression pour lubrifier régulièrement le palier d'arbre adjacent au côté chambre d'aspiration et divers composants de la chambre d'aspiration.
PCT/KR2025/000582 2024-03-22 2025-01-10 Compresseur à spirale Pending WO2025198159A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
KR1020240039856A KR20250142649A (ko) 2024-03-22 2024-03-22 스크롤 압축기
KR10-2024-0039856 2024-03-22

Publications (1)

Publication Number Publication Date
WO2025198159A1 true WO2025198159A1 (fr) 2025-09-25

Family

ID=97139930

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/KR2025/000582 Pending WO2025198159A1 (fr) 2024-03-22 2025-01-10 Compresseur à spirale

Country Status (2)

Country Link
KR (1) KR20250142649A (fr)
WO (1) WO2025198159A1 (fr)

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2001329979A (ja) * 2000-05-24 2001-11-30 Toyota Industries Corp スクロール型圧縮機における潤滑構造
KR20180117471A (ko) * 2017-04-19 2018-10-29 엘지전자 주식회사 전동식 압축기
KR20210090492A (ko) * 2020-01-10 2021-07-20 엘지전자 주식회사 전동식 압축기
CN114320902A (zh) * 2020-09-30 2022-04-12 安徽威灵汽车部件有限公司 涡旋压缩机、空调设备及车辆
KR102452563B1 (ko) * 2018-05-04 2022-10-11 한온시스템 주식회사 압축기

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2001329979A (ja) * 2000-05-24 2001-11-30 Toyota Industries Corp スクロール型圧縮機における潤滑構造
KR20180117471A (ko) * 2017-04-19 2018-10-29 엘지전자 주식회사 전동식 압축기
KR102452563B1 (ko) * 2018-05-04 2022-10-11 한온시스템 주식회사 압축기
KR20210090492A (ko) * 2020-01-10 2021-07-20 엘지전자 주식회사 전동식 압축기
CN114320902A (zh) * 2020-09-30 2022-04-12 安徽威灵汽车部件有限公司 涡旋压缩机、空调设备及车辆

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