WO2021044954A1 - スクロール圧縮機 - Google Patents

スクロール圧縮機 Download PDF

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Publication number
WO2021044954A1
WO2021044954A1 PCT/JP2020/032543 JP2020032543W WO2021044954A1 WO 2021044954 A1 WO2021044954 A1 WO 2021044954A1 JP 2020032543 W JP2020032543 W JP 2020032543W WO 2021044954 A1 WO2021044954 A1 WO 2021044954A1
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WO
WIPO (PCT)
Prior art keywords
scroll
spring
pressure
swivel
pressure chamber
Prior art date
Application number
PCT/JP2020/032543
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
二上　義幸
河野　博之
淳 作田
Original Assignee
パナソニックＩｐマネジメント株式会社
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 パナソニックＩｐマネジメント株式会社 filed Critical パナソニックＩｐマネジメント株式会社
Priority to JP2021543734A priority Critical patent/JP7262013B2/ja
Priority to CN202080051616.5A priority patent/CN114144586B/zh
Publication of WO2021044954A1 publication Critical patent/WO2021044954A1/ja

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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
    • 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
    • F04C18/0223—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 with symmetrical double wraps
    • 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
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/02—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/02—Lubrication; Lubricant separation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/20—Rotors
    • 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
    • F04C2240/30—Casings or housings
    • 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
    • F04C2240/80—Other components
    • 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
    • F04C2240/80—Other components
    • F04C2240/809—Lubricant sump

Definitions

  • This disclosure relates to a scroll compressor.
  • Patent Document 1 discloses a low-pressure scroll compressor in a closed container. As shown in FIG. 12, this scroll compressor swivels and drives a compression element 5 composed of a fixed scroll 3 and a swivel scroll 4 and the swivel scroll 4 in a chamber 2 on the low pressure side partitioned by a partition plate 1.
  • the electric element 6 and the electric element 6 are arranged and configured.
  • the refrigerant compressed by the compression element 5 is discharged to the high-pressure side chamber 8 partitioned by the partition plate 1 via the discharge port 7 of the fixed scroll 3.
  • the present disclosure provides a scroll compressor with improved performance and reliability by pressing a swivel scroll against a fixed scroll in just proportion.
  • a low pressure space, a low pressure and high pressure intermediate pressure chamber, and a high pressure chamber are arranged on the back surface of the swivel scroll, and the swivel scroll is pressed against the fixed scroll by the pressure from each of these chambers. It is configured to be.
  • FIG. 1 is a vertical cross-sectional view showing the configuration of the scroll compressor according to the first embodiment of the present disclosure.
  • FIG. 2 is a cross-sectional view of a main part of the main part of the compression element of the scroll compressor.
  • FIG. 3 is a cross-sectional view of a main part of the partition plate portion of the scroll compressor.
  • FIG. 4 is a vertical cross-sectional view showing the configuration of the scroll compressor according to the second embodiment.
  • FIG. 5 is a vertical cross-sectional view showing the configuration of the scroll compressor according to the third embodiment.
  • FIG. 6 is a cross-sectional view of a main part of the main part of the compression element of the scroll compressor.
  • FIG. 7 is a bottom view of the fixed scroll of the scroll compressor.
  • FIG. 8 is an enlarged vertical cross-sectional view of the vicinity of the annular seal member after the assembly of the scroll compressor according to the fourth embodiment.
  • FIG. 9 is an enlarged vertical cross-sectional view of the vicinity of the annular seal member before assembly of the scroll compressor.
  • FIG. 10 is an enlarged vertical cross-sectional view of the vicinity of the annular seal member before assembling the scroll compressor according to the fifth embodiment.
  • FIG. 11 is an enlarged vertical sectional view of the vicinity of the annular seal member before assembling the scroll compressor according to the sixth embodiment.
  • FIG. 12 is a vertical cross-sectional view of a conventional scroll compressor.
  • the low-pressure scroll compressor in a closed container had a pressure in a compression chamber 9 between low pressure and high pressure on the back surface of the swivel scroll 4, as shown in Patent Document 1.
  • the swivel scroll 4 was configured so as not to separate from the fixed scroll 3.
  • an eccentric rotation axis for rotating the swivel scroll 4 is installed at the center of the back surface of the swivel scroll 4.
  • the scroll compressor since the scroll compressor has a low pressure inside the closed container, the central region on the back surface of the swirl scroll 4 is a low pressure region.
  • the present disclosure provides a scroll compressor that suppresses a decrease in efficiency and has improved performance and reliability.
  • the compressor 10 includes a cylindrical closed container 20 whose vertical direction is the longitudinal direction as an outer shell.
  • the vertical direction is the Z-axis direction in each figure.
  • the compressor 10 is a closed scroll compressor provided with a compression mechanism unit 30 for compressing the refrigerant and an electric motor 40 for driving the compression mechanism unit 30 inside the closed container 20.
  • a partition plate 50 for partitioning the inside of the closed container 20 into upper and lower parts is provided above the inside of the closed container 20.
  • the partition plate 50 divides the inside of the closed container 20 into a high-pressure space 60 and a low-pressure space 70.
  • the high-pressure space 60 is a space filled with the high-pressure refrigerant after being compressed by the compression mechanism unit 30.
  • the low-pressure space 70 is a space filled with the low-pressure refrigerant before being compressed by the compression mechanism unit 30.
  • the closed container 20 includes a refrigerant suction pipe 80 that communicates the outside of the closed container 20 with the low pressure space 70, and a refrigerant discharge pipe 90 that communicates the outside of the closed container 20 with the high pressure space 60.
  • a low-pressure refrigerant is introduced into the low-pressure space 70 from a refrigeration cycle circuit (not shown) provided outside the closed container 20 via a refrigerant suction pipe 80 into the compressor 10.
  • the high-pressure refrigerant compressed by the compression mechanism unit 30 is first introduced into the high-pressure space 60. After that, the refrigerant is discharged from the high-pressure space 60 to the refrigeration cycle circuit via the refrigerant discharge pipe 90.
  • an oil sump 100 in which lubricating oil is stored is formed.
  • the compressor 10 includes a compression mechanism unit 30 and an electric motor 40 in a low-pressure space 70.
  • the compression mechanism unit 30 is composed of at least a fixed scroll 110, a swivel scroll 120, a main bearing 130, and a rotation suppressing member (hereinafter referred to as an old dam ring) 140.
  • the fixed scroll 110 is arranged below the partition plate 50 so as to be adjacent to the partition plate 50.
  • the swivel scroll 120 is arranged below the fixed scroll 110 in mesh with the fixed scroll 110.
  • the fixed scroll 110 includes a disk-shaped fixed scroll end plate 111 and a spiral-shaped fixed spiral wrap 112 erected on the lower surface of the fixed scroll end plate 111.
  • the swivel scroll 120 includes a disc-shaped swirl scroll end plate 121, a spiral swirl swirl wrap 122 erected on the upper surface of the swirl scroll end plate 121, and a lower boss portion 123.
  • the lower boss portion 123 is a cylindrical protrusion formed substantially in the center of the lower surface of the swivel scroll end plate 121.
  • a compression chamber 150 is formed between the swirl scroll 120 and the fixed scroll 110.
  • the compression chamber 150 is formed on the inner wall surface side and the outer wall surface side of the swirl swirl wrap 122.
  • the main bearing 130 that supports the swivel scroll 120 is provided below the fixed scroll 110 and the swivel scroll 120.
  • the main bearing 130 includes a boss accommodating portion 131 provided at substantially the center of the upper surface, and a bearing portion 132 provided below the boss accommodating portion 131.
  • the boss accommodating portion 131 is a recess for accommodating the lower boss portion 123 of the swivel scroll 120.
  • the bearing portion 132 is a through hole whose upper end opens into the boss accommodating portion 131 and whose lower end opens into the low pressure space 70.
  • the main bearing 130 supports the swivel scroll 120 on the upper surface, and the bearing portion 132 pivotally supports the rotating shaft 160.
  • the rotating shaft 160 is an axis in which the vertical direction in FIG. 1 is the longitudinal direction.
  • One end side of the rotating shaft 160 is pivotally supported by the bearing portion 132, and the other end side is pivotally supported by the auxiliary bearing 170.
  • the auxiliary bearing 170 is a bearing provided below the low pressure space 70, preferably in the oil sump 100.
  • An eccentric shaft 161 eccentric with respect to the axis of the rotating shaft 160 is provided at the upper end of the rotating shaft 160.
  • the eccentric shaft 161 is slidably inserted into the lower boss portion 123 via the swing bush 180 and the swivel bearing 124.
  • the lower boss portion 123 is swiveled by the eccentric shaft 161.
  • An oil passage 162 through which lubricating oil passes is formed inside the rotating shaft 160.
  • the oil passage 162 is a through hole formed in the axial direction of the rotating shaft 160.
  • One end of the oil passage 162 is opened in the oil sump 100 as a suction port 163 provided at the lower end of the rotating shaft 160.
  • a paddle 190 for pumping lubricating oil from the suction port 163 to the oil passage 162 is provided above the suction port 163.
  • a first branch oil passage 164 is formed above the rotating shaft 160, and a second branch oil passage 165 is formed below the rotating shaft 160.
  • One end of the first branch oil passage 164 opens as the first oil supply port 166 at the bearing surface of the bearing portion 132, and the other end of the first branch oil passage 164 communicates with the oil passage 162.
  • one end of the second branch oil passage 165 is opened as a second oil supply port 167 on the bearing surface of the auxiliary bearing 170, and the other end of the second branch oil passage 165 communicates with the oil passage 162.
  • the upper end of the oil passage 162 opens inside the boss accommodating portion 131 as a third fuel filler port 168.
  • the rotating shaft 160 is connected to the electric motor 40.
  • the electric motor 40 is arranged between the main bearing 130 and the sub bearing 170.
  • the electric motor 40 includes a stator 41 fixed to the closed container 20 and a rotor 42 arranged inside the stator 41.
  • the rotating shaft 160 is fixed to the rotor 42.
  • the rotating shaft 160 includes a balance weight 200a provided above the rotor 42 and a balance weight 200b provided below the rotor 42.
  • the balance weight 200a and the balance weight 200b are arranged at positions shifted by 180 ° in the circumferential direction of the rotation shaft 160.
  • the rotating shaft 160 rotates in a balanced manner by the centrifugal force generated by the balance weight 200a and the balance weight 200b and the centrifugal force generated by the revolving motion of the swivel scroll 120.
  • the balance weight 200a and the balance weight 200b may be provided on the rotor 42.
  • the fixed scroll 110, the swivel scroll 120, and the old dam ring 140 are arranged between the partition plate 50 and the main bearing 130.
  • the partition plate 50 and the main bearing 130 are fixed to the closed container 20.
  • the fixed scroll 110 is fastened to the main bearing 130 with bolts or the like.
  • the swivel scroll 120 is provided so as to be movable in the axial direction between the fixed scroll 110 and the main bearing 130.
  • low-pressure spaces (low-pressure regions) 71 and 72 having low-pressure pressure are arranged at the central portion and the outermost peripheral portion on the back surface of the swivel scroll 120.
  • a high pressure chamber 221 having a high pressure and an intermediate pressure chamber 222 having an intermediate pressure are arranged between the low pressure space 71 in the central portion and the low pressure space 72 in the outermost peripheral portion.
  • the high pressure chamber 221 is arranged on the back surface of the swivel scroll 120, inside the intermediate pressure chamber 222, that is, on the central side.
  • a plurality of annular grooves 133 are formed on the surface supporting the swivel scroll 120 on the outside of the boss accommodating portion 131 of the main bearing 130.
  • a seal member 210 is inserted into the annular groove 133.
  • a pressure chamber 220 is formed between the seal members 210.
  • a pressure higher than that of the low pressure space (low pressure region) 71 and 72 is introduced into this space (pressure chamber 220).
  • the sealing member 210 is made of a resin material such as PTFE, which is generally considered to have good sealing properties.
  • the seal member 210 may be configured in an annular shape.
  • the pressure chamber 220 is further divided into a high pressure chamber 221 and an intermediate pressure chamber 222 by a sealing member 210.
  • a pressure equivalent to that of the discharged gas is introduced into the high pressure chamber 221.
  • the pressure of the gas in the middle of compression between the low pressure and the high pressure of the compression chamber 150 is introduced into the intermediate pressure chamber 222.
  • the area of the high pressure chamber 221 and the intermediate pressure chamber 222 with respect to the swivel scroll 120 and the pressure of the compression chamber 150 to be introduced into the intermediate pressure chamber 222 can be appropriately set. Therefore, even in the low-pressure compressor in the closed container, the swivel scroll 120 does not separate from the fixed scroll 110 and the swivel scroll 120 does not separate from the fixed scroll 110 under various operating conditions in which the compression pressure is different between the low pressure and the high pressure. It is possible to set the optimum pressing force that is not pressed too much.
  • the main bearing 130 is formed with a return path 134 in which one end opens in the boss accommodating portion 131 and the other end opens in the lower surface of the main bearing 130.
  • the old dam ring 140 is provided between the fixed scroll 110 and the swivel scroll 120.
  • the old dam ring 140 prevents the turning scroll 120 from rotating and makes a turning motion.
  • the swirl swirl wrap 122 is a wall having an involute curved cross section whose radius gradually expands from the center side to the outer peripheral side of the swirl scroll end plate 121.
  • the swirl swirl wrap 122 has a predetermined height (length in the vertical direction) and a predetermined wall thickness (length in the radial direction of the swirl swirl wrap 122).
  • a discharge counterbore 125 is formed in a compression chamber 150 communicating with the first discharge port 113, which will be described later, at a substantially central portion of the swivel scroll 120.
  • the swivel scroll end plate 121 is formed with a high pressure introduction path 126 that communicates the discharge counterbore 125 and the high pressure chamber 221.
  • a medium pressure port 127 is formed in a region where a refrigerant having an intermediate pressure during compression exists.
  • the intermediate pressure introduction path 128 communicates the intermediate pressure port 127 and the intermediate pressure chamber 222 (see FIG. 2).
  • a pair of key grooves are provided on the Oldam ring 140 side of the swivel scroll end plate 121.
  • the fixed spiral wrap 112 is a wall having an involute curved cross section whose radius gradually expands from the center side to the outer peripheral side of the fixed scroll end plate 111.
  • the fixed swirl wrap 112 has a predetermined height (vertical length) equal to that of the swirl swirl wrap 122 and a predetermined wall thickness (diametrical length of the fixed swirl wrap 112).
  • a first discharge port 113 is formed at a substantially central portion of the fixed scroll end plate 111. Further, a bypass port 114 is formed on the fixed scroll end plate 111. The bypass port 114 is located in the vicinity of the first discharge port 113 and in a region where the high-pressure refrigerant immediately before the completion of compression exists.
  • the bypass port 114 includes a bypass port that communicates with the compression chamber 150 formed on the outer wall surface side of the swirl swirl wrap 122, and a bypass port that communicates with the compression chamber 150 formed on the inner wall surface side of the swirl swirl wrap 122. Two sets are provided.
  • an outer peripheral step portion 115 having a step with respect to the tip of the fixed spiral wrap 112 is formed on the outer peripheral portion of the fixed scroll 110.
  • the outer peripheral step portion 115 is arranged at a position lower than the tip of the fixed spiral wrap 112 by the thickness of the old dam ring 140 or more.
  • An old dam ring 140 is arranged on the outer peripheral step portion 115.
  • a pair of key grooves are provided on the outer periphery of the fixed scroll 110.
  • a suction portion (not shown) for taking the refrigerant into the compression chamber 150 is formed on the peripheral wall of the fixed scroll 110.
  • an upper boss portion 119 is provided in the center on the upper surface (the surface on the partition plate 50 side) of the fixed scroll 110.
  • the upper boss portion 119 is a columnar protrusion protruding from the upper surface of the fixed scroll 110.
  • the first discharge port 113 and the bypass port 114 are opened on the upper surface of the upper boss portion 119.
  • a discharge space 110H is formed between the upper boss portion 119 and the partition plate 50 on the upper surface side of the upper boss portion 119.
  • the first discharge port 113 and the bypass port 114 communicate with the discharge space 110H.
  • bypass check valve 230 that allows the bypass port 114 to be opened and closed and a bypass check valve stop 240 that prevents excessive deformation of the bypass check valve 230 are provided.
  • a bypass check valve 230 that allows the bypass port 114 to be opened and closed and a bypass check valve stop 240 that prevents excessive deformation of the bypass check valve 230 are provided.
  • the Oldam ring 140 is arranged between the fixed scroll 110 and the swivel scroll 120. As described above, the old dam ring 140 is arranged on the outer peripheral step portion 115 of the fixed scroll 110.
  • the Oldam ring 140 includes a substantially annular ring portion, a pair of first keys projecting from the upper surface of the ring portion, and a pair of second keys projecting from the lower surface of the ring portion.
  • the first key is arranged on a parallel straight line that is not on a straight line.
  • the second key is arranged on a parallel straight line that is not on a straight line.
  • the straight line on which the first key is arranged and the straight line on which the second key is arranged are provided so as to be orthogonal to each other.
  • the first key engages the first keyway of the fixed scroll 110
  • the second key engages the second keyway of the swivel scroll 120 (not shown).
  • the turning scroll 120 can make a turning motion without rotating with respect to the fixed scroll 110.
  • FIG. 3 is a cross-sectional view of a main part of the partition plate portion of the scroll compressor according to the present embodiment.
  • a second discharge port 51 is provided at the center of the partition plate 50.
  • a discharge check valve 250 for opening and closing the second discharge port 51 and a discharge check valve stop 260 for preventing excessive deformation of the discharge check valve 250 are provided.
  • a discharge space 110H is formed between the partition plate 50 and the fixed scroll 110.
  • the discharge space 110H communicates with the compression chamber 150 by the first discharge port 113 and the bypass port 114.
  • the discharge space 110H communicates with the high pressure space 60 by the second discharge port 51.
  • the plate thickness of the discharge check valve 250 is thicker than the plate thickness of the bypass check valve 230. This makes it possible to prevent the discharge check valve 250 from opening before the bypass check valve 230.
  • the cross-sectional area of the second discharge port 51 is larger than the cross-sectional area of the first discharge port 113. As a result, the pressure loss of the refrigerant discharged from the compression chamber 150 can be reduced.
  • a taper may be formed on the inflow side of the second discharge port 51. Thereby, the pressure loss can be further reduced.
  • a recess 52 is provided around the second discharge port 51.
  • the upper boss portion 119 of the fixed scroll 110 is inserted into the recess 52 to form a discharge space 110H.
  • the boss seal member 270 seals between the discharge space 110H and the low pressure space 70.
  • the boss seal member 270 may be configured in an annular shape.
  • the intermediate pressure refrigerant during compression is introduced from the intermediate pressure port 127 shown in FIG. 2 through the intermediate pressure introduction path 128 into the intermediate pressure chamber 222 (see FIG. 2) provided on the back surface of the swivel scroll 120.
  • the compressed high-pressure refrigerant is introduced from the discharge counterbore 125 shown in FIG. 2 through the high-pressure introduction path 126 into the high-pressure chamber 221 (see FIG. 2) provided on the back surface of the swivel scroll 120.
  • the swivel scroll 120 is pressed against the fixed scroll 110 from the back surface of the swivel scroll 120 at an appropriately set pressure of the intermediate pressure chamber 222 and the pressure of the high pressure chamber 221. Therefore, as compared with the case where only the intermediate pressure chamber 222 is provided, the swivel scroll 120 does not separate from the fixed scroll 110 and the swivel scroll 120 becomes the fixed scroll 110 under various operating conditions in which the compression pressure is low pressure and high pressure. On the other hand, it is possible to set the optimum pressing force that is not pressed too much. Therefore, in the low-pressure compressor in a closed container, it is possible to prevent a decrease in efficiency and a decrease in reliability.
  • the opening on the intermediate pressure chamber 222 side of the intermediate pressure introduction path 128 is intermittently communicated with the intermediate pressure chamber 222 across the seal member 210 by the swivel scroll 120 rotating.
  • the compression chamber 150 whose pressure fluctuates due to the compression of the refrigerant and the intermediate pressure chamber 222 can be communicated intermittently. Therefore, the pressure pulsation of the intermediate pressure chamber 222 can be reduced, and the swivel scroll 120 can more reliably suppress the separation of the fixed scroll 110 to improve the efficiency of the compressor.
  • the old dam ring 140 is arranged between the fixed scroll 110 and the swivel scroll 120.
  • the intermediate pressure chamber 222 and the high pressure chamber 221 provided on the back surface of the swivel scroll 120 can be made wider than those of the conventional compressor in which the old dam ring 140 is arranged on the back side of the swivel scroll 120. Therefore, it is possible to secure the areas of the intermediate pressure chamber 222 and the high pressure chamber 221 necessary for properly pressing the swivel scroll 120 against the fixed scroll 110.
  • the swivel scroll 120 is suppressed from separating from the fixed scroll 110 under various operating conditions in which the low-pressure and high-pressure compression pressures are different, and the swivel scroll 120 is the fixed scroll 110. It is possible to set the optimum pressing force that is not pressed too much against the object. Therefore, it is possible to prevent a decrease in the efficiency and a decrease in the reliability of the compressor.
  • the old dam ring 140 is installed in the outer peripheral step portion 115 communicating with the low pressure space 70. Therefore, since the sliding portion of the old dam ring 140 is lubricated with the oil contained in the intake refrigerant, it is possible to prevent a decrease in reliability.
  • low-pressure spaces (low-pressure regions) 71 and 72 are arranged in the central portion and the outermost peripheral portion on the back surface of the swivel scroll 120.
  • a high pressure chamber 221 and an intermediate pressure chamber 222 are arranged between the low pressure spaces (low pressure regions) 71 and 72 on the back surface of the swivel scroll 120.
  • the high pressure chamber 221 is arranged inside (center side) of the intermediate pressure chamber 222.
  • the refrigerant is compressed from low pressure to high pressure as it goes from the outer circumference to the center. Therefore, the central portion of the swivel scroll 120 receives a force in a direction away from the fixed scroll 110 due to a pressure close to high pressure.
  • the high pressure chamber 221 is arranged closer to the center than the intermediate pressure chamber 222, so that the central portion of the swivel scroll 120 is stronger than the outer peripheral portion. It can be pressed against the fixed scroll 110.
  • the separation of the swivel scroll 120 with respect to the fixed scroll 110 can be suppressed more effectively, so that the pressure leakage can be reduced. Further, since an appropriate pressing force can be applied to the swivel scroll 120, it is possible to prevent a decrease in efficiency and a decrease in reliability.
  • the scroll compressor includes a partition plate 50 that divides the inside of the closed container 20 into a high-pressure space 60 and a low-pressure space 70, a fixed scroll 110 adjacent to the partition plate 50, and a fixed scroll 110. It has a swivel scroll 120 that is meshed to form a compression chamber 150, a rotation suppressing member 140 that prevents the swivel scroll 120 from rotating, and a main bearing 130 that supports the swivel scroll 120.
  • the fixed scroll 110, the swivel scroll 120, the rotation suppressing member 140, and the main bearing 130 are arranged in the low pressure space 70.
  • the fixed scroll 110 and the swivel scroll 120 are arranged between the partition plate 50 and the main bearing 130.
  • Low-pressure spaces (low-pressure regions) 71 and 72, low-pressure and high-pressure intermediate pressure chambers 222, and high-pressure chambers 221 are arranged on the back surface of the swirl scroll 120.
  • the intermediate pressure chamber 222 and the high pressure chamber 221 can introduce an appropriate pressure into an appropriate region on the back surface of the swirl scroll 120. Therefore, it is possible to suppress the swivel scroll 120 from separating from the fixed scroll 110 and reduce the pressure leakage. Further, since it is not necessary to mount a special component for expanding the area to which pressure is applied on the back surface of the swivel scroll, it is possible to prevent a decrease in efficiency and a decrease in reliability with a simple configuration.
  • the scroll compressor of the present embodiment has a configuration in which the central portion and the outermost peripheral portion on the back surface of the swivel scroll are low-pressure spaces (low-pressure regions) 71 and 72, and the high-pressure chamber 221 is arranged inside the intermediate pressure chamber 222. is there.
  • a large pressure can be applied to the central portion of the swivel scroll 120 to which a strong pressure is applied in the direction away from the fixed scroll 110. Therefore, the separation of the swivel scroll 120 with respect to the fixed scroll 110 can be effectively suppressed to reduce pressure leakage, and an appropriate pressing force can be applied to the swivel scroll 120, resulting in a decrease in efficiency and reliability. Can be prevented.
  • annular seal member 210 that separates the low-pressure space (low-pressure region) 71, 72, the intermediate pressure chamber 222, and the high-pressure chamber 221 is arranged on the back surface of the swirl scroll 120. ing.
  • the pressure communicating with the compression chamber 150 can be arbitrarily determined. Therefore, the swivel scroll 120 can be pressed against the fixed scroll 110 with the optimum pressure. Therefore, it is possible to suppress the turning scroll 120 from separating from the fixed scroll 110 and reduce the pressure leakage. Further, since an appropriate pressing force can be applied to the swivel scroll 120, it is possible to prevent a decrease in efficiency and a decrease in reliability.
  • the rotation suppressing member 140 is arranged between the swivel scroll 120 and the fixed scroll 110.
  • the high pressure chamber 221 and the intermediate pressure chamber 222 can be provided to the maximum in the area on the back surface of the swivel scroll 120. Therefore, the swivel scroll 120 can be properly pressed against the fixed scroll 110, the swivel scroll 120 can be suppressed from separating from the fixed scroll 110, and pressure leakage can be reduced. Further, since an appropriate pressing force can be applied to the swivel scroll 120, it is possible to prevent a decrease in efficiency and a decrease in reliability.
  • FIG. 4 is a vertical cross-sectional view of the scroll compressor according to the second embodiment.
  • the compressor 10 includes a cylindrical closed container 20 whose vertical direction is the longitudinal direction as an outer shell.
  • the vertical direction is the Z-axis direction in each figure.
  • the high voltage introduction path 129 is arranged inside the fixed scroll 110. Further, a high-voltage introduction path 126 is arranged inside the swivel scroll 120.
  • the swivel scroll 120 swivels, so that the high-pressure introduction path 126 and the high-pressure introduction path 129 are intermittently communicated with each other, and the discharge space 110H from which the high-pressure refrigerant is discharged from the fixed scroll 110 and the high-pressure chamber 221 are communicated with each other. Scroll.
  • the oil accumulated in the discharge space 110H can be supplied to the sliding portion between the swivel scroll 120 and the fixed scroll 110, the reliability of the sliding portion can be improved.
  • the discharge space 110H and the high pressure chamber 221 are communicated with each other.
  • a stable pressure can be applied to the high pressure chamber 221 with relatively little fluctuation, so that the swivel scroll 120 can be stably pressed against the fixed scroll 110. Therefore, it is possible to more reliably suppress the turning scroll 120 from separating from the fixed scroll 110, and it is possible to reduce pressure leakage. Further, since an appropriate pressing force can be applied to the swivel scroll 120, it is possible to prevent a decrease in efficiency and a decrease in reliability.
  • FIG. 5 is a vertical cross-sectional view of the scroll compressor according to the third embodiment. Further, FIG. 6 is a cross-sectional view of a main part of the main part of the compression element of the scroll compressor, and FIG. 7 is a bottom view of the fixed scroll.
  • the compressor 10 includes a cylindrical closed container 20 having a longitudinal direction in the vertical direction as an outer shell.
  • the vertical direction is the Z-axis direction in each figure.
  • the intermediate pressure chamber 222 and the high pressure chamber 221 are arranged inside the outermost peripheral portion 116 of the thrust sliding surface (the alternate long and short dash line in FIGS. 6 and 7) with the swivel scroll 120 in the fixed scroll 110.
  • the outermost peripheral portion 116 of the thrust sliding surface refers to the peripheral edge of the maximum range of the thrust sliding surface with the swivel scroll 120 in the fixed scroll 110.
  • the pressing force by the intermediate pressure chamber 222 and the high pressure chamber 221 is applied to the swivel scroll 120 inside the outermost peripheral portion 116 of the thrust sliding surface.
  • the swivel scroll 120 is at the pressure of the intermediate pressure chamber 222 and the high pressure chamber 221 provided inside the outermost peripheral portion 116 of the thrust sliding surface with the swivel scroll 120 of the fixed scroll 110. , Pressed against the fixed scroll 110. Therefore, it is possible to prevent the outer peripheral portion of the swivel scroll end plate 121 from being deformed by the pressure of the intermediate pressure chamber 222 and the high pressure chamber 221.
  • the scroll compressor according to the present embodiment has the configuration of the first embodiment or the second embodiment, and further, the intermediate pressure chamber 222 and the high pressure chamber 221 are formed from the outermost peripheral portion 116 of the thrust sliding surface of the swivel scroll and the fixed scroll. Is also placed inside.
  • FIG. 8 is an enlarged vertical cross-sectional view of the vicinity of the annular seal member after the assembly of the scroll compressor according to the present embodiment. Since the basic configuration of the present embodiment is the same as that of the first to third embodiments, the description thereof will be omitted. Further, the same components as those already described are designated by the same reference numerals, and some description thereof will be omitted.
  • a plurality of annular seal members 210 are provided in a plurality of storage grooves 133 provided in the main bearing 130. It is sealed by being inserted. Specifically, a plurality of annular seal members 210a, 210b, 210c are inserted into the storage grooves 133a, 133b, 133c, respectively. Further, a plurality of spring members 211a, 211b, 211c are inserted between the plurality of annular seal members 210a, 210b, 210c and the bottom surfaces of the storage grooves 133a, 133b, 133c, respectively. In the present embodiment, the plurality of spring members 211a, 211b, 211c are configured so that the spring loads F at the time of assembly are substantially the same as each other.
  • the spring load F of each of the plurality of spring members 211 is within ⁇ 10% of the average of the spring loads of the plurality of spring members 211.
  • the plurality of annular seal members 210 are uniformly pressed against the swivel scroll 120 by the plurality of spring members 211. Therefore, it is possible to more reliably and effectively prevent a decrease in efficiency and a decrease in reliability.
  • the operation of the annular seal member 210 may become unstable immediately after the compressor is started or depending on the operating conditions.
  • the annular seal member 210 becomes unstable, the annular seal member 210 is not pressed against the back surface of the swivel scroll 120, and as a result, the intermediate pressure chamber 222 having a pressure lower than the pressure of the high pressure chamber 221 is subjected to the high pressure of the high pressure chamber 221. Excessive inflow of refrigerant and oil is possible. In such a case, the swivel scroll 120 is excessively pressed against the fixed scroll 110, which may reduce the efficiency of the compressor and reduce the reliability.
  • the plurality of annular seal members 210a, 210b, 210c are imprinted on the back surface of the swivel scroll 120 by the spring loads of the plurality of spring members 211a, 211b, 211c, respectively. .. Further, the plurality of spring members 211a, 211b, 211c are configured so that the spring loads F at the time of assembly are substantially the same as each other. Therefore, the back surface of the swivel scroll 120 is imprinted with the annular seal members 210a, 210b, 210c in a well-balanced manner. That is, the back surface of the swivel scroll 120 can be stably stamped without being affected by pressure fluctuations and the like. Therefore, it is possible to improve the efficiency from the time when the compressor is started, and to suppress the deterioration of performance and reliability due to the unstable behavior of the swivel scroll 120.
  • the spring constant ka of the spring member (first spring member) 211a, the spring constant kb of the spring member (second spring member) 211b, and the spring of the spring member (third spring member) 211c have a spring constant kc.
  • the constants are almost the same as each other.
  • each spring member 211 is within ⁇ 10% of the average of the spring constants of the spring member 211.
  • the spring load F of each spring member 211 can be set to within ⁇ 10% of the average of the spring loads F.
  • FIG. 9 is an enlarged vertical cross-sectional view of the vicinity of the annular seal member before assembling the scroll compressor according to the present embodiment.
  • the spring constant ka of the spring member (first spring member) 211a, the spring constant kb of the spring member (second spring member) 211b, and the spring constant kc of the spring member (third spring member) 211c are almost the same. Further, in order to keep the amount of contraction x of the spring constant, the storage groove (first storage groove) 133a, the storage groove (second storage groove) 133b, and the storage groove (third storage groove) 133c arranged in the main bearing 130.
  • the depths of 133h are made constant, and the natural lengths 211h (natural lengths 211ah, 211bh, 211ch) of the plurality of spring members 211a, 211b, 211c are made constant.
  • the depths 133h (depths 133ah, 133bh, 133ch) of the storage grooves 133a, 133b, 133c of the main bearing 130 are constant, and the plurality of spring members 211a, 211b, 211c are natural.
  • the length 211h (natural length 211ah, 211bh, 211ch) is constant.
  • at least one of the depth 133h of each of the storage grooves 133a, 133b, 133c and the natural length 211h of the plurality of spring members 211a, 211b, 211c is changed, and each spring of the spring members 211a, 211b, 211c is changed.
  • the amount of shrinkage x may be constant.
  • the partition plate that divides the inside of the closed container into the high-pressure space and the low-pressure space, the fixed scroll adjacent to the partition plate, and the fixed scroll are meshed to form a compression chamber. It has a swivel scroll, a rotation suppressing member that prevents the swivel scroll from rotating, and a main bearing that supports the swivel scroll.
  • the fixed scroll, the swivel scroll, the rotation restraining member, and the main bearing are arranged in the low pressure space, and the fixed scroll and the swivel scroll are arranged between the partition plate and the main bearing.
  • a low-pressure space, a low-pressure and high-pressure intermediate pressure chamber, and a high-pressure chamber are arranged on the back surface of the swivel scroll. Further, a plurality of annular seal members for partitioning the low pressure space, the intermediate pressure chamber, and the high pressure chamber are arranged, and a plurality of spring members are arranged on the back surface of the annular seal member.
  • the spring member can be swiveled particularly immediately after the compressor is started.
  • a plurality of annular seal members can be pressed against the fixed scroll in a well-balanced manner on the back surface of the scroll, and the sealing property is improved. Therefore, the swivel scroll can be stably pressed against the fixed scroll, and the performance and reliability can be effectively improved.
  • spring constants of the plurality of spring members may be constant with each other.
  • the spring constant can be easily made constant depending on the spring thickness, spring width, number of folds, etc. of the leaf spring. It is possible to adjust. Then, if the amount of contraction of the springs of the plurality of spring members is made substantially the same as each other, the spring loads of the plurality of spring members can be easily made substantially the same.
  • FIG. 10 is an enlarged vertical cross-sectional view of the vicinity of the annular seal member before assembling the scroll compressor according to the present embodiment.
  • the spring constants ka, kb, and kc of the plurality of spring members 211a, 211b, and 211c are different from each other. Further, the natural lengths 211h of the plurality of spring members 211a, 211b, 211c are substantially the same as each other.
  • the spring constants ka, kb, kc of the plurality of spring members 211a, 211b, 211c are different from each other, the natural lengths 211h of the plurality of spring members 211a, 211b, 211c are substantially the same as each other, and
  • the depths 133ah, 133bh, 133ch of the plurality of storage grooves 133a, 133b, 133c in the main bearing 130 By adjusting the depths 133ah, 133bh, 133ch of the plurality of storage grooves 133a, 133b, 133c in the main bearing 130, the shrinkage amount x of the plurality of spring members 211a, 211b, 211c can be adjusted. Therefore, the spring loads F of the plurality of spring members 211a, 211b, and 211c can be easily made substantially the same by adjusting the storage groove 133 of the main bearing 130 by processing.
  • the natural length 211h of the plurality of spring members 211a, 211b, 211c is preferably within ⁇ 30%. Since the storage groove depths 133ah, 133bh, and 133ch can be processed with high accuracy, the spring loads of the plurality of spring members 211a, 211b, and 211c can be adjusted by adjusting the storage groove depths 133ah, 133bh, and 133ch, respectively. Fs can be approximately the same as each other.
  • the scroll compressor of the present embodiment is configured such that the spring constants of the plurality of spring members are different from each other and the natural lengths of the plurality of spring members are substantially the same as each other.
  • the spring constants of the plurality of spring members are different, the natural lengths of the plurality of spring members are made the same, and the depths of the plurality of storage grooves in the main bearing are adjusted to cause the plurality of spring members to shrink.
  • the amount can be adjusted. Therefore, the spring loads of the plurality of spring members can be easily made substantially the same by processing the storage groove.
  • FIG. 11 is an enlarged vertical cross-sectional view of the vicinity of the annular seal member before assembling the scroll compressor according to the present embodiment.
  • the spring constants ka, kb, and kc of the plurality of spring members 211a, 211b, and 211c are different from each other. Further, the depths 133h of the storage grooves 133a, 133b, 133c provided in the main bearing 130 are configured to be substantially the same as each other.
  • the depths 133h of the plurality of storage grooves 133a, 133b, and 133c provided in the main bearing 130 are substantially the same as each other.
  • the shrinkage amount x of the plurality of spring members 211a, 211b, 211c can be adjusted by adjusting the natural lengths 211ah, 211bh, 211ch of the plurality of spring members 211a, 211b, 211c, respectively. Therefore, the spring loads F of the plurality of spring members 211a, 211b, and 211c can be made substantially the same with each other easily and at low cost during processing.
  • the depth 133h (depth 133ah, 133bh, 133ch) of the storage grooves 133a, 133b, 133c provided in the main bearing 130 is preferably within ⁇ 5%.
  • the processing tolerance of the natural lengths 211h (natural lengths 211ah, 211bh, 211ch) of the spring members 211a, 211b, 211c can be increased, so that the springs can be easily processed, and the processing cost can be further reduced.
  • the scroll compressor of the present embodiment is configured so that the spring constants of the plurality of spring members are different from each other and the depths of the storage grooves provided in the main bearing are substantially the same as each other. There is.
  • the depths of the plurality of storage grooves provided in the main bearing are set to be the same, and the natural lengths of the plurality of spring members are adjusted.
  • the amount of contraction of the spring member can be adjusted. Therefore, the spring loads of the plurality of spring members can be made substantially the same with each other easily and at a lower cost during processing.
  • the scroll compressor according to the present disclosure can prevent a decrease in efficiency and a decrease in reliability by pressing a swivel scroll with an appropriate force against a fixed scroll even in a low-pressure compressor in a closed container. Therefore, it is useful for scroll compressors of refrigeration cycle devices used in electric appliances such as water heaters, hot water heaters, and air conditioners.
  • Compressor 20 Airtight container 30 Compressor mechanism 40 Electric motor 41 stator 42 rotor 50 partition plate 51 2nd discharge port 52 recess 60 high pressure space 70 low pressure space 71,72 low pressure space (low pressure region) 80 Refrigerant suction pipe 90 Refrigerant discharge pipe 100 Oil pool 110 Fixed scroll 110H Discharge space 111 Fixed scroll end plate 112 Fixed swirl wrap 113 First discharge port 114 Bypass port 115 Outer peripheral stepped part 116 Thrust sliding surface outermost outermost part 119 Upper boss part 120 Swivel scroll 121 Swivel scroll end plate 122 Swivel swirl wrap 123 Lower boss part 124 Swivel bearing 125 Discharge counterbore 126 High pressure introduction path 127 Medium pressure port 128 Intermediate pressure introduction path 129 High pressure introduction path 130 Main bearing 131 Boss accommodating part 132 Bearing part 133 Circular groove (storage groove) 133a annular groove (first storage groove) 133b annular groove (second storage groove) 133c annular groove (third storage groove) 133h depth 133ah

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
PCT/JP2020/032543 2019-09-05 2020-08-28 スクロール圧縮機 WO2021044954A1 (ja)

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Cited By (1)

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CN114215750A (zh) * 2021-11-24 2022-03-22 苏州为山之环境技术有限公司 一种轴向密封机构及包括该轴向密封机构的涡旋压缩机

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JPH05149270A (ja) * 1991-11-29 1993-06-15 Toshiba Corp スクロール式圧縮機
JPH0921389A (ja) * 1996-08-19 1997-01-21 Hitachi Ltd スクロール圧縮機
JP2001090680A (ja) * 1999-09-27 2001-04-03 Toyota Autom Loom Works Ltd スクロール型圧縮機のシール構造
JP2005140016A (ja) * 2003-11-06 2005-06-02 Denso Corp スクロール型圧縮機
JP2005147101A (ja) * 2003-11-20 2005-06-09 Mitsubishi Electric Corp スクロール圧縮機及びこれを用いた冷凍空調装置
JP2006161818A (ja) * 2006-02-07 2006-06-22 Mitsubishi Electric Corp スクロール圧縮機
JP2018035748A (ja) * 2016-08-31 2018-03-08 ダイキン工業株式会社 スクロール圧縮機

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JPH1113655A (ja) * 1997-06-20 1999-01-19 Fujitsu General Ltd スクロール圧縮機
JP3893487B2 (ja) * 1997-10-01 2007-03-14 三菱電機株式会社 スクロール圧縮機

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH05149270A (ja) * 1991-11-29 1993-06-15 Toshiba Corp スクロール式圧縮機
JPH0921389A (ja) * 1996-08-19 1997-01-21 Hitachi Ltd スクロール圧縮機
JP2001090680A (ja) * 1999-09-27 2001-04-03 Toyota Autom Loom Works Ltd スクロール型圧縮機のシール構造
JP2005140016A (ja) * 2003-11-06 2005-06-02 Denso Corp スクロール型圧縮機
JP2005147101A (ja) * 2003-11-20 2005-06-09 Mitsubishi Electric Corp スクロール圧縮機及びこれを用いた冷凍空調装置
JP2006161818A (ja) * 2006-02-07 2006-06-22 Mitsubishi Electric Corp スクロール圧縮機
JP2018035748A (ja) * 2016-08-31 2018-03-08 ダイキン工業株式会社 スクロール圧縮機

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN114215750A (zh) * 2021-11-24 2022-03-22 苏州为山之环境技术有限公司 一种轴向密封机构及包括该轴向密封机构的涡旋压缩机
CN114215750B (zh) * 2021-11-24 2024-01-23 苏州为山之环境技术有限公司 一种轴向密封机构及包括该轴向密封机构的涡旋压缩机

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CN114144586A (zh) 2022-03-04
JP7262013B2 (ja) 2023-04-21

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