WO2022123657A1 - Compresseur à spirales et dispositif à cycle frigorifique - Google Patents

Compresseur à spirales et dispositif à cycle frigorifique Download PDF

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Publication number
WO2022123657A1
WO2022123657A1 PCT/JP2020/045715 JP2020045715W WO2022123657A1 WO 2022123657 A1 WO2022123657 A1 WO 2022123657A1 JP 2020045715 W JP2020045715 W JP 2020045715W WO 2022123657 A1 WO2022123657 A1 WO 2022123657A1
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WO
WIPO (PCT)
Prior art keywords
scroll compressor
chamber
end side
flange portion
peripheral surface
Prior art date
Application number
PCT/JP2020/045715
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English (en)
Japanese (ja)
Inventor
遼太 飯島
和行 松永
Original Assignee
日立ジョンソンコントロールズ空調株式会社
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 日立ジョンソンコントロールズ空調株式会社 filed Critical 日立ジョンソンコントロールズ空調株式会社
Priority to CN202080107367.7A priority Critical patent/CN116457578A/zh
Priority to JP2022567924A priority patent/JP7398577B2/ja
Priority to PCT/JP2020/045715 priority patent/WO2022123657A1/fr
Publication of WO2022123657A1 publication Critical patent/WO2022123657A1/fr

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    • 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 or the like.
  • Patent Document 1 describes that "the peripheral end of the auxiliary bearing is sandwiched and fixed between the main case and the side case constituting the sealed case". ing.
  • the scroll compressor according to the present invention has a first frame provided with a first bearing that pivotally supports a drive shaft on one end side of the motor, and the scroll compressor on the other end side of the motor.
  • a second frame provided with a second bearing that supports the drive shaft, the second frame has a flange portion at least a part of the peripheral portion thereof, and the other end portion of the tubular chamber. The vicinity and the vicinity of the edge of the bottom chamber are fixed so as to sandwich the flange portion, and a side groove recessed inward in the radial direction is provided on the side surface of the flange portion in the circumferential direction. And said.
  • FIG. 1 It is a vertical sectional view of the scroll compressor which concerns on 1st Embodiment.
  • the scroll compressor according to the first embodiment it is a cross-sectional view of the scroll compressor in line II-II of FIG.
  • It is a perspective view of the lower frame provided in the scroll compressor which concerns on 1st Embodiment.
  • FIG. 1 is a vertical sectional view of the scroll compressor 100 according to the first embodiment.
  • the scroll compressor 100 shown in FIG. 1 is a device that compresses a gaseous refrigerant.
  • the scroll compressor 100 includes a closed container 1, a compression mechanism unit 2, a crank shaft 3 (drive shaft), an electric motor 4, an old dam ring 5, balance weights 61, 62, and a lower portion.
  • a frame 7 (second frame) and a refueling pump 8 are provided.
  • the closed container 1 is a metal container that houses the compression mechanism portion 2, the crank shaft 3, the electric motor 4, the lower frame 7, and the like, and is substantially sealed. Lubricating oil for improving lubricity is sealed in the closed container 1, and is stored as an oil sump R1 at the bottom of the closed container 1.
  • the closed container 1 includes a cylindrical cylinder chamber 11 (also referred to as a case), a lid chamber 12 that closes the upper side (one end side) of the cylinder chamber 11, and a bottom chamber that closes the lower side (the other end side) of the cylinder chamber 11. 13 and.
  • a step portion 11a is provided on the inner peripheral surface near the upper end of the cylinder chamber 11.
  • the step portion 11a is a portion to which the upper frame side flange portion 23a, which will be described later, is locked, and is formed by cutting or the like.
  • the step portion 11a is formed from the upper end of the cylinder chamber 11 to a predetermined depth so as to increase the inner diameter of the cylinder chamber 11.
  • the lid chamber 12 has an inverted U shape in a vertical cross-sectional view, and is fixed to the inside near the upper end of the tubular chamber 11.
  • the bottom chamber 13 is fixed to the outside near the lower end of the tubular chamber 11.
  • the bottom chamber 13 includes a bottom portion 13a having a U-shape in a vertical cross-sectional view, a large diameter portion 13b, and a diameter expansion portion 13c.
  • the large diameter portion 13b is a cylindrical portion provided on the upper side (one end side) of the bottom portion 13a, and has a larger inner diameter and outer diameter than the bottom portion 13a.
  • the diameter-expanded portion 13c is an annular portion connecting the bottom portion 13a and the large-diameter portion 13b so as to expand the diameter from the bottom portion 13a to the large-diameter portion 13b.
  • the bottom portion 13a, the large diameter portion 13b, and the enlarged diameter portion 13c are integrally formed. Further, the outer peripheral surface near the lower end of the tubular chamber 11 and the inner peripheral surface near the upper end of the large diameter portion 13b are in contact with each other. Then, in the welded portion W1 shown in FIG. 1, the upper end of the large diameter portion 13b is welded (welded) to the outer peripheral surface of the cylinder chamber 11.
  • the suction pipe P1 is fixed to the lid chamber 12 of the closed container 1 in a state of being inserted.
  • the suction pipe P1 is a pipe that guides the refrigerant to the suction chamber H1 of the compression mechanism unit 2.
  • the discharge pipe P2 is fixed to the cylinder chamber 11 of the closed container 1 in a state of being inserted.
  • the discharge pipe P2 is a pipe that guides the refrigerant compressed by the compression mechanism unit 2 to the outside of the scroll compressor 100.
  • the compression mechanism unit 2 is a mechanism that compresses the refrigerant as the crank shaft 3 rotates.
  • the compression mechanism unit 2 includes a fixed scroll 21, a swivel scroll 22, and an upper frame 23 (first frame), and is arranged in an upper space inside the closed container 1.
  • the fixed scroll 21 includes a base plate 21a and a spiral fixed wrap 21b.
  • the base plate 21a includes a thick main body portion 211a having a circular shape in a plan view, and a fixed scroll side flange portion 211b protruding radially outward from the lower portion of the main body portion 211a.
  • the vicinity of the center of the lower surface of the main body portion 211a is recessed upward in a predetermined manner.
  • the fixed wrap 21b has a spiral shape (see also FIG. 2) and extends downward from the base plate 21a in the above-mentioned region.
  • the lower surface of the base plate 21a and the lower end of the fixed wrap 21b are substantially flush with each other.
  • the swivel scroll 22 is a member that swivels with the drive of the electric motor 4 to form a compression chamber C1 (see FIG. 2) together with the fixed scroll 21.
  • the swivel scroll 22 includes a disc-shaped end plate 22a, a swivel lap 22b erected on the end plate 22a, and a boss portion 22c fitted to the upper end portion of the crank shaft 3. As shown in FIG. 1, the swivel lap 22b extends above the end plate 22a, while the boss portion 22c extends below the end plate 22a.
  • FIG. 2 is a cross-sectional view of the scroll compressor 100 in line II-II of FIG.
  • the swirl lap 22b shown in FIG. 2 is a member that forms the compression chamber C1 together with the fixed lap 21b, and has a spiral shape. Then, the spiral fixed lap 21b and the spiral swirling lap 22b mesh with each other to form a compression chamber C1 between the fixed lap 21b and the swirling lap 22b.
  • the compression chamber C1 is a space for compressing the gaseous refrigerant, and is formed on the outer line side and the inner line side of the swirl lap 22b, respectively.
  • a discharge port V1 for guiding the refrigerant compressed in the compression chamber C1 to the space above the compression mechanism unit 2 is provided.
  • the upper frame 23 shown in FIG. 1 is a metal member that supports the fixed scroll 21, and is fixed to the closed container 1.
  • the upper frame 23 has a substantially rotationally symmetric shape and is provided under the fixed scroll 21.
  • the upper frame 23 is provided with a hole (not shown) through which the crank shaft 3 is inserted.
  • the upper frame 23 is provided with an upper frame side flange portion 23a on its peripheral edge portion.
  • the upper frame side flange portion 23a is a portion that abuts on the lower surface of the fixed scroll side flange portion 211b.
  • the flange portion 23a on the upper frame side is locked to the step portion 11a of the cylinder chamber 11, and the swivel scroll 22 and the fixed scroll 21 are housed in the closed container 1 and then the lid chamber. 12 is installed. In this state, the peripheral end surface of the lid chamber 12 comes into contact with the upper surface of the fixed scroll side flange portion 211b.
  • crank shaft 3 (drive shaft) shown in FIG. 1 is a shaft that rotates integrally with the rotor 4b of the motor 4, and extends in the vertical direction. As shown in FIG. 1, the crank shaft 3 includes a main shaft 3a and an eccentric portion 3b extending upward from the main shaft 3a.
  • the spindle 3a is coaxially fixed to the rotor 4b of the motor 4, and rotates integrally with the rotor 4b.
  • the eccentric portion 3b is an axis that rotates while being eccentric with respect to the main shaft 3a, and is fitted to the boss portion 22c of the swivel scroll 22. Then, the eccentric portion 3b rotates while being eccentric, so that the swivel scroll 22 turns in a predetermined manner.
  • the main bearing 9 rotatably supports the upper part of the crank shaft 3 and is fixed to the peripheral wall surface of the hole (reference numeral is not shown) of the upper frame 23. That is, the upper frame 23 (first frame) is provided with a main bearing 9 (first bearing) that pivotally supports the crank shaft 3 (drive shaft) on the upper side (one end side) of the motor 4.
  • the swivel bearing 10 rotatably supports the eccentric portion 3b with respect to the boss portion 22c of the swivel scroll 22, and is fixed to the inner peripheral wall of the boss portion 22c.
  • a slide bearing is used as the main bearing 9 and the swivel bearing 10.
  • an oil supply passage 3c for guiding the lubricating oil to a predetermined value is provided inside the crank shaft 3. The lubricating oil flowing through the oil supply passage 3c is guided to the compression mechanism portion 2 and each bearing.
  • the motor 4 is a drive source for rotating the crank shaft 3 and is housed in the closed container 1. Specifically, the electric motor 4 is installed between the compression mechanism portion 2 and the lower frame 7 in the vertical direction. As shown in FIG. 1, the electric motor 4 includes a stator 4a and a rotor 4b. The stator 4a is fixed to the inner peripheral wall of the cylinder chamber 11. The rotor 4b is rotatably arranged inside the stator 4a in the radial direction. Then, by energizing the winding 41a of the stator 4a, the rotor 4b rotates integrally with the crank shaft 3.
  • the old dam ring 5 is a ring-shaped member that receives the eccentric rotation of the eccentric portion 3b and revolves the swivel scroll 22 without rotating. As shown in FIG. 1, the old dam ring 5 is provided between the swivel scroll 22 and the upper frame 23. The old dam ring 5 is mounted in a groove (not shown) provided on the lower surface of the swivel scroll 22, and is also mounted in another groove (not shown) provided in the upper frame 23.
  • the balance weights 61 and 62 are members for suppressing the vibration of the scroll compressor 100.
  • the balance weight 61 is installed between the upper frame 23 and the electric motor 4 on the crank shaft 3.
  • the other balance weight 62 is installed on the lower surface of the rotor 4b.
  • the lower frame 7 (second frame) is a metal member that rotatably supports the lower part of the crank shaft 3, and is fixed in a state of being sandwiched between the cylinder chamber 11 and the bottom chamber 13. The details of the lower frame 7 will be described later.
  • the refueling pump 8 is a non-volumetric pump that pumps lubricating oil, and is installed at the lower part of the refueling passage 3c.
  • the refueling pump 8 includes a thin plate-shaped metal piece (not shown) twisted in a predetermined manner. Then, the lubricating oil rises through the oil supply passage 3c due to the rotation of the metal piece accompanying the drive of the electric motor 4.
  • the swivel scroll 22 When the swivel scroll 22 is swiveled by the drive of the electric motor 4, the volume of the compression chambers C1 formed one after another is reduced accordingly, and the gaseous refrigerant is compressed.
  • the compressed refrigerant is discharged into the upper space in the closed container 1 through the discharge port V1 of the fixed scroll 21, and is further guided to the lower side of the compression mechanism unit 2.
  • the refrigerant guided to the lower side of the compression mechanism portion 2 is guided to a condenser (not shown) via a discharge pipe P2 or the like, and circulates in a predetermined refrigeration cycle.
  • FIG. 3 is a perspective view of the lower frame 7 included in the scroll compressor. Note that FIG. 3 shows a cross section of the lower frame 7 that is plane-symmetrical with respect to a predetermined cut surface. As shown in FIG. 3, the lower frame 7 includes an annular portion 72, a flange portion 73, and a connecting portion 74 in addition to the cylindrical base portion 71.
  • the base portion 71 is a portion where an auxiliary bearing 71a is provided on the inner peripheral surface thereof, and has a cylindrical shape.
  • the auxiliary bearing 71a is a bearing that supports the lower portion of the crank shaft 3 and receives a radial load from the crank shaft 3. That is, the lower frame 7 (second frame) is provided with an auxiliary bearing 71a (second bearing) that pivotally supports the crank shaft 3 (drive shaft) on the lower side (the other end side) of the motor 4.
  • auxiliary bearing 71a for example, a slide bearing is used.
  • the inner peripheral surface of the base 71 may be subjected to a predetermined polishing process or surface treatment to form a slide bearing (that is, an auxiliary bearing 71a). Further, a cylindrical slide bearing (that is, an auxiliary bearing 71a) may be fixed to the inner peripheral surface of the base 71.
  • the annular portion 72 has an annular shape and is arranged so as to surround the base 71.
  • a predetermined press-fitting portion 72a is provided on the outer peripheral surface of the annular portion 72 over the entire circumference of the annular portion 72.
  • the press-fitting portion 72a is a portion where a part of the outer peripheral surface of the annular portion 72 protrudes outward in the radial direction, and is provided on the upper side of the flange portion 73.
  • the outer diameter of the press-fitting portion 72a is slightly larger than the inner diameter near the lower end of the tubular chamber 11.
  • the flange portion 73 shown in FIG. 3 is a portion sandwiched between the lower end of the tubular chamber 11 (see FIG. 1) and the enlarged diameter portion 13c of the bottom chamber 13 (see FIG. 1), and has a diameter from the annular portion 72. It protrudes outward in the direction.
  • the flange portion 73 is provided on the peripheral edge portion K1 of the lower frame 7, and is integrally formed with the annular portion 72. In the example of FIG. 3, the lower surface of the flange portion 73 and the lower surface of the annular portion 72 are flush with each other.
  • a side surface groove 73a recessed inward in the radial direction is provided in the circumferential direction.
  • a side groove 73a is provided over the entire circumference of the side surface of the flange portion 73.
  • the action / effect of providing the side groove 73a will be described later.
  • the connecting portion 74 is a portion connecting the base portion 71 and the annular portion 72, and extends in the radial direction.
  • three connecting portions 74 are provided at equal intervals (at intervals of 120 °) in the circumferential direction with respect to the central axis of the crank shaft 3.
  • FIG. 4 is a partially enlarged view of the region G1 of FIG.
  • the vicinity of the lower end (the other end side) of the tubular chamber 11 and the vicinity of the edge of the bottom chamber 13 are fixed with the flange portion 73 sandwiched between them. That is, the lower frame 7 including the flange portion 73 is fixed by the cylinder chamber 11 and the bottom chamber 13 by the press-fit method of the covering specification.
  • the side groove 73a is provided in the flange portion 73. Prior to the technical significance (action / effect) of providing the side groove 73a, first, the problem when the side groove 73a is not provided in the flange portion 73 will be briefly described.
  • the holding force of the flange portion 73 by increasing the press load when the flange portion 73 is sandwiched in the vertical direction by the cylinder chamber 11 and the bottom chamber 13.
  • the press load during assembly is too large, the contact stress of parts such as the flange portion 73 exceeds the yield point, and the parts are plastically deformed, resulting in a decrease in assembly accuracy and a decrease in the holding force of the flange portion 73. May invite. Therefore, in the first embodiment, the amount of decrease in the holding force of the flange portion 73 when the press load is released is reduced, and the amount of decrease in the holding force of the flange portion 73 when the internal pressure is applied to the closed container 1 is reduced.
  • the flange portion 73 is provided with a side groove 73a.
  • the lower end (the other end side) of the cylinder chamber 11 and the enlarged diameter portion 13c are fixed with the flange portion 73 sandwiched between them. Further, the outer peripheral surface on the lower side (the other end side) of the cylinder chamber 11 and the inner peripheral surface on the upper side (one end side) of the large diameter portion 13b are in contact with each other. The side surface of the flange portion 73 and the inner peripheral surface of the large diameter portion 13b may be in contact with each other, or a predetermined gap may be provided.
  • the radial depth of the side groove 73a (the distance from the broken line A11 to the broken line A14) is the point M1 (from the broken line A11 to the broken line A12) where the enlarged diameter portion 13c is in contact with the flange portion 73. Is deeper than the inner edge (dashed line A12). Further, the radial depth of the side groove 73a (distance from the broken line A11 to the broken line A14) is deeper than the inner peripheral surface (broken line A13) on the lower end side of the tubular chamber 11.
  • the bottom of the side groove 73a is deeper in the radial direction than the inner edge of the portion M1 where the enlarged diameter portion 13c is in contact with the flange portion 73, and further, inside the lower side (the other end side) of the cylinder chamber 11. It is deeper in the radial direction than the peripheral surface.
  • FIGS. 5 to 8 will be sequentially used to explain the load acting on each component and the like.
  • the portion where the flange portion 73 is sandwiched by the cylinder chamber 11 and the bottom chamber 13 is referred to as a sandwiching portion S1 (see FIG. 4).
  • FIG. 5 is an explanatory view of spring models MD1 and MD2 in the vicinity of the sandwiching portion S1 before the cylinder chamber 11 and the bottom chamber 13 are welded.
  • the sandwiching portion S1 and the components around it are replaced with two parallel spring models MD1 and MD2 (elastic deformation models).
  • MD1 and MD2 elastic deformation models
  • one of the spring models MD1 shows elastic deformation of the bottom chamber 13.
  • the other spring model MD2 shows the elastic deformation when the cylinder chamber 11 and the flange portion 73 are combined as one spring.
  • the two spring models MD1 and MD2 are assumed to be deformed one-dimensionally in the vertical direction.
  • both of the two spring models MD1 and MD2 are located at the enlarged diameter portion 13c of the bottom chamber 13. Further, in FIG. 5, since the cylinder chamber 11 and the bottom chamber 13 are in the state before welding, the upper ends of the two spring models MD1 and MD2 are not connected (see reference numeral 30).
  • FIG. 6 is an explanatory diagram showing a load and the like acting on the sandwiching portion S1 in a state where the press load P is applied before welding the cylinder chamber 11 and the bottom chamber 13. Prior to welding the cylinder chamber 11 and the bottom chamber 13, a downward press load P is applied to the cylinder chamber 11 via the lid chamber 12 (see FIG. 1). In this state, since the cylinder chamber 11 and the bottom chamber 13 have not been welded yet, they are independent as two spring models MD1 and MD2 (see reference numeral 30).
  • the spring model MD1 showing elastic deformation of the bottom chamber 13 is in a state of natural length.
  • the spring model MD2 showing the elastic deformation of the cylinder chamber 11 and the flange portion 73 is in a state of being compressed by the press load P (> 0). Therefore, in the spring model MD2, a compressive load Fp as a reaction force (elastic force) with respect to the press load P is generated as an upward force to expand. Then, the press load P and the compression load Fp are in balance and stand still.
  • the force (holding force) for holding the lower frame 7 in the closed container 1 acts on the vertical holding force of the flange portion 73 (a force whose magnitude is equal to the compression load Fp) and the press-fitting portion 72a. Includes radial forces and. Then, in a state where the press load P is applied to the cylinder chamber 11, the cylinder chamber 11 and the bottom chamber 13 are welded, and the press load P is further released.
  • FIG. 7 is an explanatory view showing a load and the like acting on the sandwiching portion S1 in a state where the press load is released after welding the cylinder chamber 11 and the bottom chamber 13.
  • a predetermined welded portion W1 is formed so as to weld the upper end of the bottom chamber 13 and the side surface of the tubular chamber 11.
  • the upper ends of the two spring models MD1 and MD2 are connected to form one spring model MD3.
  • the spring model MD2 expands in the vertical direction by the displacement ⁇ x1.
  • the two spring models MD1 and MD2 are connected as one spring model MD3 (see FIG. 7), the other spring model MD1 (see FIG. 6) also extends by the displacement ⁇ x1.
  • a tensile load Fc that tries to shrink to the original length is generated in the spring model MD1 which was originally a natural length.
  • the magnitude of the force acting on the two spring models MD1 and MD2 is balanced between the tensile load Fc and the compressed load Ff after the decrease due to the extension of the displacement ⁇ x1. Then, the following equations (1) to (3) are obtained.
  • kc included in the equation (1) is the rigidity coefficient of the spring model MD1 (see FIG. 6).
  • kf included in the equation (2) is a rigidity coefficient of the spring model MD2 (see FIG. 6). Based on the above-mentioned equation (1), the following equation (4) is obtained.
  • the following is clarified as the action at the time of assembling the scroll compressor 100. That is, by providing the side groove 73a in the flange portion 73 to reduce the rigidity of the spring model MD2 (see FIG. 6) (that is, to reduce the rigidity coefficient kf), the press load P which is the same value as the compression load Fp is applied. Even when applied, the compressive load Ff (that is, the narrowing force of the lower frame 7) of the spring model MD2 (see FIG. 6) can be increased. As a result, it is possible to reduce the amount of decrease in the load (Fp-Ff) that is lost from the press load P at the time of assembly without being used for the holding force of the lower frame 7. Therefore, a sufficient holding force can be maintained by the flange portion 73 of the lower frame 7 without applying an excessive press load P when assembling the scroll compressor 100.
  • FIG. 8 is an explanatory diagram showing a load and the like acting on the sandwiching portion S1 when the internal pressure of the closed container 1 rises during the operation of the scroll compressor 100.
  • the gas load Fg acts as an upward force in the spring model MD3.
  • the spring model MD1 see FIG. 6
  • the spring model MD2 extend by the same displacement ⁇ x2.
  • a tensile load ⁇ Fc and a tensile load ⁇ Ff are generated as differences from before the gas load Fg acts. The balance of each load as these differences is expressed by the following equations (8) to (10).
  • the following is clarified as the action of the scroll compressor 100 during operation. That is, by providing the side groove 73a in the flange portion 73 and reducing the rigidity of the flange portion 73 (that is, reducing the rigidity coefficient kf), the tensile load ⁇ Ff with respect to the gas load Fg can be reduced.
  • the tensile load ⁇ Ff represents the amount of decrease in the holding force of the lower frame 7. Therefore, even if the internal pressure of the closed container 1 increases during the operation of the scroll compressor 100, the amount of decrease in the holding force of the lower frame 7 can be reduced.
  • the amount of decrease in the rigidity of the lower frame 7 due to the side groove 73a is large.
  • the bottom of the side groove 73a has a diameter rather than the inner edge of the portion where the enlarged diameter portion 13c is in contact with the flange portion 73. It is preferable that the bottom of the side groove 73a is deeper in the radial direction than the inner peripheral surface on the lower side of the tubular chamber 11. As a result, the amount of decrease in the rigidity of the lower frame 7 becomes relatively large, so that the holding force of the lower frame 7 can be sufficiently secured even after the press load is released.
  • ⁇ Effect> According to the first embodiment, by providing the side groove 73a in the flange portion 73 of the lower frame 7, it is possible to reduce the amount of decrease in the holding force of the lower frame 7 due to the release of the press load. That is, a sufficient holding force can be secured in the lower frame 7 without applying an excessive press load. As a result, the tightening allowance of the press-fitting portion 72a can be reduced. Further, it is possible to suppress deformation of the auxiliary bearing 71a (see FIG. 3) due to press fitting of the lower frame 7, and thus to suppress wear and seizure of the auxiliary bearing 71a. Further, during the operation of the scroll compressor 100, the tensile load ⁇ Ff (see FIG. 8) can be reduced with respect to the gas load Fg (see FIG. 8). Therefore, even when the internal pressure of the closed container 1 increases, the amount of decrease in the holding force of the lower frame 7 can be reduced.
  • the configuration of the scroll compressor 100 can be simplified and the manufacturing cost can be reduced. As described above, according to the first embodiment, it is possible to provide a highly reliable scroll compressor 100 with a simple configuration.
  • the second embodiment is different in that the inner peripheral surface of the lower portion of the annular portion 72A (see FIG. 9) is cut out radially outward as compared with the case of the first embodiment (see FIG. 4). Others are the same as those in the first embodiment. Therefore, a part different from the first embodiment will be described, and a description of the overlapping part will be omitted.
  • FIG. 9 is a partially enlarged view showing the vicinity of the lower frame 7A of the scroll compressor 100A according to the second embodiment.
  • the position of the partially enlarged view of FIG. 9 corresponds to the region G1 of FIG.
  • the inner peripheral surface of the lower portion (the portion below the connecting portion 74) of the annular portion 72A is the upper portion of the annular portion 72A (the portion above the connecting portion 74). It is cut out radially outside the inner peripheral surface.
  • the inner peripheral surface of the lower portion of the lower frame 7A is cut out radially outward, and the radial wall thickness t2 from the bottom of the side surface groove 73a to the inner peripheral surface of the annular portion 72A is relatively small. I try to make it smaller. As a result, the portion 721A having a wall thickness t2 is easily deformed by a press load or the like. In the lower frame 7A, stress due to the press load is particularly likely to be concentrated in the vicinity of the side groove 73a. Further, in the manufacture of the scroll compressor 100A, the enlarged diameter portion 13c of the bottom chamber 13 is often designed to be located on the outer side in the radial direction than the lower end surface of the tubular chamber 11. Even in such a case, since the stress in the lower frame 7A due to the press load is dispersed, the breakage of the lower frame 7A can be suppressed. Therefore, the reliability of the scroll compressor 100A can be improved.
  • the third embodiment is different from the first embodiment in that a lower surface groove 72b recessed upward from the lower surface of the annular portion 72B (see FIG. 10) is provided. Others are the same as those in the first embodiment. Therefore, a part different from the first embodiment will be described, and a description of the overlapping part will be omitted.
  • FIG. 10 is a partially enlarged view showing the vicinity of the lower frame 7B of the scroll compressor 100B according to the third embodiment.
  • the position of the partially enlarged view of FIG. 10 corresponds to the region G1 of FIG.
  • a lower surface groove 72b recessed from the lower surface (the surface on the other end side) of the annular portion 72B to the upper side (one end side) is provided in the circumferential direction.
  • the radial wall thickness t2 from the bottom of the side groove 73a to the inner peripheral surface of the annular portion 72B becomes smaller than in the case where the lower surface groove 72b is not provided, so that the stress due to the press load can be dispersed. ..
  • the lower surface groove 72b may be provided over the entire circumference in the circumferential direction, or may be provided in a part of the circumferential direction.
  • FIG. 11 is a perspective view of the lower frame 7C of the scroll compressor 100C according to the fourth embodiment.
  • a cutout portion 72e formed by being cut out radially inward from the outer peripheral surface of the annular portion 72C is provided. It is provided. That is, three notched portions 72e are provided on the outer peripheral surface of the annular portion 72C so as to correspond one-to-one with the three connecting portions 74. That is, in the lower frame 7C, the press-fitting portion 72a is not provided at the portion where the notch portion 72e is provided (on the extension line of the connecting portion 74).
  • the entire annular portion 72C including the press-fit portion 72a is cut out, but the annular portion 72C may not be provided with only the press-fit portion 72a. That is, the press-fitting portion 72a may not be provided in a predetermined region in the circumferential direction when the connecting portion 74 is extended outward in the radial direction. Even with such a configuration, it is possible to prevent the deformation of the press-fitting portion 72a from being directly transmitted to the auxiliary bearing 71a via the connecting portion 74.
  • a notch portion 72e is provided in a predetermined region G2 when the connecting portion 74 is extended radially outward.
  • the reliability of the scroll compressor 100C can be improved by suppressing the deformation of the auxiliary bearing 71a.
  • the fifth embodiment is different from the fourth embodiment in that the outer peripheral surface of the flange portion 73D is cut out in addition to the annular portion 72D of the lower frame 7D (see FIG. 12). Others are the same as those in the fourth embodiment. Therefore, the parts different from the fourth embodiment will be described, and the description of the overlapping parts will be omitted.
  • FIG. 12 is a perspective view of the lower frame 7D of the scroll compressor 100D according to the fifth embodiment.
  • the outer peripheral surface of the annular portion 72D is cut out radially inward in the predetermined region G2 when the connecting portion 74 is extended radially outward, and further, the flange portion 73D is formed.
  • a notch portion 72f is provided in which the outer peripheral surface of the is notched inward in the radial direction. That is, three notched portions 72f are provided on the outer peripheral surfaces of the annular portion 72D and the flange portion 73D in a one-to-one correspondence with the three connecting portions 74.
  • the lower frame 7D (second frame) may have a flange portion 73D at least a part of the peripheral portion K2 thereof.
  • the radial depth of the notch 72f is deeper than the bottom surface of the side groove 73a, but the depth of the notch 72f can be changed as appropriate.
  • the sixth embodiment is different from the first embodiment in that the bottom chamber 13E (see FIG. 13) is installed inside the tubular chamber 11E (see FIG. 13). Others are the same as those in the first embodiment. Therefore, a part different from the first embodiment will be described, and a description of the overlapping part will be omitted.
  • FIG. 13 is a partially enlarged view showing the vicinity of the lower frame 7 of the scroll compressor 100E according to the sixth embodiment.
  • the bottom chamber 13E has a diameter-expanded portion 13c (see FIG. 1) and a large-diameter portion 13b (see FIG. 1) as described in the first embodiment. Is not particularly provided, and is U-shaped in a vertical cross-sectional view.
  • a step portion 11b is provided on the inner peripheral surface of the lower end portion of the tubular chamber 11E.
  • the step portion 11b is a portion to which the flange portion 73 of the lower frame 7 is locked, and is formed so as to increase the inner diameter of the cylinder chamber 11E from the lower end of the cylinder chamber 11E to a predetermined depth.
  • the lower frame 7 includes a flange portion 73 that protrudes radially outward from the annular portion 72. On the side surface of the flange portion 73, a side surface groove 73a recessed inward in the radial direction is provided in the circumferential direction. Then, the vicinity of the lower end (the other end side) of the tubular chamber 11E and the vicinity of the edge of the bottom chamber 13E are fixed in a state of sandwiching the flange portion 73. Specifically, the surface of the stepped portion 11b of the tubular chamber 11E (an annular surface perpendicular to the central axis of the tubular chamber 11E) and the upper end surface of the bottom chamber 13E sandwich the flange portion 73. It is fixed.
  • the inner peripheral surface on the lower side (the other end side) of the tubular chamber 11E and the outer peripheral surface on the upper side (one end side) of the bottom chamber 13E are in contact with each other. Then, in the welded portion W2 shown in FIG. 13, the lower end of the tubular chamber 11E is welded to the outer peripheral surface of the bottom chamber 13. As described above, it is also possible to adopt the press-fit method of the inner cover specification in which the bottom chamber 13E is installed inside the tubular chamber 11E.
  • FIG. 14 is a block diagram of the refrigerant circuit Q of the air conditioner 200 according to the seventh embodiment.
  • the solid line arrow in FIG. 14 indicates the flow of the refrigerant during the heating operation.
  • the broken line arrow in FIG. 14 indicates the flow of the refrigerant during the cooling operation.
  • the air conditioner 200 is a device that performs air conditioning such as cooling and heating. As shown in FIG. 11, the air conditioner 200 includes a scroll compressor 100, an outdoor heat exchanger 51, an outdoor fan 52, an expansion valve 53, a four-way valve 54, an indoor heat exchanger 55, and an indoor fan. 56 and.
  • a scroll compressor 100 In the example shown in FIG. 14, a scroll compressor 100, an outdoor heat exchanger 51, an outdoor fan 52, an expansion valve 53, and a four-way valve 54 are provided in the outdoor unit U1.
  • the indoor heat exchanger 55 and the indoor fan 56 are provided in the indoor unit U2.
  • the scroll compressor 100 is a device that compresses a gaseous refrigerant, and has the same configuration as that of the first embodiment (see FIG. 1).
  • the outdoor heat exchanger 51 is a heat exchanger in which heat is exchanged between the refrigerant passing through the heat transfer tube (not shown) and the outside air sent from the outdoor fan 52.
  • the outdoor fan 52 is a fan that sends outside air to the outdoor heat exchanger 51.
  • the outdoor fan 52 includes an outdoor fan motor 52a as a drive source, and is installed in the vicinity of the outdoor heat exchanger 51.
  • the indoor heat exchanger 55 is a heat exchanger in which heat is exchanged between the refrigerant passing through the heat transfer tube (not shown) and the indoor air (air in the air conditioning chamber) sent from the indoor fan 56.
  • the indoor fan 56 is a fan that sends indoor air to the indoor heat exchanger 55.
  • the indoor fan 56 includes an indoor fan motor 56a as a drive source, and is installed in the vicinity of the indoor heat exchanger 55.
  • the expansion valve 53 is a valve that reduces the pressure of the refrigerant condensed by the "condenser” (one of the outdoor heat exchanger 51 and the indoor heat exchanger 55).
  • the refrigerant decompressed by the expansion valve 53 is guided to an "evaporator” (the other of the outdoor heat exchanger 51 and the indoor heat exchanger 55).
  • the four-way valve 54 is a valve that switches the flow path of the refrigerant according to the operation mode of the air conditioner 200.
  • the scroll compressor 100 In the refrigerant circuit Q, the scroll compressor 100, the outdoor heat exchanger 51 (condenser), the expansion valve 53, and the indoor heat exchanger 55 (evaporator) are used.
  • the refrigerant circulates in sequence.
  • the scroll compressor 100, the indoor heat exchanger 55 (condenser), the expansion valve 53, and the outdoor heat exchanger 51 (evaporator) are used.
  • the refrigerant circulates in sequence.
  • the shape of the side groove 73a may be U-shaped or V-shaped in a vertical cross-sectional view, in addition to the shape shown in FIG.
  • the "bottom" of the side groove 73a is assumed to be a portion located on the innermost side in the radial direction on the wall surface of the side groove 73a (the portion having the deepest depth of the side groove 73a).
  • the present invention is not limited to this. That is, the side groove 73a may be provided on at least a part of the side surface of the flange portion 73.
  • another member is particularly provided in the gap between the side groove 73a and the bottom chamber 13 (in the sixth embodiment, the gap between the side groove 73a and the tubular chamber 11E: see FIG. 13).
  • an annular member (not shown) having a lower rigidity than the annular portion 72 may be installed in the side groove 73a.
  • Such a configuration is also included in the matter that the side groove 73a is provided on the flange portion 73.
  • the configuration in which the bottom chamber 13 includes the enlarged diameter portion 13c and the large diameter portion 13b and the upper end of the large diameter portion 13b and the outer peripheral surface of the tubular chamber 11 are welded to each other has been described. , Not limited to this. That is, instead of the bottom chamber 13, a diameter-expanded portion (not shown) or a large-diameter portion (not shown) may be provided near the lower end of the cylindrical cylindrical chamber 11. In such a configuration, the upper end surface of the bottom chamber 13 and the enlarged diameter portion (not shown) of the tubular chamber 11 are fixed with the flange portion 73 sandwiched between them. Further, the outer peripheral surface near the upper end of the bottom chamber 13 and the inner peripheral surface near the lower end of the tubular chamber 11 come into contact with each other. Even with such a configuration, the same effect as that of the first to fifth embodiments can be obtained.
  • the scroll compressor 100 (see FIG. 1) is installed vertically has been described, but the present invention is not limited to this.
  • the scroll compressor 100 may be installed horizontally or diagonally.
  • the air conditioner 200 (see FIG. 14) described in the seventh embodiment can be applied to various types of air conditioners such as room air conditioners, package air conditioners, and multi air conditioners for buildings.
  • the air conditioner 200 (refrigeration cycle device) provided with the scroll compressor 100 (see FIG. 14) has been described, but the present invention is not limited to this.
  • the second embodiment can be applied to other "refrigerating cycle devices" such as a water heater, an air-conditioned hot water supply device, a refrigerator, and a chiller.
  • each embodiment can be combined appropriately.
  • the second embodiment (see FIG. 9) and the third embodiment (see FIG. 10) may be combined.
  • the fifth embodiment (see FIG. 13) and the sixth embodiment (see FIG. 14) may be combined.
  • various combinations are possible.
  • each embodiment is described in detail in order to explain the present invention in an easy-to-understand manner, and is not necessarily limited to the one including all the configurations described. Further, it is possible to appropriately add / delete / replace other configurations with respect to a part of the configurations of each embodiment.
  • the above-mentioned mechanism and configuration show what is considered necessary for explanation, and do not necessarily show all the mechanisms and configurations in the product.

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

Abstract

L'invention concerne un compresseur à spirales hautement fiable, etc., présentant une configuration simple. Le compresseur (100) à spirales comprend : un récipient étanche (1) ; un moteur électrique (4) ; un vilebrequin (3) ; une spirale fixe (21) ; une spirale tournante (22) ; un cadre supérieur (23) ; et un cadre inférieur (7). Le cadre inférieur (7) comporte une bride (73) dans au moins une partie de son bord circonférentiel. Une partie à proximité de l'extrémité inférieure d'une chambre cylindrique (11) et une partie à proximité du bord d'une chambre inférieure (13) sont fixées de manière à interposer la bride (73) entre elles. Une rainure (73a) de surface latérale, évidée radialement vers l'intérieur, est disposée sur la surface latérale de la bride (73) dans la direction circonférentielle.
PCT/JP2020/045715 2020-12-08 2020-12-08 Compresseur à spirales et dispositif à cycle frigorifique WO2022123657A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
CN202080107367.7A CN116457578A (zh) 2020-12-08 2020-12-08 涡旋压缩机及冷冻循环装置
JP2022567924A JP7398577B2 (ja) 2020-12-08 2020-12-08 スクロール圧縮機及び冷凍サイクル装置
PCT/JP2020/045715 WO2022123657A1 (fr) 2020-12-08 2020-12-08 Compresseur à spirales et dispositif à cycle frigorifique

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2020/045715 WO2022123657A1 (fr) 2020-12-08 2020-12-08 Compresseur à spirales et dispositif à cycle frigorifique

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WO2022123657A1 true WO2022123657A1 (fr) 2022-06-16

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CN (1) CN116457578A (fr)
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Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH07158577A (ja) * 1993-12-10 1995-06-20 Toshiba Corp 密閉形圧縮機
WO2020202515A1 (fr) * 2019-04-03 2020-10-08 日立ジョンソンコントロールズ空調株式会社 Compresseur et climatiseur

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11236085B2 (en) 2018-10-24 2022-02-01 Gilead Sciences, Inc. PD-1/PD-L1 inhibitors

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH07158577A (ja) * 1993-12-10 1995-06-20 Toshiba Corp 密閉形圧縮機
WO2020202515A1 (fr) * 2019-04-03 2020-10-08 日立ジョンソンコントロールズ空調株式会社 Compresseur et climatiseur

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CN116457578A (zh) 2023-07-18
JP7398577B2 (ja) 2023-12-14

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