WO2018151512A1 - Compresseur à spirale - Google Patents

Compresseur à spirale Download PDF

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Publication number
WO2018151512A1
WO2018151512A1 PCT/KR2018/001906 KR2018001906W WO2018151512A1 WO 2018151512 A1 WO2018151512 A1 WO 2018151512A1 KR 2018001906 W KR2018001906 W KR 2018001906W WO 2018151512 A1 WO2018151512 A1 WO 2018151512A1
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WO
WIPO (PCT)
Prior art keywords
bearing
center
motor
distance
scroll
Prior art date
Application number
PCT/KR2018/001906
Other languages
English (en)
Korean (ko)
Inventor
안현승
문치명
임권수
임재훈
정수철
Original Assignee
한온시스템 주식회사
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
Priority claimed from KR1020180016942A external-priority patent/KR102273425B1/ko
Application filed by 한온시스템 주식회사 filed Critical 한온시스템 주식회사
Priority to JP2019512978A priority Critical patent/JP6757465B2/ja
Priority to CN202110619068.8A priority patent/CN113279958B/zh
Priority to DE112018000087.7T priority patent/DE112018000087B4/de
Priority to US16/326,989 priority patent/US11359627B2/en
Priority to CN201880003464.4A priority patent/CN109690085B/zh
Publication of WO2018151512A1 publication Critical patent/WO2018151512A1/fr
Priority to US17/743,802 priority patent/US20220268277A1/en

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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
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00

Definitions

  • the present invention relates to a scroll compressor, and more particularly, to a scroll compressor capable of compressing a refrigerant by forming a compression chamber together with a fixed scroll and the fixed scroll and pivoting with respect to the fixed scroll. Relates to a compressor.
  • a vehicle is provided with an air conditioning (A / C) for indoor air conditioning.
  • an air conditioning apparatus includes a compressor as a configuration of a cooling system that compresses a low temperature low pressure gaseous refrigerant introduced from an evaporator into a high temperature high pressure gaseous refrigerant and sends it to a condenser.
  • the compressor applied to the vehicle is typically formed as a mechanical compressor driven by receiving the driving force of the engine, but for example, the compressor applied to the electric vehicle may be formed as an electric compressor driven by the driving force of the motor.
  • the compressor has a reciprocating type to compress the refrigerant in accordance with the reciprocating motion of the piston and a rotary type to perform the compression while rotating.
  • the reciprocating type includes a crank type for transferring to a plurality of pistons using a crank, a swash plate type for transferring to a rotating shaft provided with a swash plate, and a rotary type vane rotary type using a rotating rotary shaft and vanes.
  • Scroll compressors are widely used for refrigerant compression in air conditioners and the like because they have a relatively high compression ratio compared to other types of compressors, and the suction, compression, and discharge strokes of the refrigerant are smooth and stable torque can be obtained.
  • Korean Patent Laid-Open Publication No. 10-2016-0081675 discloses a conventional scroll compressor that is electrically driven.
  • a conventional scroll compressor is a motor (3) for generating a driving force inside the casing 11, the rotary shaft 4 rotated by the motor (3) And a swing scroll 6 which pivots by the rotational shaft 4, and a fixed scroll 5 which forms a compression chamber together with the swing scroll 6.
  • the first bearing 82 and the motor 3 which rotatably support the rotating shaft 4 with respect to the casing 11 on one side of the motor 3 are referred to.
  • a third bearing 83 rotatably supporting the rotation shaft 4 with respect to the scroll 6.
  • the load capacity of the second bearing 81 is greater than that of the first bearing 82 and the third bearing 83.
  • an object of this invention is to provide the scroll compressor which can prevent the damage of the bearing which supports a rotating shaft between a motor and a rotating scroll.
  • Another object of the present invention is to provide a scroll compressor capable of suppressing cost, size and weight increase due to a bearing.
  • the casing A motor for generating a driving force in the casing; A rotating shaft rotated by the motor; A swing scroll which pivots by the rotation axis; A fixed scroll which forms a compression chamber together with the pivoting scroll; A first bearing rotatably supporting the rotation shaft with respect to the casing on one side of the motor; A second bearing rotatably supporting the rotating shaft with respect to the casing on the other side of the motor; And a third bearing rotatably supporting the rotating shaft with respect to the pivoting scroll on the opposite side of the first bearing with respect to the second bearing, wherein the center of the first bearing is extended in the extending direction of the rotating shaft.
  • the center of the second bearing is called the first bearing center
  • the center of the second bearing is called the second bearing center
  • the center of the third bearing is called the third bearing center
  • the center of the rotor of the motor is called the motor center.
  • the distance between the first bearing center and the third bearing center is formed to be a predetermined distance
  • the distance between the motor center and the third bearing center is formed farther than the distance between the motor center and the first bearing center
  • Scroll compression wherein the distance between the second bearing center and the motor center is greater than the distance between the second bearing center and the third bearing center Provide a flag.
  • the distance between the motor center and the third bearing center may be 1.9 times the distance between the motor center and the first bearing center.
  • the distance between the second bearing center and the motor center may be formed to be included in the range of 1.17 times to 1.22 times the distance between the motor center and the first bearing center.
  • the distance between the second bearing center and the motor center may be formed to be 1.22 times the distance between the motor center and the first bearing center.
  • the second bearing may have the same load capacity as at least one of the first bearing and the third bearing.
  • the present invention the casing; A motor for generating a driving force in the casing; A rotating shaft rotated by the motor; A swing scroll which pivots by the rotation axis; A fixed scroll which forms a compression chamber together with the pivoting scroll; A first bearing rotatably supporting the rotation shaft with respect to the casing on one side of the motor; A second bearing rotatably supporting the rotating shaft with respect to the casing on the other side of the motor; And a third bearing rotatably supporting the rotating shaft with respect to the pivoting scroll on the opposite side of the first bearing with respect to the second bearing, wherein the center of the first bearing is extended in the extending direction of the rotating shaft.
  • the center of the second bearing is called the first bearing center
  • the center of the second bearing is called the second bearing center
  • the center of the third bearing is called the third bearing center
  • the distance between the second bearing center and the third bearing center is Provided is a scroll compressor that is formed closer than the distance between the second bearing center and the first bearing center.
  • the distance between the second bearing center and the first bearing center may be formed to be in a range of 2.97 times to 3.27 times the distance between the second bearing center and the third bearing center.
  • a distance between the second bearing center and the third bearing center may be formed closer than the distance between the second bearing center and the motor center.
  • the distance between the second bearing center and the motor center may be formed to be in a range of 1.60 times to 1.80 times the distance between the second bearing center and the third bearing center.
  • the distance between the motor center and the third bearing center may be formed farther than the distance between the motor center and the first bearing center.
  • the distance between the motor center and the third bearing center may be formed to be 1.9 times the distance between the motor center and the first bearing center.
  • the distance D1 between the first bearing center and the third bearing center may be formed at a predetermined distance.
  • the present invention the casing; A motor for generating a driving force in the casing; A rotating shaft rotated by the motor; A swing scroll which pivots by the rotation axis; A fixed scroll which forms a compression chamber together with the pivoting scroll; And a second bearing rotatably supporting the rotating shaft between the motor and the compression chamber, wherein the rotating shaft includes an eccentric bush that is rotated at a position overlapping with the second bearing in the axial direction of the rotating shaft.
  • the second bearing provides a scroll compressor that is formed as close to the compression chamber as possible within a range that does not interfere with the eccentric bush.
  • the casing includes: a first partition wall partitioning a space in which the motor is accommodated and a space in which the inverter 5 is accommodated; And a second partition wall partitioning a space in which the motor is accommodated and a space in which the compression chamber is provided, wherein the first partition includes a first support groove into which a first bearing for supporting one end of the rotation shaft is inserted. And a second supporting groove into which the second bearing for supporting the other end of the rotating shaft is inserted, and the second supporting groove is formed from a surface of the second partition wall facing the compression chamber. It provides a scroll compressor that is formed intaglio.
  • the second support groove may be formed as shallow as possible within the range that the second bearing does not protrude axially from the second support groove.
  • a scroll compressor includes: a first bearing rotatably supporting a rotating shaft with respect to a casing on one side of a motor; A second bearing rotatably supporting a rotation shaft with respect to the casing on the other side of the motor; And a third bearing rotatably supporting the rotational axis with respect to the turning scroll on the opposite side of the first bearing relative to the second bearing, wherein the distance between the first bearing center and the third bearing center is formed at a predetermined distance. And the distance between the motor center and the third bearing center is formed farther than the distance between the motor center and the first bearing center, and the distance between the second bearing center and the motor center is formed farther than the distance between the second bearing center and the third bearing center. Can be. Thereby, breakage of the 2nd bearing which supports a rotating shaft between a motor and a rotating scroll can be prevented.
  • the second bearing may have the same load capacity as at least one of the first bearing and the third bearing. As a result, the cost, size and weight increase due to the bearing can be suppressed.
  • FIG. 1 is a cross-sectional view showing a scroll compressor according to an embodiment of the present invention
  • FIG. 2 is a diagram showing a load applied to the first bearing and the third bearing according to the distance between the motor center and the first bearing center and the distance between the motor center and the third bearing center in the scroll compressor of FIG.
  • FIG. 3 is a diagram illustrating a load applied to a second bearing according to the distance between the second bearing center and the motor center and the distance between the motor center and the third bearing center in the scroll compressor of FIG. 1.
  • FIG. 1 is a cross-sectional view showing a scroll compressor according to an embodiment of the present invention
  • Figure 2 is a scroll compressor of Figure 1 according to the distance between the motor center and the first bearing center and the distance between the motor center and the third bearing center
  • FIG. 3 is a diagram illustrating loads applied to a first bearing and a third bearing
  • FIG. 3 shows the second bearing according to the distance between the second bearing center and the motor center and the distance between the motor center and the third bearing center in the scroll compressor of FIG. 1.
  • a scroll compressor includes a casing 1, a motor 2 generating a driving force inside the casing 1, and the motor 2. It may include a rotary shaft (3) rotated by, a compression mechanism (4) driven by the rotary shaft (3) to compress the refrigerant.
  • the casing 1 includes a first housing 11 for accommodating the motor 2, a second housing 12 for accommodating an inverter 5 for controlling the motor 2, and the compression mechanism 4. It may include a third housing 13 for receiving the.
  • the first housing 11 includes an annular wall 111, a first partition wall 112 covering one end of the annular wall 111, and a second partition wall 113 covering the other end of the annular wall 111. ), And the annular wall 111, the first partition wall 112, and the second partition wall 113 may form a motor accommodating space in which the motor 2 is accommodated.
  • the second housing 12 may be coupled to the first partition wall 112 to form an inverter accommodation space in which the inverter 5 is accommodated.
  • the first partition wall 112 partitions the motor accommodating space and the inverter accommodating space, and a connector 6 connecting the inverter 5 and the motor 2 to one side of the first partition wall 112.
  • the connector hole 1121 may pass through.
  • the third housing 13 may be coupled to the second partition wall 113 to form a compression space in which the compression mechanism 4 is accommodated.
  • the second partition wall 113 partitions the motor receiving space and the compression space, and serves as a main frame for supporting the compression mechanism 4, and the motor on the center side of the second partition wall 113.
  • the fixed scroll 41 to be described later of the compression mechanism 4 is fastened to the second partition wall 113
  • the third housing 13 is fastened to the fixed scroll 41.
  • the present invention is not limited thereto, and the third housing 13 may accommodate the compression mechanism 4 and be fastened to the second partition wall 113.
  • the motor 2 may include a stator 21 fixed to the first housing 11 and a rotor 22 rotated in interaction with the stator 21 inside the stator 21. .
  • the rotating shaft 3 penetrates through the center of the rotor 22, and one end 31 of the rotating shaft 3 protrudes toward the first partition wall 112 based on the rotor 22.
  • the other end 32 of the rotating shaft 3 may protrude toward the second partition wall 113 with respect to the rotor 22.
  • One end portion 31 of the rotation shaft 3 may be rotatably supported by a first bearing 71 provided at the center side of the first partition wall 112.
  • a first support groove 1122 into which the first bearing 71 and one end portion 31 of the rotation shaft 3 are inserted, is formed at the center side of the first partition wall 112, and the first bearing ( 71 may be interposed between the first support groove 1122 and one end portion 31 of the rotation shaft 3.
  • the other end 32 of the rotating shaft 3 may be connected to the compression mechanism 4 through the bearing hole 1131 of the second partition wall 113.
  • first portion 321 supporting the other end portion 32 of the rotating shaft 3 to the second partition wall 113 and a second portion (eccentric bush) 322 connected to the compression mechanism 4 are provided.
  • the first part 321 is rotatably supported by the second bearing 72 provided in the bearing hole 1131 of the second partition wall 113, and the second part (eccentric bush) (
  • the 322 may be rotatably supported by the third bearing 73 provided in the compression mechanism 4.
  • a second portion (eccentric bush) 322 of the third bearing 73 and the other end 32 of the rotating shaft 3 is inserted into the turning scroll 42, which will be described later, of the compression mechanism 4.
  • a boss portion 423 is formed, and the third bearing 73 is to be interposed between the boss portion 423 and a second portion (eccentric bush) 322 of the other end portion 32 of the rotating shaft 3. Can be.
  • the compression mechanism 4 is fixed scroll 41 and the second partition wall 113 which is fixed to the second partition wall 113 on the opposite side of the motor 2 with respect to the second partition wall 113. And the fixed scroll 41 and engaged with the fixed scroll 41 to form two pairs of compression chambers, and may include a swing scroll 42 pivoted by the rotation shaft 3. .
  • the fixed scroll 41 protrudes from the disk-shaped fixed hard plate portion 411 and the compression surface of the fixed hard plate portion 411 and is fixed to the rotary wrap 422 to be described later with the rotating scroll 42 ( 412).
  • a discharge port 413 may be formed at a central side of the fixed hard plate part 411 to penetrate the fixed hard plate part 411 to discharge the refrigerant compressed in the compression chamber.
  • the discharge port 413 may be in communication with the discharge space formed between the fixed scroll 41 and the third housing 13.
  • the pivoting scroll 42 is a disk-shaped pivoting hard disk portion 421 and a pivoting wrap 422 projecting from the compression surface of the pivoting hard disk portion 421 to engage with the fixed wrap 412 to form the compression chamber It may include.
  • the boss 423 may be formed at the pivotal light plate part 421 to protrude to the opposite side of the pivot wrap 422 to insert the rotation shaft 3.
  • the rotating shaft 3 rotates together with the rotor 22 to transmit rotational force to the turning scroll 42.
  • the pivoting scroll 42 is pivoted by the second portion (eccentric bush) 322 of the rotary shaft 3, so that the compression chamber is continuously moved toward the center side can be reduced in volume.
  • the refrigerant may flow into the motor accommodating space through a refrigerant inlet (not shown) formed in the annular wall 111 of the first housing 11.
  • the refrigerant in the motor accommodating space may be sucked into the compression chamber through a refrigerant passage hole (not shown) formed in the second partition wall 113 of the first housing 11.
  • the refrigerant sucked into the compression chamber may be compressed while being moved to the center side along the movement path of the compression chamber and discharged to the discharge space through the discharge port 413.
  • a series of processes in which the refrigerant discharged into the discharge space is discharged to the outside of the scroll compressor through the refrigerant discharge port formed in the third housing 13 is repeated.
  • the rotation shaft 3 is rotatably supported by the first bearing 71, the second bearing 72, and the third bearing 73, which is applied to the second bearing 72.
  • the load to be applied is much larger than the load applied to the first bearing 71 and the load applied to the third bearing 73, so that the second bearing 72 can be easily damaged.
  • the second bearing 72 may be formed as a bearing having a greater load capacity than the first bearing 71 and the third bearing 73. In this case, the cost, size and weight of the second bearing 72 may be increased, which may result in an increase in the overall cost, size and weight of the scroll compressor.
  • the second bearing 72 is formed at a predetermined position so as to reduce the load applied to the second bearing 72 to prevent damage of the second bearing 72. Can be.
  • the load applied to the second bearing 72 is a load applied to the second bearing 72 by the rotating shaft 3, the rotational force applied to the rotating shaft 3, and the compression mechanism 4 is a refrigerant.
  • the operating point of the reaction force, the support point of the rotating shaft (3) is closely related.
  • the compression performance is lowered, which is not preferable.
  • the positional relationship between the action point of the rotational force, the action point of the reaction force, and the support point of the rotation shaft 3 is adjusted by considering this.
  • the load applied to the second bearing 72 can be reduced.
  • the center of the first bearing 71 is called a first bearing center CB1
  • the second bearing 72 The center is called the second bearing center CB2
  • the center of the third bearing 73 is called the third bearing center CB3
  • the center of the rotor 22 of the motor 2 is the motor center CM.
  • the motor center CM is an operating point of the rotational force
  • the third bearing center CB3 is an operating point of the reaction force
  • the first bearing center CB1 and the third bearing center CB3 may be configured such that the length of the scroll compressor (length in left and right in FIG. 1) is not increased by more than a predetermined value. ) And the distance between the third bearing center CB3 (hereinafter, referred to as a first distance) D1 may be formed at a predetermined distance.
  • the distance is a distance measured along the extending direction of the rotary shaft 3 (left and right in Fig. 1).
  • the motor center (CM), the motor center (CM) and the third bearing center (CB3) to ensure the maximum performance of the motor (2) in the motor accommodating space limited to the motor (2).
  • Distance (hereinafter referred to as 1-2 distance) (D12) may be formed farther than the distance between the motor center (CM) and the first bearing center (CB1) (hereinafter referred to as 1-1 distance) (D11).
  • the motor 2 should be formed so as not to interfere with the first and second partition walls 112 and 113, and to meet the above constraints to ensure the maximum performance (size) of the motor (2)
  • the motor center CM is preferably formed at an intermediate position between the first partition wall 112 and the second partition wall 113.
  • the first-second distance D12 is defined as the first-first. It may be formed farther than one distance (D11).
  • the motor center (CM) is the operating point of the rotational force, the first bearing 71 and the third bearing according to which position in the extension direction of the rotation axis (3) the motor shaft (CM)
  • the load applied to 73 is varied.
  • the sum L1 + L3 of the loads applied to the first bearing 71 and the third bearing 73 is minimum.
  • the motor center CM may be formed such that the first-second distance D12 is 1.9 times the first-first distance D11.
  • the second bearing center CB2 is formed on the second bearing 72 in a state in which the first bearing 71, the third bearing 73, and the motor center CM are formed as described above.
  • the distance between the second bearing center CB2 and the motor center CM (hereinafter, referred to as a 1-2-1 distance) D121 is defined as the second bearing center CB2 and the first bearing.
  • the distance between the three bearing centers CB3 (hereinafter, referred to as a 1-2-2 distance) D122 may be greater.
  • the second bearing center CB2 is a portion to which a load (hereinafter, referred to as a first load) by the rotational force and a load (hereinafter, referred to as a second load) by the reaction force are simultaneously applied, and the first load is the rotation force.
  • the second load may be proportional to the strength of the reaction force and the first-2-2 distance D122. Accordingly, as the second bearing center CB2 is adjacent to the first bearing 71 side, the first-2-1 distance D121 is decreased to decrease the first load, but the first-2- is reduced.
  • the second distance D122 may be increased to increase the second load.
  • the first-2-2 distance D122 is decreased to decrease the second load, but the first-2-1 is reduced.
  • the first load may be increased.
  • the reaction force is stronger than the rotational force
  • the total load applied to the second bearing 72 is more to the first-2-2 distance D122 than the first-2-1 distance D121. It is greatly influenced, so that the first-2-1 distance D121 is formed farther than the first-2-2 distance D122 can reduce the total load applied to the second bearing 72. have.
  • the first-2-1 distance D121 is the first-2 distance D12
  • the total load applied to the second bearing 72 is increased when the -2 distance D122 is too far away. That is, as a result of the experiment, as shown in FIG. 3, the total load L2 applied to the second bearing 72 is the first-2-1 distance D121 to the first-2 distance D12.
  • the second bearing center CB2 has the first-2-1 distance D121 so as to significantly reduce the total load L2 applied to the second bearing 72.
  • the ratio occupied in (D12) is preferably included in the range of 0.62 to 0.64, and the first-2-1 distance (D121) such that the total load (L2) applied to the second bearing 72 is minimized. ) May be formed so that the ratio occupies 0.62 in the first-second distance D12. That is, the second bearing center CB2 is preferably formed such that the first-2-1 distance D121 is in a range of 1.17 times to 1.22 times the first-first distance D11, It may be more preferable that the first-2-1 distance D121 is formed to be 1.22 times the first-first distance D11.
  • the first distance D1 is formed to be a predetermined distance, and the first-second distance D12 is formed farther than the first-first distance D11, As the first-2-1 distance D121 is formed farther than the first-2-2 distance D122, the performance of the motor 2 is maximized within the entire length of the predetermined scroll compressor. In addition, the load applied to the first bearing 71 and the third bearing 73 is minimized, but the load applied to the second bearing 72 is reduced to prevent breakage of the second bearing 72. can do.
  • the second bearing 72 when used as a bearing having a load level equivalent to that of the related art, durability of the second bearing 72 and the scroll compressor as a whole may be improved.
  • the second bearing 72 may be replaced with a bearing having a smaller load capacity than the conventional bearing. That is, the second bearing 72 may have the same load capacity as at least one of the first bearing 71 and the third bearing 73. As a result, the cost, size and weight increase due to the bearing can be suppressed. However, in consideration of safety, the second bearing 72 may have a larger load capacity than the first bearing 71 and the third bearing 73 even if the load capacity is smaller than that of the conventional art.
  • the first distance D1 is formed to be a predetermined distance, and the first-second distance D12 is formed farther than the first-first distance D11.
  • the 1-2-1 distance D121 is formed farther than the first-2-2 distance D122, but is not limited thereto.
  • the second bearing may be formed to be closer than the sum of the first-first distance D11 and the first-second distance D121.
  • the load applied to the 72 can be reduced.
  • the load applied to the second bearing 72 may be reduced only by forming the first-2-2 distance D122 closer to the first-2-1 distance D121.
  • the second bearing 72 is formed adjacent to the compression chamber.
  • the load applied to the second bearing 72 may be reduced.
  • the second portion (eccentric bush) 322 rotated at a position overlapping with the second bearing 72 in the axial direction of the rotation shaft 3 may interfere with the second bearing 72.
  • the second bearing 72 needs to be formed as close to the compression chamber as possible within the range that does not interfere with the second portion (eccentric bush) 322.
  • the second support groove 1132 is formed intaglio from the surface of the second partition 113 facing the compression chamber side, the second bearing 72 is the second support groove 1132 It can be formed as shallow as possible within the range that does not protrude from the (second direction) toward the second portion (eccentric bush) 322 from.
  • the present invention provides a scroll compressor that can prevent breakage of a bearing supporting a rotating shaft between a motor and a swinging scroll.
  • the present invention provides a scroll compressor that can suppress the cost, size and weight increase due to the bearing.

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

Abstract

La présente invention concerne un compresseur à spirale qui peut comprendre : un premier palier pour supporter en rotation un arbre de rotation sur un carter sur un côté d'un moteur; un deuxième palier pour supporter en rotation l'arbre de rotation sur le carter de l'autre côté du moteur; et un troisième palier pour supporter en rotation l'arbre de rotation sur une volute orbitale sur le côté opposé au premier palier par rapport au deuxième palier, la distance entre le centre du premier palier et le centre du troisième palier étant définie par une distance prédéfinie, la distance entre le centre du moteur et le centre du troisième palier étant définie par une distance plus longue que la distance entre le centre du moteur et le centre du premier palier, et la distance entre le centre du deuxième palier et le centre du moteur étant définie par une distance plus longue que la distance entre le centre du deuxième palier et le centre du troisième palier. Par conséquent, il est possible d'éviter que le deuxième palier qui est placé dans de mauvaises conditions de charge soit endommagé.
PCT/KR2018/001906 2017-02-15 2018-02-13 Compresseur à spirale WO2018151512A1 (fr)

Priority Applications (6)

Application Number Priority Date Filing Date Title
JP2019512978A JP6757465B2 (ja) 2017-02-15 2018-02-13 スクロール圧縮機
CN202110619068.8A CN113279958B (zh) 2017-02-15 2018-02-13 涡旋式压缩机
DE112018000087.7T DE112018000087B4 (de) 2017-02-15 2018-02-13 Scrollverdichter
US16/326,989 US11359627B2 (en) 2017-02-15 2018-02-13 Multi-bearing scroll compressor to enhance load management
CN201880003464.4A CN109690085B (zh) 2017-02-15 2018-02-13 涡旋式压缩机
US17/743,802 US20220268277A1 (en) 2017-02-15 2022-05-13 Multi-bearing scroll compressor to enhance load management

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
KR10-2017-0020530 2017-02-15
KR20170020530 2017-02-15
KR1020180016942A KR102273425B1 (ko) 2017-02-15 2018-02-12 스크롤 압축기
KR10-2018-0016942 2018-02-12

Related Child Applications (2)

Application Number Title Priority Date Filing Date
US16/326,989 A-371-Of-International US11359627B2 (en) 2017-02-15 2018-02-13 Multi-bearing scroll compressor to enhance load management
US17/743,802 Division US20220268277A1 (en) 2017-02-15 2022-05-13 Multi-bearing scroll compressor to enhance load management

Publications (1)

Publication Number Publication Date
WO2018151512A1 true WO2018151512A1 (fr) 2018-08-23

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PCT/KR2018/001906 WO2018151512A1 (fr) 2017-02-15 2018-02-13 Compresseur à spirale

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WO (1) WO2018151512A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20230113626A1 (en) * 2020-07-01 2023-04-13 Hanon Systems Scroll compressor for compressing a refrigerant and method for oil enrichment and distribution

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR20120042494A (ko) * 2010-10-25 2012-05-03 엘지전자 주식회사 밀폐형 압축기
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KR20140142046A (ko) * 2013-06-03 2014-12-11 엘지전자 주식회사 스크롤 압축기
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