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WO2019208951A1 - Compresseur à volute - Google Patents

Compresseur à volute Download PDF

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Publication number
WO2019208951A1
WO2019208951A1 PCT/KR2019/003889 KR2019003889W WO2019208951A1 WO 2019208951 A1 WO2019208951 A1 WO 2019208951A1 KR 2019003889 W KR2019003889 W KR 2019003889W WO 2019208951 A1 WO2019208951 A1 WO 2019208951A1
Authority
WO
WIPO (PCT)
Prior art keywords
shaft
scroll
bush
fixed
shaft member
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.)
Ceased
Application number
PCT/KR2019/003889
Other languages
English (en)
Korean (ko)
Inventor
최윤성
김진호
안성용
이재하
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
Publication of WO2019208951A1 publication Critical patent/WO2019208951A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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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
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • 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
    • F04C29/0042—Driving elements, brakes, couplings, transmissions specially adapted for pumps
    • F04C29/0078—Fixing rotors on shafts, e.g. by clamping together hub and shaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2230/00—Manufacture
    • F04C2230/60—Assembly methods
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/50—Bearings

Definitions

  • the present invention relates to a scroll compressor, and more particularly, to a double-sided scroll compressor in which a compression chamber is formed on both sides of the swing scroll.
  • the compressor is applied to a vapor compression refrigeration cycle (hereinafter, abbreviated as refrigeration cycle) such as a refrigerator or an air conditioner.
  • refrigeration cycle a vapor compression refrigeration cycle
  • the hermetic compressor has a form in which a driving unit generating power and a compression unit operated by the driving unit to compress the fluid are installed together in an inner space of the sealed casing.
  • the compressor may be classified into a reciprocating type, a rotary type, and a scroll type according to a method of compressing a refrigerant.
  • the scroll compressor is formed so as to continuously compress the refrigerant by forming two pairs of compression chambers, a suction chamber, an intermediate pressure chamber, and a discharge chamber, between the fixed scroll and the swing scroll.
  • the compression chamber of the double-sided scroll compressor is formed by two fixed scrolls facing each other and a pivoting scroll disposed between the two fixed scrolls.
  • the pivoting scroll receives a driving force from the rotational shaft, which is configured to penetrate the fixed scroll.
  • the rotating shaft which transmits a driving force to a revolving scroll is not comprised integrally, but is comprised by coupling of several components mutually. Therefore, in order to ensure assembly stability of the rotating shaft, the plurality of parts are formed with different diameters.
  • the rotating shaft thus formed does not transmit equal force to the two fixed scrolls, thereby causing a problem of deteriorating the reliability of the compressor.
  • the size of the bearing formed on one fixed scroll and the size of the bearing formed on the other fixed scroll are different.
  • One object of the present invention is to provide a scroll compressor having a rotating shaft of a swinging scroll that applies the same load to two fixed scrolls.
  • Another object of the present invention is to provide a scroll compressor having a rotating shaft formed of a structure capable of improving bearing reliability.
  • a scroll compressor includes a casing, a rotating shaft positioned inside the casing, a drive unit configured to rotate the rotating shaft, and first and second fixings positioned to be fixed to the casing. And a compression unit including a scroll and a pivoting scroll connected to the rotary shaft and having one side and the other side engaged with the first and second fixed scrolls to form first and second compression chambers, respectively. It is done.
  • the rotating shaft of the scroll compressor proposed in the present invention includes a shaft body and a bush formed to surround the shaft body, and the shaft body includes a first shaft member and a second shaft member having different diameters. Characterized in that.
  • the shaft body is formed by the combination of the first shaft member and the second shaft member, the second shaft member is one of the pivoting scroll and the first and second fixed scroll. It is characterized in that it is formed to penetrate.
  • the diameter of the portion of the second shaft member passing through the pivoting scroll corresponds to the diameter of the portion of the second shaft member passing through any one of the first and second fixed scrolls. It features.
  • the diameter of the first shaft member is formed larger than the diameter of the second shaft member, the first shaft member is to connect any one of the drive unit and the first and second fixed scroll. It is characterized by.
  • the bush is characterized in that it is formed to surround the second shaft member.
  • the bush comprises a first bush member formed to surround a portion of the second shaft member, and a second bush member formed to surround another portion of the second shaft member. do.
  • the central axis of the shaft body characterized in that spaced apart from the central axis of the bush by a predetermined distance.
  • the central axis of the second shaft member is spaced apart from the central axis of the first bush member in a first direction and in a second direction different from the central axis of the second bush member and the first direction. Characterized by being spaced apart.
  • the central axis of the second shaft member is located between the central axis of the first bush member and the central axis of the second bush member.
  • the first fixed scroll is located on a side farther from the drive unit than the second fixed scroll, the diameter of the portion of the shaft body penetrating the pivoting scroll is the first of the shaft body. 1 characterized in that it corresponds to the diameter of the portion penetrating the fixed scroll.
  • the rotation axis is sequentially passed through the second fixed scroll, the swing scroll and the first fixed scroll from the drive unit, coupled with the swing scroll, the driving force of the drive unit to the swing scroll It is characterized in that it is formed to deliver.
  • the portion of the rotating shaft is characterized in that it is formed to be eccentric from the centerline formed by the drive unit.
  • the scroll compressor according to the present invention has an advantage of improving the operational stability of the compressor by having a rotating shaft designed to apply the same load to two opposite fixed scrolls, respectively.
  • the diameter of the bearing disposed on each of the two fixed scroll can be formed to be the same, the effect of improving the reliability of the bearing is derived.
  • FIG. 1 is a longitudinal sectional view showing a typical scroll compressor.
  • Figure 2 is a longitudinal sectional view showing a typical scroll compressor.
  • FIG. 3 is a cross-sectional view showing the axis of rotation of FIG.
  • Figure 4 is a longitudinal sectional view showing a scroll compressor proposed in the present invention.
  • FIG. 5 is a cross-sectional view showing the axis of rotation of FIG.
  • FIG. 6 is an exploded perspective view illustrating the rotating shaft of FIG. 4.
  • FIG. 7 is a perspective view illustrating the rotating shaft of FIG. 4.
  • FIG. 8 is a conceptual diagram illustrating components constituting the rotation axis of FIG. 4.
  • FIG. 9 is a conceptual diagram illustrating a shaft body and a bush of a rotating shaft.
  • FIG. 10 is a conceptual diagram illustrating a shaft body and a bush of a rotating shaft.
  • FIG. 1 is a longitudinal sectional view showing a scroll compressor 100 according to an embodiment of the present invention.
  • the scroll compressor 100 described in this embodiment may be a component of a vapor compression refrigeration cycle using refrigerant as a working fluid.
  • the scroll compressor 100 of the present embodiment includes a casing 110, a rotation shaft 120, a drive unit 130, and a compression unit 104.
  • the casing 110 forms a sealed space S, and the sealed space S may be filled with a high-pressure refrigerant discharged from the compression unit 104.
  • the casing 110 may include a shell 111, an upper cap 112, and a lower cap 113.
  • the cylindrical shell 111 may be fixed to the suction pipe (SP) in which the refrigerant is sucked in and the discharge pipe (DP) in which the compressed refrigerant is discharged.
  • the suction pipe SP may be positioned to directly suck the refrigerant into the compression unit 104
  • the discharge pipe DP may be positioned to communicate with the sealed space S to discharge the compressed high pressure refrigerant.
  • the rotating shaft 120 may be located inside the casing 110 and may be rotatably supported by the first and second fixed scrolls 140x and 140y to be described later. That is, a bearing portion 121 may be formed between the first and second fixed scrolls 140x and 140y and the rotation shaft 120.
  • the upper side of the rotating shaft 120 may be connected to the driving unit 130, the lower side of the compression unit 104, the oil supply passage 122 may be formed so as to penetrate through the lower end of the rotating shaft 120.
  • the closed space S is a high pressure space
  • oil supply by differential pressure may be performed even if a separate pump is not formed at the lower end of the rotating shaft 120.
  • a balance weight 123 may be mounted on the rotation shaft 120 to compensate for an imbalance caused by the pivoting motion of the pivoting scroll 150 to be described later.
  • a pair of balance weights 123 may be positioned above and below the compression unit 104.
  • the drive unit 130 serves to supply a driving force for rotating the rotation shaft 120.
  • the drive unit 130 is rotated in the central space of the stator 131 is fixed to the inner wall surface of the casing 110 to form a space in the center, the winding coil 132 wound around the stator 131, the stator 131
  • the rotor 133 may be provided.
  • the rotation shaft 120 may be coupled to the center of the rotor 133 so that the rotation shaft 120 may be rotationally driven.
  • the compression unit 104 of the scroll compressor 100 may be configured in a double-sided scroll method.
  • the compression unit 104 may include first and second fixed scrolls 140x and 140y and a pivoting scroll 150.
  • Each of the first and second fixed scrolls 140x and 140y has a disc-shaped fixed side plate portion 141 and is formed to protrude from opposite surfaces of the fixed side plate portion 141. Each may be further provided.
  • the first fixed scroll 140x is positioned near the lower side of the sealed space S in which the oil is stored, and the second fixed scroll 140y is coupled to the upper portion of the first fixed scroll 140x. Can be.
  • first and second fixed scrolls 140x and 140y may have fixed sidewall portions 143 that are supported and fixed to the inner circumferential surface of the shell 111, respectively.
  • the suction pipe SP may be disposed to communicate with the suction hole 144 formed to penetrate the fixed side wall portion 143 of the first fixed scroll 140x.
  • the pivoting scroll 150 may be positioned between the first fixed scroll 140x and the second fixed scroll 140y.
  • the swing scroll 150 protrudes from both sides of the swing side hard plate portion 151 and the swing side hard plate portion 151 (lower side and upper side in Fig. 1), respectively, to form first and second fixed scrolls.
  • a pair of pivoting wraps 152 formed to engage the fixed wraps 142 of 140x and 140y may be provided.
  • the swinging scroll 150 is eccentrically connected to the rotating shaft 120 and is made to swing.
  • An old dam ring (not shown) may be mounted between the first or second fixed scrolls 140x and 140y and the swing scroll 150 to implement the swing movement of the swing scroll 150.
  • the rotary shaft 120 may include an eccentric portion 124 formed to protrude from its outer circumferential surface so that the pivoting scroll 150 may be eccentrically coupled to the rotary shaft 120.
  • the space formed by the first and second fixed scrolls 140x and 140y and the orbiting scroll 150 may be the first and second compression chambers Px and Py that compress the refrigerant while the volume changes.
  • Each of the first and second compression chambers Px and Py may include a suction chamber, an intermediate pressure chamber, and a discharge chamber that are sequentially formed so that the refrigerant moves with increasing pressure in accordance with the swinging movement of the swinging scroll 150.
  • the suction chamber, the intermediate pressure chamber, and the discharge chamber may be sequentially located from the outside to the center in the radial direction of the rotation shaft 120.
  • the refrigerant may be compressed in two stages by the first compression chamber Px and the second compression chamber Py. That is, the refrigerant is compressed from the suction chamber of the first compression chamber Px adjacent to the suction hole 144 through which the suction pipe SP passes through the intermediate pressure chamber and the discharge chamber of the first compression chamber Px.
  • the refrigerant compressed in the compression chamber Px may be moved to the suction chamber of the second compression chamber Py.
  • the moved refrigerant is compressed through the suction chamber, the intermediate pressure chamber and the discharge chamber of the second compression chamber Py, and passes through the discharge hole 145 penetrating the fixed side plate portion 141 of the second fixed scroll 140y. It can be discharged to the closed space (S).
  • the discharge chamber of the first compression chamber Px and the suction chamber of the second compression chamber Py may communicate with each other by a connection flow path formed to pass through the first and second fixed scrolls 140x and 140y.
  • the pivoting scroll 150 is pivoted between the first and second fixed scrolls 140x and 140y, and the first and second compression chambers Px and Py are outward ( It moves from the suction chamber to the inside (discharge chamber) and repeats the process of decreasing the volume.
  • the refrigerant is sucked into the first compression chamber Px through the suction pipe SP and the suction hole 144 and compressed (first stage). Compression process), the refrigerant discharged from the first compression chamber (Px) is sucked into the second compression chamber (Py) through the connection flow path and compressed (two-stage compression process).
  • the refrigerant compressed in the second compression chamber Py may be discharged into the closed space S through the discharge hole 145, and the refrigerant may be separated from the oil while remaining in the discharge space and discharged into the discharge pipe DP. .
  • oil is accumulated on the bottom surface of the sealed space S, and the accumulated oil is supplied to the first and second compression chambers Px and Py along the oil supply passage 122 by the pressure of the sealed space S. To perform lubrication and cooling.
  • the medium pressure refrigerant passing through the condenser may be bypassed and injected (injected) into the first and second compression chambers Px and Py.
  • the configuration and features of the injection flow path will be described.
  • the scroll compressor 100 of the present embodiment is configured to bypass the refrigerant discharged into the discharge pipe DP and passed through the condenser to the first and second compression chambers Px and Py, respectively. 2 injection flow paths (160, 180).
  • first and second injection flow paths 160 and 180 are formed to penetrate the first and second fixed scrolls 140x and 140y, respectively.
  • the first and second injection flow paths 160 and 180 may be formed of a pipe passing through the shell 111 and a hole penetrating through the fixed side plate part 141 to communicate with the pipe.
  • the scroll compressor 100 may be configured such that the first and second injection passages 160 and 180 which bypass the refrigerant to the first and second compression chambers Px and Py are controlled independently of each other. have. That is, the first and second injection passages 160 and 180 may be controlled to supply refrigerants having different pressures to the first and second compression chambers Px and Py at different times.
  • the refrigerant discharged from the condenser may be sequentially used.
  • the refrigerant passing through the condenser may be bypassed to be first injected into the second compression chamber Py, and the refrigerant having a lower pressure may be bypassed to be injected again into the first compression chamber Px. That is, when the first and second compression chambers Px and Py perform two-stage compression, a refrigerant having a suitable pressure may be supplied to each compression chamber.
  • the refrigerant since the first and second injection passages 160 and 180 operate independently of each other, the refrigerant may be injected into the first and second compression chambers Px and Py at various pressure combinations.
  • the driving mode can be implemented.
  • FIG. 2 shows the configuration of a rotating shaft of a general scroll compressor in more detail.
  • the rotating shaft 120 of the scroll compressor shown in FIG. 2 is formed by the combination of three different shaft body members 120a, 120b, 120c.
  • the rotating shaft 120 is formed so as to sequentially pass through the second fixed scroll 140y, the turning scroll 150, and the first fixed scroll 140x from the driving unit, and the second fixed scroll 140y and the turning scroll 150. And through-holes formed in the first fixed scroll 140x, respectively, a plurality of bushes 200a, 200b, 200c surrounding the shaft body of the rotating shaft 120, and bearings disposed around the bushes.
  • the rotary shaft 120 is configured by the combination of different shaft body members so that the rotary shaft 120 passes through the second fixed scroll 140y, the pivoting scroll 150, and the first fixed scroll 140x. .
  • the diameters of the shaft body members to be joined must be designed to different values.
  • the diameter A of the first shaft body member 120a penetrating the second fixed scroll 140y and the second shaft body member 120b penetrating the pivoting scroll 150 are shown.
  • the diameter B and the diameter C of the third shaft body member penetrating the first fixed scroll 140x are different from each other.
  • FIG. 3 a cross section of a second shaft body member 120b and a bush 200b surrounding the second shaft body member 120b is shown.
  • the cross section of the second shaft body member 120b and the bush 200b surrounding the second shaft body member 120b is formed in a circular shape, and a central axis of the second shaft body member 120b is provided.
  • the central axes of the bushes 200b surrounding the second shaft body member 120b coincide with each other. That is, the distance from the outer surface of the second shaft body member 120b to the outer surface of the bush 200b maintains a substantially uniform spacing.
  • FIG. 4 illustrates a longitudinal section of the scroll compressor proposed in the present invention.
  • the rotating shaft 401 of the scroll compressor proposed in the present invention includes shaft bodies 401a and 401b and bushes 200b and 200c formed to surround the shaft body.
  • the shaft body may include a first shaft member 401a and a second shaft member 401b formed to have different diameters.
  • the rotation shaft 401 of the present invention may sequentially pass through the second fixed scroll, the turning scroll, and the first fixed scroll from the driving unit.
  • the rotating shaft 401 may be coupled to the swing scroll 150 and may be formed to transmit a driving force of the driving unit to the swing scroll.
  • part of the rotating shaft 401 may be formed to be eccentric from the central axis formed by the drive unit.
  • the rotating shaft 401 is formed by coupling a plurality of components, any one component and the other of the plurality of components may be formed with different diameters.
  • the rotating shaft 401 is coupled to the combination of the first portion 401a formed with the first diameter A and the second portion 401b formed with the second diameter B smaller than the first diameter A.
  • FIG. It can be formed by.
  • the shaft body 401 may be formed by combining the first shaft member 401a and the second shaft member 401b.
  • the second shaft member is formed to penetrate the pivoting scroll 150 and at least one of the first and second fixed scrolls 140x and 140y.
  • FIG. 4 an embodiment in which the second shaft member 401b penetrates the pivoting scroll 150 and the second fixed scroll 140y is illustrated, but the present invention is not limited thereto.
  • the diameter of the portion 411b penetrating the pivoting scroll 150 of the second shaft member 401b is the portion 421b penetrating at least one of the first and second fixed scrolls of the second shaft member. It can correspond to the diameter of.
  • the diameter A of the first shaft member 401a may be formed differently from the diameter B of the second shaft member 401b. This is because different diameters of different members can be easily combined.
  • the diameter A of the first shaft member 401a may be larger than the second shaft member 401b. Since the first shaft member 401a is closer to the drive unit side than the second shaft member 401b, it is advantageous in terms of stability of the scroll compressor that the diameter of the first shaft member is thicker.
  • the first shaft member 401a is coupled to the rotor of the driving unit by shrinking and connects the driving unit to any one of the first and second fixed scrolls.
  • the bushes 400b and 400c may be formed to surround the second shaft member 401b.
  • the bush may include a first bush member 400b formed to surround a portion of the second shaft member 401b and a second bush member 400c formed to surround another portion of the second shaft member 401b. Can be.
  • the central axis of the shaft body may be spaced apart from the central axis of the bush 400b by a predetermined distance.
  • the central axis of the second shaft member 401b forming the shaft body may be spaced apart from the central axis of the bush 400b by a predetermined distance.
  • the bush 400b according to the present invention may be formed to be eccentric with respect to the shaft body.
  • the shaft body may be disposed in an eccentric position.
  • the central axis of the second shaft member 401b may be spaced apart from the central axis of the first bush member 400b in the first direction.
  • the central axis of the second shaft member 401b may be spaced apart from the central axis of the second bush member 400c in a second direction different from the first direction.
  • the first bush member 400b may be formed to be eccentrically to the right, and the second bush member 400c may be formed to be eccentrically to the left.
  • the central axis of the second shaft member 401b may be located between the central axis of the first bush member 400b and the central axis of the second bush member 400c.
  • the diameter A of the first shaft member 401a may correspond to the diameter of the second bush member 400c surrounding the second shaft member 401b.
  • the bearing 210a disposed in the through hole of the first fixed scroll 140x and the bearing 210c disposed in the through hole of the second fixed scroll 140y may have the same standard.
  • first bush member 400b and the second bush member 400c may be formed to have diameters corresponding to each other.
  • the diameter of the bearing disposed on each of the two fixed scroll can be formed to be the same, the effect of improving the reliability of the bearing is derived.
  • FIG. 6 is an exploded perspective view of the bushes 400b and 400c and the shaft body.
  • first bush member 400b and the second bush member 400c may be formed as separate parts from each other, and may be coupled to each other.
  • first bush member 400b and the second bush member 400c may be formed as an integral member.
  • FIG. 7 the appearance of the rotating shaft 401 to which the bushes 400b and 400c and the shaft body are coupled is shown.
  • FIG. 8 shows a longitudinal section of a rotating shaft 401 in which bushes 400b and 400c and a shaft body are coupled.
  • one end close to the driving unit and one end opposite to the driving unit among the both ends of the rotating shaft 401 according to the present invention may have the same diameter.
  • the central axes respectively formed at both ends of the rotation shaft 401 may correspond to each other.
  • a portion of the rotation shaft 401 may be eccentric with respect to the central axis respectively formed at both ends of the rotation shaft 401.
  • the portion may be a portion of the rotating shaft 401 penetrating the pivoting scroll 150.
  • a plurality of central axes formed by the first shaft body member 401a, the second shaft body member 401b, and the first bush member 400b and the second bush member 400c are formed.
  • a conceptual diagram is shown that represents spaced distances or eccentric directions.
  • the first center axis 901 of the bearing disposed on the swinging scroll, the second center axis 902 of the second shaft body member 401b, and the third center of the bearing disposed on the fixed scroll An imaginary line is shown, each representing axis 903.
  • the turning radius x of the rotation axis 401 is determined by the distance between the first central axis 901 and the third central axis 903.
  • the inner diameter a of the bearing disposed in the fixed scroll corresponds to the outer diameter of a portion of the rotating shaft 401 that passes through the fixed scroll.
  • the diameter of the second shaft body member 401b may be determined to be smaller than the difference between the inner diameter a of the bearing disposed on the fixed scroll and the turning radius x.
  • the user may consider the inner diameter a of the bearing disposed on the fixed scroll and the turning radius x.
  • FIG. 10 a conceptual diagram relating to the design of the first bush member 400b is shown.
  • the central axis of the first bush member 400 and the central axis of the second shaft body member 401b are determined. You can determine the distance between them.

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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 concerne un compresseur à volute qui comprend : un boîtier ; un arbre de rotation positionné à l'intérieur du boîtier ; une unité d'entraînement conçue pour faire tourner l'arbre de rotation ; et une unité de compression comprenant une première et une seconde volute de fixation positionnées de façon à être fixées au boîtier et une volute pivotante reliée à l'arbre de rotation de façon à se déplacer de manière pivotante et ayant un côté et l'autre côté en prise avec la première et la seconde volute de fixation, respectivement, pour former une première et une seconde chambre de compression, l'arbre de rotation comprenant un corps d'arbre et une bague formée pour entourer le corps d'arbre, et le corps d'arbre comprenant un premier élément d'arbre et un second élément d'arbre formés pour avoir des diamètres différents.
PCT/KR2019/003889 2018-04-26 2019-04-02 Compresseur à volute Ceased WO2019208951A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
KR1020180048689A KR102060472B1 (ko) 2018-04-26 2018-04-26 스크롤 압축기
KR10-2018-0048689 2018-04-26

Publications (1)

Publication Number Publication Date
WO2019208951A1 true WO2019208951A1 (fr) 2019-10-31

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Application Number Title Priority Date Filing Date
PCT/KR2019/003889 Ceased WO2019208951A1 (fr) 2018-04-26 2019-04-02 Compresseur à volute

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KR (1) KR102060472B1 (fr)
WO (1) WO2019208951A1 (fr)

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH07286586A (ja) * 1994-04-20 1995-10-31 Daikin Ind Ltd スクロール型流体装置
JPH08170592A (ja) * 1994-12-16 1996-07-02 Hitachi Ltd 軸貫通二段スクロール圧縮機
JPH10103260A (ja) * 1996-09-20 1998-04-21 Asuka Japan:Kk スクロール流体機械
JPH10110690A (ja) * 1996-08-09 1998-04-28 Hitachi Ltd スクロール形流体機械
JP2007162571A (ja) * 2005-12-14 2007-06-28 Mitsubishi Electric Corp スクロール圧縮機

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH07286586A (ja) * 1994-04-20 1995-10-31 Daikin Ind Ltd スクロール型流体装置
JPH08170592A (ja) * 1994-12-16 1996-07-02 Hitachi Ltd 軸貫通二段スクロール圧縮機
JPH10110690A (ja) * 1996-08-09 1998-04-28 Hitachi Ltd スクロール形流体機械
JPH10103260A (ja) * 1996-09-20 1998-04-21 Asuka Japan:Kk スクロール流体機械
JP2007162571A (ja) * 2005-12-14 2007-06-28 Mitsubishi Electric Corp スクロール圧縮機

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