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WO2018008495A1 - Compresseur à spirale - Google Patents

Compresseur à spirale Download PDF

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Publication number
WO2018008495A1
WO2018008495A1 PCT/JP2017/023834 JP2017023834W WO2018008495A1 WO 2018008495 A1 WO2018008495 A1 WO 2018008495A1 JP 2017023834 W JP2017023834 W JP 2017023834W WO 2018008495 A1 WO2018008495 A1 WO 2018008495A1
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WO
WIPO (PCT)
Prior art keywords
wrap
scroll
height
gap
expansion coefficient
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/JP2017/023834
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English (en)
Japanese (ja)
Inventor
亮太 中井
泰弘 村上
康夫 水嶋
匡宏 野呂
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Daikin Industries Ltd
Original Assignee
Daikin Industries Ltd
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 Daikin Industries Ltd filed Critical Daikin Industries Ltd
Publication of WO2018008495A1 publication Critical patent/WO2018008495A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • 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.
  • a scroll compressor includes a fixed wrap and a swivel wrap having a tooth bottom portion that has a step formed so as to become deeper from the outer peripheral side toward the inner peripheral side (Patent Document 1 (International Publication No. WO2014 / 155646). )reference).
  • An object of the present invention is to provide a scroll compressor that suppresses contact between two scroll members.
  • a scroll compressor includes a first scroll member made of a first material and a second scroll member made of a second material.
  • the first scroll member has a spiral first wrap.
  • the second scroll member forms a compression chamber together with the first scroll member.
  • the second scroll member has a spiral second wrap.
  • the second material is different from the first material.
  • the linear expansion coefficient of the second material is larger than the linear expansion coefficient of the first material.
  • the average thickness of the entire second wrap is thinner than the average thickness of the entire first wrap.
  • the average thickness of the entire first wrap and the entire second wrap are different from each other in average thickness. Specifically, the average thickness of the entire second wrap is thinner than the average thickness of the entire first wrap. Therefore, the amount of expansion of the second wrap due to heat can be reduced.
  • the second lap is set to be thin in advance, so that contact between the two scroll members can be suppressed. In particular, wear due to contact between the first wrap and the second wrap can be suppressed.
  • a scroll compressor includes a first scroll member made of a first material and a second scroll member made of a second material.
  • the first scroll member has a spiral first wrap.
  • the second scroll member forms a compression chamber together with the first scroll member.
  • the second scroll member has a spiral second wrap.
  • the second material is different from the first material.
  • the linear expansion coefficient of the second material is larger than the linear expansion coefficient of the first material.
  • the average height of the entire second lap is lower than the average height of the entire first lap.
  • the average height of the entire first wrap and the second wrap is different from each other. Specifically, the average height of the entire second lap is lower than the average height of the entire first lap. Therefore, the amount of expansion of the second wrap due to heat can be reduced. In anticipation of the amount of expansion due to heat, the height of the second wrap is set to be low in advance, so that contact between the two scroll members can be suppressed.
  • the linear expansion coefficient of the second material is in the range of 101% to 107% with respect to the linear expansion coefficient of the first material.
  • the thickness or height of the second wrap is set in consideration of the difference in expansion amount due to the difference. is doing. Accordingly, contact between the first scroll member and the second scroll member can be suppressed.
  • the first scroll member has a first base on which a first wrap is formed. At least one of the second wrap and the first base is formed in a stepped shape from the outer peripheral side to the inner peripheral side of the second wrap. Thereby, the 1st clearance gap between the front-end
  • the rate of change of the first gap between the inner peripheral end and the outer peripheral end in the central portion of the second lap is greater than the rate of change of the first gap between the inner peripheral end and the outer peripheral end in the non-central portion of the second lap.
  • the rate of change of the first gap at the center of the second lap is locally increased.
  • the first gap in the center of the second wrap is set to be locally large in anticipation of expansion of the second lap due to heat. Contact between the two scroll members at the center can be suppressed.
  • the second scroll member has a second base on which a second wrap is formed. At least one of the first wrap and the second base is formed in a stepped shape from the outer peripheral side to the inner peripheral side of the first wrap. Thereby, the 2nd clearance gap between the front-end
  • the rate of change of the second gap between the inner peripheral end and the outer peripheral end in the central portion of the first lap is greater than the rate of change of the second gap between the inner peripheral end and the outer peripheral end in the non-central portion of the first lap.
  • the rate of change of the second gap at the center of the first lap is locally increased.
  • the second gap in the center of the first wrap is set to be locally large in anticipation of the expansion of the first lap due to heat. Contact between the two scroll members at the center can be suppressed.
  • the first scroll member and the second scroll member compress a refrigerant containing more than 50% by weight of R32 as a refrigerant.
  • the refrigerant containing more than 50% by weight of R32 and the R410A refrigerant when the refrigerant containing more than 50% by weight of R32 and the R410A refrigerant are compressed under the same conditions, the refrigerant containing more than 50% by weight of R32 is R410A. It becomes hotter than the refrigerant. That is, the first wrap and the second wrap are more easily deformed. Even in this case, since the thickness or height of the second wrap is set according to the difference in the linear expansion coefficient, the contact between the first scroll member and the second scroll member can be suppressed.
  • the second lap is set to be thin in advance in anticipation of the amount of expansion due to heat, so that the contact between the two scroll members can be suppressed.
  • the second lap is set to be low in advance in anticipation of the amount of expansion due to heat, so that the contact between the two scroll members can be suppressed.
  • contact between the first scroll member and the second scroll member can be suppressed even when the difference in linear expansion coefficient is relatively small.
  • the contact between the two scroll members at the center of the compression chamber can be suppressed.
  • the contact between the two scroll members at the center of the compression chamber can be suppressed.
  • FIG. 1 is a longitudinal sectional view of a scroll compressor 101 according to the present embodiment.
  • the scroll compressor 101 is used in a refrigeration apparatus such as an air conditioner.
  • the scroll compressor 101 compresses the refrigerant gas circulating in the refrigerant circuit of the refrigeration apparatus.
  • a refrigerant containing more than 50% by weight of R32 can be used as the refrigerant.
  • the scroll compressor 101 mainly includes a casing 10, a compression mechanism 15, a housing 23, an Oldham coupling 39, a drive motor 16, a lower bearing 60, a crankshaft 17, and a suction.
  • a tube 19 and a discharge tube 20 are provided.
  • the casing 10 includes a cylindrical body casing portion 11, a bowl-shaped upper wall section 12, and a bowl-shaped bottom wall section 13.
  • the upper wall portion 12 is welded to the upper end portion of the trunk portion casing portion 11 in an airtight manner.
  • the bottom wall portion 13 is welded to the lower end portion of the body casing portion 11 in an airtight manner.
  • the casing 10 is installed so that the cylindrical axial direction of the trunk casing 11 is along the vertical direction.
  • a compression mechanism 15, a housing 23, a drive motor 16, a crankshaft 17 and the like are accommodated inside the casing 10.
  • An oil sump space 10 a in which lubricating oil is stored is formed at the bottom of the casing 10. Lubricating oil is used to keep the lubricity of sliding parts such as the compression mechanism 15 good during the operation of the scroll compressor 101.
  • the compression mechanism 15 sucks and compresses the low-temperature and low-pressure refrigerant gas and discharges the compressed refrigerant that is the high-temperature and high-pressure refrigerant gas.
  • the compression mechanism 15 is mainly composed of a fixed scroll 24 and a turning scroll 26.
  • the fixed scroll 24 is fixed with respect to the casing 10.
  • the orbiting scroll 26 performs a revolving motion with respect to the fixed scroll 24.
  • the fixed scroll 24 includes a first end plate 24a as a first base and a first wrap 24b.
  • the first wrap 24b is formed upright on the first end plate 24a.
  • the first wrap 24b has a spiral shape.
  • a main suction hole 24c is formed in the first end plate 24a.
  • the main suction hole 24c is a space that connects the suction pipe 19 and a compression chamber 40 described later.
  • the main suction hole 24c forms a suction space.
  • the suction space is a space for introducing a low-temperature and low-pressure refrigerant gas from the suction pipe 19 into the compression chamber 40.
  • a discharge hole 41 is formed at the center of the first end plate 24a.
  • an enlarged recess 42 communicating with the discharge hole 41 is formed on the upper surface of the first end plate 24a.
  • the enlarged recess 42 is a space recessed in the upper surface of the first end plate 24a.
  • a lid 44 is fixed to the upper surface of the fixed scroll 24 with bolts 44 a so as to close the enlarged recess 42.
  • the fixed scroll 24 and the lid 44 are tightly sealed through a gasket (not shown).
  • a muffler space 45 that silences the operation sound of the compression mechanism 15 is formed by covering the enlarged recess 42 with the lid 44.
  • the fixed scroll 24 is formed with a first compressed refrigerant channel 46 that communicates with the muffler space 45 and opens on the lower surface of the fixed scroll 24.
  • An oil groove 24e is formed on the lower surface of the first end plate 24a.
  • Gray cast iron can be used as the material of the fixed scroll 24 as the first material.
  • FC250 can be used.
  • the linear expansion coefficient of FC250 is about 11.5 to 12.0 ( ⁇ 10 ⁇ 6 / ° C.).
  • the orbiting scroll 26 includes a second end plate 26a as a second base and a second wrap 26b.
  • the second end plate 26a has a disk shape.
  • An upper end bearing 26c is formed at the center of the lower surface of the second end plate 26a.
  • the second wrap 26b is formed upright on the second end plate 26a.
  • the second wrap 26b has a spiral shape.
  • the orbiting scroll 26 has an oil supply hole 63 formed therein.
  • the oil supply pore 63 communicates the outer peripheral portion of the upper surface of the second end plate 26a and the space inside the upper end bearing 26c.
  • the fixed scroll 24 and the orbiting scroll 26 form a compression chamber 40 by the engagement of the first wrap 24b and the second wrap 26b.
  • the compression chamber 40 is a space surrounded by the first end plate 24a, the first wrap 24b, the second end plate 26a, and the second wrap 26b.
  • the volume of the compression chamber 40 is gradually reduced by the revolving motion of the orbiting scroll 26.
  • the lower surfaces of the first end plate 24a and the first wrap 24b slide with the upper surfaces of the second end plate 26a and the second wrap 26b.
  • the surface of the fixed scroll 24 that slides with the orbiting scroll 26 is referred to as a sliding surface 24d.
  • the linear expansion coefficient of the orbiting scroll 26 is larger than the linear expansion coefficient of the fixed scroll 24. More specifically, the linear expansion coefficient of the orbiting scroll 26 is in the range of 101% to 107% with respect to the linear expansion coefficient of the fixed scroll 24.
  • Ductile cast iron can be used as the material of the orbiting scroll 26 as the second material.
  • FCD600 can be used.
  • the linear expansion coefficient of FCD is about 11.7 to 12.8 ( ⁇ 10 ⁇ 6 / ° C.).
  • the housing 23 is disposed below the compression mechanism 15.
  • the outer peripheral surface of the housing 23 is joined to the inner peripheral surface of the body casing portion 11 in an airtight manner. Thereby, the internal space of the casing 10 is partitioned into a high-pressure space S ⁇ b> 1 below the housing 23 and a low-pressure space S ⁇ b> 2 that is a space above the housing 23.
  • the housing 23 mounts a fixed scroll 24 and sandwiches the orbiting scroll 26 together with the fixed scroll 24.
  • a second compressed refrigerant channel 48 is formed through the outer periphery of the housing 23 in the vertical direction. The second compressed refrigerant channel 48 communicates with the first compressed refrigerant channel 46 on the upper surface of the housing 23, and communicates with the high-pressure space S ⁇ b> 1 on the lower surface of the housing 23.
  • the crank chamber S3 is recessed in the upper surface of the housing 23.
  • a housing through hole 31 is formed in the housing 23.
  • the housing through hole 31 penetrates the housing 23 in the vertical direction from the center of the bottom surface of the crank chamber S3 to the center of the lower surface of the housing 23.
  • a portion that is a part of the housing 23 and in which the housing through hole 31 is formed is referred to as an upper bearing 32.
  • the housing 23 is formed with an oil return passage 23a that connects the high-pressure space S1 near the inner surface of the casing 10 and the crank chamber S3.
  • the Oldham Joint 39 is an annular member installed between the orbiting scroll 26 and the housing 23.
  • the Oldham joint 39 is a member for preventing rotation of the orbiting scroll 26 that is revolving.
  • the drive motor 16 is a brushless DC motor disposed below the housing 23.
  • the drive motor 16 is mainly composed of a stator 51 fixed to the inner surface of the casing 10 and a rotor 52 disposed with an air gap provided inside the stator 51.
  • the outer peripheral surface of the stator 51 is provided with a plurality of core cut portions that are formed from the upper end surface to the lower end surface of the stator 51 and are notched at predetermined intervals in the circumferential direction.
  • the core cut portion forms a motor cooling passage 55 that extends in the vertical direction between the body casing portion 11 and the stator 51.
  • the rotor 52 is connected to the crankshaft 17 passing through the center of rotation in the vertical direction.
  • the rotor 52 is connected to the compression mechanism 15 via the crankshaft 17.
  • (1-6) Lower Bearing The lower bearing 60 is disposed below the drive motor 16. The outer peripheral surface of the lower bearing 60 is joined to the inner surface of the casing 10 in an airtight manner. The lower bearing 60 supports the crankshaft 17.
  • crankshaft 17 is arranged so that its axial direction is along the vertical direction.
  • the crankshaft 17 has a shape in which the axial center of the upper end portion is slightly eccentric with respect to the axial center of the portion excluding the upper end portion.
  • the crankshaft 17 has a balance weight 18.
  • the balance weight 18 is fixed in close contact with the crankshaft 17 at a height position below the housing 23 and above the drive motor 16.
  • the crankshaft 17 is connected to the rotor 52 through the rotation center of the rotor 52 in the vertical direction.
  • the crankshaft 17 is connected to the orbiting scroll 26 by fitting the upper end portion of the crankshaft 17 into the upper end bearing 26c.
  • the crankshaft 17 is supported by the upper bearing 32 and the lower bearing 60.
  • the crankshaft 17 has a main oil supply passage 61 extending in its axial direction.
  • the upper end of the main oil supply passage 61 communicates with an oil chamber 67 formed by the upper end surface of the crankshaft 17 and the lower surface of the second end plate 26a.
  • the oil chamber 67 communicates with the sliding surface 24d and the oil groove 24e through the oil supply hole 63 of the second end plate 26a, and finally communicates with the low pressure space S2 through the compression chamber 40.
  • the lower end of the main oil supply path 61 is connected to an oil supply pipe that is a pipe for supplying the lubricating oil stored in the oil reservoir space 10 a to the compression mechanism 15.
  • the crankshaft 17 has a first sub oil supply path 61a, a second sub oil supply path 61b, and a third sub oil supply path 61c branched from the main oil supply path 61.
  • the first sub oil supply path 61a, the second sub oil supply path 61b, and the third sub oil supply path 61c extend in the horizontal direction.
  • the first sub oil supply passage 61 a is open to the sliding surface between the crankshaft 17 and the upper end bearing 26 c of the orbiting scroll 26.
  • the second sub oil supply passage 61 b opens in the sliding surface between the crankshaft 17 and the upper bearing 32 of the housing 23.
  • the third sub oil supply passage 61 c is open on the sliding surface between the crankshaft 17 and the lower bearing 60.
  • the suction pipe 19 is a pipe for introducing the refrigerant of the refrigerant circuit from the outside of the casing 10 to the compression mechanism 15.
  • the suction pipe 19 is fitted into the upper wall portion 12 of the casing 10 in an airtight manner.
  • the suction pipe 19 penetrates the low pressure space S2 in the vertical direction.
  • the discharge pipe 20 is a pipe for discharging the compressed refrigerant from the high-pressure space S1 to the outside of the casing 10.
  • the discharge pipe 20 is fitted in the body casing part 11 of the casing 10 in an airtight manner.
  • the discharge pipe 20 penetrates the high-pressure space S1 in the horizontal direction.
  • FIG. 2 is a bottom view of the fixed scroll 24 viewed along the vertical direction.
  • FIG. 3 is a top view of the orbiting scroll 26 viewed along the vertical direction.
  • FIG. 4A is a diagram illustrating the configuration of the fixed scroll 24 of FIG. 4B is a diagram illustrating the configuration of the orbiting scroll 26 of FIG.
  • the load applied to the first wrap 24b increases toward the center of the first wrap 24b (that is, the start of winding of the first wrap 24b). For this reason, the thickness of the inner peripheral end of the first wrap 24b is thicker than the thickness of the outer peripheral end of the first wrap 24b. In the present embodiment, the thickness of the first wrap 24b is gradually increased from the outer peripheral side toward the inner peripheral side as a whole. The height of the first wrap 24b is constant.
  • the load applied to the second wrap 26b during the operation of the scroll compressor 101 becomes higher toward the center of the second wrap 26b (that is, the winding start of the second wrap 26b).
  • the thickness of the inner peripheral end of the second wrap 26b is thicker than the thickness of the outer peripheral end of the second wrap 26b.
  • the thickness of the second wrap 26b is gradually increased from the outer peripheral side toward the inner peripheral side as a whole. The height of the second wrap 26b is constant.
  • the height of the first wrap 24b is the same as the height of the second wrap 26b.
  • the average thickness of the second wrap 26b is thinner than the average thickness of the first wrap 24b. That is, the average thickness of the wrap having the larger linear expansion coefficient (that is, the second wrap 26b) is thinner than the average thickness of the wrap having the smaller linear expansion coefficient (that is, the first wrap 24b).
  • the thickness of the second wrap 26b is generally thinner than the thickness of the first wrap 24b. The difference between the thickness of the second wrap 26b and the thickness of the first wrap 24b is particularly largest at each inner peripheral end.
  • the fixed scroll 24 and the orbiting scroll 26 are both composed of iron-based members, the thickness of the first wrap 24b and the thickness of the second wrap 26b are different from each other as described above.
  • the low-temperature and low-pressure refrigerant before being compressed is supplied from the suction pipe 19 to the compression chamber 40 of the compression mechanism 15 via the main suction hole 24c.
  • the compression chamber 40 moves from the outer peripheral portion of the fixed scroll 24 toward the center portion while gradually reducing the volume.
  • the refrigerant in the compression chamber 40 is compressed to become a compressed refrigerant.
  • the temperature of the compression chamber 40 increases with the movement. In particular, when the refrigerant is compressed under a high load condition, the temperature rises more. As the temperature rises, the first wrap 24b and the second wrap 26b expand.
  • the average thickness of the entire second wrap 26b that is more easily affected by heat is thinner than the average thickness of the entire first wrap 24b. Therefore, the expansion amount due to heat of the second wrap 26b is suppressed. As a result, contact between the fixed scroll 24 and the orbiting scroll 26 can be suppressed.
  • the compressed refrigerant is discharged from the discharge hole 41 to the muffler space 45, and then discharged to the high-pressure space S1 via the first compressed refrigerant channel 46 and the second compressed refrigerant channel 48. Then, the compressed refrigerant descends the motor cooling passage 55 and reaches the high pressure space S ⁇ b> 1 below the drive motor 16. Then, the compressed refrigerant reverses the flow direction and raises the air gap between the other motor cooling passage 55 and the drive motor 16. Finally, the compressed refrigerant is discharged from the discharge pipe 20 to the outside of the scroll compressor 101.
  • the linear expansion coefficient of the orbiting scroll 26 is larger than the linear expansion coefficient of the fixed scroll 24. Further, in the fixed scroll 24 and the orbiting scroll 26, the average thickness of the entire first wrap 24b and the average thickness of the entire second wrap 26b are different from each other. Specifically, the average thickness of the entire second wrap 26b is thinner than the average thickness of the entire first wrap 24b.
  • the amount of thermal expansion of the first wrap 24b is calculated by the product of the amount of change in temperature, the original thickness of the first wrap 24b, and the linear expansion coefficient of the first wrap 24b.
  • the amount of expansion of the second wrap 26b due to heat is calculated by the product of the amount of change in temperature, the original thickness of the second wrap 26b, and the linear expansion coefficient of the second wrap 26b.
  • the amount of change in temperature is the difference between the temperature before operation of the scroll compressor 101 and the temperature during operation of the scroll compressor 101.
  • the second wrap 26b on the side having the larger linear expansion coefficient is formed thinner than the first wrap 24b on the side having the smaller linear expansion coefficient. Since the thickness of the second wrap 26b is formed in consideration of the difference in expansion amount due to the difference in linear expansion coefficient, the expansion amount of the second wrap 26b due to heat can be suppressed.
  • the second lap is formed thin in advance in anticipation of the amount of expansion due to heat, so that the contact between the fixed scroll 24 and the orbiting scroll 26 can be suppressed.
  • wear due to contact between the first wrap 24b and the second wrap 26b can be suppressed.
  • the linear expansion coefficient of the orbiting scroll 26 is in the range of 101% to 107% with respect to the linear expansion coefficient of the fixed scroll 24. That is, even when the difference between the linear expansion coefficient of the fixed scroll 24 and the linear expansion coefficient of the orbiting scroll 26 is relatively small, the difference is reflected in the thickness of the second wrap 26b without being ignored. Therefore, contact between the fixed scroll 24 and the orbiting scroll 26 can be suppressed.
  • the fixed scroll 24 and the orbiting scroll 26 compress a refrigerant containing more than 50% by weight of R32 as a refrigerant.
  • the refrigerant containing more than 50% by weight of R32 and the R410A refrigerant are compressed under the same conditions, the refrigerant containing more than 50% by weight of R32 has a higher temperature than the refrigerant of R410A. That is, the first wrap 24b and the second wrap 26b are more easily deformed. Even in this case, since the thickness of the second wrap 26b is set according to the difference in the linear expansion coefficient, the contact between the fixed scroll 24 and the orbiting scroll 26 can be suppressed.
  • FIG. 5A is a diagram illustrating another example of the configuration of the fixed scroll 24.
  • FIG. 5B is a diagram for explaining another example of the configuration of the orbiting scroll 26.
  • 5A and 5B the same components as those of the fixed scroll 24 shown in FIG. 4A and the orbiting scroll 26 shown in FIG. 4B are referenced for the fixed scroll 24 shown in FIG. 4A and the orbiting scroll 26 shown in FIG. 4B.
  • the same reference symbols as those used are used.
  • the magnitude relationship between the linear expansion coefficient of the fixed scroll 24 and the linear expansion coefficient of the orbiting scroll 26 is as already described.
  • the fixed scroll 24 of FIG. 5A is the same as the fixed scroll 24 of FIG. 4A.
  • the height of the inner peripheral end of the second wrap 26b is lower than the height of the outer peripheral end of the second wrap 26b.
  • the height of the second wrap 26b gradually decreases from the outer peripheral side toward the inner peripheral side.
  • the height of the second wrap 26b may be reduced stepwise from the outer peripheral side toward the inner peripheral side.
  • the average height of the second wrap 26b in FIG. 5B is lower than the average height of the first wrap 24b. That is, the average height of the wrap on the side with the larger linear expansion coefficient (that is, the second wrap 26b) is lower than the average height of the wrap on the side with the smaller linear expansion coefficient (that is, the first wrap 24b).
  • the difference between the height of the second wrap 26b and the height of the first wrap 24b is particularly largest at each inner peripheral end.
  • the average height of the entire first wrap 24b is different from the average height of the entire second wrap 26b.
  • the average height of the entire second wrap 26b is lower than the average height of the entire first wrap 24b. That is, the second wrap 26b on the side having a larger linear expansion coefficient is formed lower than the first wrap 24b on the side having a smaller linear expansion coefficient as a whole. Since the height of the second wrap 26b is formed in consideration of the difference in expansion amount due to the difference in linear expansion coefficient, the expansion amount of the second wrap 26b due to heat can be suppressed.
  • the second lap is formed in advance in anticipation of the amount of expansion due to heat, so that contact between the fixed scroll 24 and the orbiting scroll 26 can be suppressed.
  • wear due to contact between the first end plate 24a and the second wrap 26b can be suppressed.
  • FIG. 6A is a diagram for explaining another example of the configuration of the fixed scroll 24.
  • FIG. 6B is a diagram illustrating another example of the configuration of the orbiting scroll 26.
  • 6A and 6B the same components as those of the fixed scroll 24 shown in FIG. 4A and the orbiting scroll 26 shown in FIG. 4B are referenced for the fixed scroll 24 shown in FIG. 4A and the orbiting scroll 26 shown in FIG. 4B. The same reference symbols as those used are used.
  • the magnitude relationship between the linear expansion coefficient of the fixed scroll 24 and the linear expansion coefficient of the orbiting scroll 26 is as already described.
  • the fixed scroll 24 in FIG. 6A is the same as the fixed scroll 24 in FIG. 4A.
  • the thickness of the inner peripheral end of the second wrap 26b is thicker than the thickness of the outer peripheral end of the second wrap 26b.
  • the thickness of the second wrap 26b gradually increases from the outer peripheral side toward the inner peripheral side.
  • the height of the inner peripheral end of the second wrap 26b is lower than the height of the outer peripheral end of the second wrap 26b.
  • the height of the second wrap 26b gradually decreases from the outer peripheral side toward the inner peripheral side. Note that the height of the second wrap 26b may be reduced stepwise from the outer peripheral side toward the inner peripheral side.
  • the average thickness of the second wrap 26b is thinner than the average thickness of the first wrap 24b, and the average height of the second wrap 26b is lower than the average height of the first wrap 24b. That is, the average of the thickness and height of the wrap having the larger linear expansion coefficient (that is, the second wrap 26b) is the average of the thickness and height of the wrap having the smaller linear expansion coefficient (that is, the first wrap 24b). Smaller than each.
  • Each of the difference between the thickness of the second wrap 26b and the thickness of the first wrap 24b and the difference between the height of the second wrap 26b and the height of the first wrap 24b are particularly largest at the inner peripheral end.
  • the thickness and height of the second wrap 26b are formed in consideration of the difference in the expansion amount due to the difference in the linear expansion coefficient, so that the expansion amount due to heat of the second wrap 26b is suppressed. Can do. As a result, contact between the fixed scroll 24 and the orbiting scroll 26 can be suppressed.
  • the height of the first wrap 24b is constant, but the first wrap is within a range that satisfies the condition that the average height of the second wrap 26b is lower than the average height of the first wrap 24b.
  • the height of the wrap 24b may not be constant.
  • the height of the inner peripheral end of the first wrap 24b may be lower than the height of the outer peripheral end of the first wrap 24b.
  • the height of the first wrap 24b may gradually decrease from the outer peripheral side toward the inner peripheral side, or may decrease stepwise from the outer peripheral side toward the inner peripheral side.
  • the refrigerant flow path portion from the main suction hole 24c to the discharge hole 41 in the first end plate 24a may be formed in a step shape from the outer peripheral side toward the inner peripheral side.
  • the refrigerant flow path portion surrounded by the outer peripheral end from the center of the second wrap 26b of the second end plate 26a may be formed in a step shape from the outer peripheral side toward the inner peripheral side.
  • FIG. 7A is a diagram illustrating a first gap that is a gap between the first end plate 24a and the second lap 26b.
  • the horizontal axis indicates the angle from the center (that is, the start of winding) of the second wrap 26b
  • the vertical axis indicates the height of the first gap. That is, the distance between the first end plate 24a and the tip of the second wrap 26b is shown.
  • a first region 34a, a second region 34b, and a third region 34c are formed in order from the inner peripheral side in the refrigerant flow path portion 24f from the main suction hole 24c to the discharge hole 41 in the first end plate 24a. Has been.
  • the gap height h 1 indicates the distance between the tip of the second wrap 26b and the first region 34a.
  • Gap height h 2 indicates the distance between the tip and the second region 34b of the second lap 26b.
  • the clearance height h 3 indicates the distance between the tip of the second wrap 26b and the third region 34c.
  • the range from the center of the second wrap 26b to 540 ° is defined as the center of the second wrap 26b.
  • a range from 540 ° to the outer peripheral edge of the second wrap 26b is defined as a non-center portion.
  • a range from the center of the second wrap 26 b to 540 ° forms the central portion of the compression chamber 40.
  • a range from 540 ° to the outer peripheral end of the second wrap 26 b forms a non-central portion of the compression chamber 40.
  • the height of the refrigerant flow path portion 24f decreases from the outer peripheral side toward the inner peripheral side.
  • the height of the refrigerant flow path portion 24f is lowered stepwise. That is, the third region 34c, the second region 34b, and the first region 34a become lower in this order.
  • step portions are formed in the refrigerant flow path portion 24f. That is, step portions are formed at the boundary between the third region 34c and the second region 34b and at the boundary between the second region 34b and the first region 34a.
  • the height of the second lap 26b is constant.
  • the height of the first gap is increased from the outer peripheral side of the second wrap 26b toward the inner peripheral side.
  • the height of the first gap changes in a step shape.
  • the gap height h 1 is the largest and the gap height h 3 is the smallest.
  • the change rate of the height of the refrigerant flow path portion 26f can be regarded as the change rate of the first gap as it is.
  • the rate of change of the first gap between the inner peripheral end and the outer peripheral end in the center portion of the second wrap 26b is greater than the rate of change of the first gap between the inner peripheral end and the outer peripheral end in the non-center portion of the second wrap 26b. That is, while the height of the first gap is relatively large changes by the difference between the gap height h 1 and the gap height h 2 over the 540 ° from 0 °, the gap height over the 900 ° of 540 ° h 2 And only the difference between the gap height h 3 changes. In other words, the rate of change of the first gap at the center of the second lap 26b is locally increased.
  • the first gap in the central part of the second wrap 26b is set to be locally large in anticipation of the expansion of the second wrap 26b due to heat. Contact between the fixed scroll 24 and the orbiting scroll 26 at the center of the compression chamber 40 can be suppressed.
  • FIG. 7B is a diagram illustrating a second gap that is a gap between the first wrap 24b and the second end plate 26a.
  • the horizontal axis indicates the angle from the center (that is, the start of winding) of the first wrap 24b
  • the vertical axis indicates the height of the second gap. That is, the distance between the tip of the first wrap 24b and the second end plate 26a is shown.
  • the first region 36a, the second region 36b, and the third region are sequentially arranged from the inner peripheral side. 36c is formed.
  • the gap height h 4 indicates the distance between the tip of the first wrap 24b and the first region 36a.
  • the gap height h 5 indicates the distance between the tip of the first wrap 24b and the second region 36b.
  • the clearance height h 6 indicates the distance between the tip of the first wrap 24b and the third region 36c.
  • the range from the center of the first wrap 24b to 540 ° is defined as the center of the first wrap 24b.
  • a range from 540 ° to the outer peripheral edge of the first lap 24b is defined as a non-center portion.
  • a range from the center of the first wrap 24 b to 540 ° forms the center of the compression chamber 40.
  • a range from 540 ° to the outer peripheral end of the first wrap 24 b forms a non-central portion of the compression chamber 40.
  • the height of the refrigerant flow path portion 26f decreases from the outer peripheral side toward the inner peripheral side.
  • the height of the refrigerant flow path portion 26f is lowered stepwise. That is, the third region 36c, the second region 36b, and the first region 36a become lower in this order.
  • stepped portions are formed at the boundary between the third region 36c and the second region 36b and at the boundary between the second region 36b and the first region 36a.
  • the height of the first lap 24b is constant.
  • the height of the second gap is increased from the outer peripheral side of the first wrap 24b toward the inner peripheral side.
  • the height of the second gap changes in a step shape.
  • the gap height h 4 is the largest and the gap height h 6 is the smallest.
  • the change rate of the height of the refrigerant flow path portion 24f can be regarded as the change rate of the second gap as it is.
  • the rate of change of the second gap between the inner peripheral end and the outer peripheral end in the central portion of the first wrap 24b is larger than the rate of change of the second gap between the inner peripheral end and the outer peripheral end in the non-central portion of the first wrap 24b. That is, while the height of the second gap is relatively large changes by the difference between the gap height h 4 and the gap height h 5 toward 540 ° from 0 °, the gap height h 5 toward 900 ° from 540 ° And only the difference between the gap height h 6 changes. In other words, the rate of change of the second gap at the center of the first lap 24b is locally increased.
  • the second gap in the central part of the first wrap 24b is set to be locally large in anticipation of the expansion of the first wrap 24b due to heat. Contact between the fixed scroll 24 and the orbiting scroll 26 at the center of the compression chamber 40 can be suppressed.

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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

Cette invention concerne un compresseur à spirale qui supprime le contact entre deux éléments de spirale. Un compresseur à spirale (101) est équipé d'une spirale fixe (24) comprenant une première substance et d'une spirale orbitale (26) comprenant une seconde substance. La spirale fixe (24) possède un premier recouvrement en forme de spirale (24b). Ensemble, la spirale orbitale (26) et la spirale fixe (24) forment une chambre de compression. La spirale orbitale (26) comporte un second recouvrement en forme de spirale (26b). La seconde substance diffère de la première substance. Le coefficient de dilatation linéaire de la seconde substance est supérieur au coefficient de dilatation linéaire de la première substance. L'épaisseur moyenne du second recouvrement nappe (26b) est globalement inférieure à l'épaisseur moyenne du premier recouvrement (24b) globalement.
PCT/JP2017/023834 2016-07-06 2017-06-29 Compresseur à spirale Ceased WO2018008495A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2016133796A JP2018003762A (ja) 2016-07-06 2016-07-06 スクロール圧縮機
JP2016-133796 2016-07-06

Publications (1)

Publication Number Publication Date
WO2018008495A1 true WO2018008495A1 (fr) 2018-01-11

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Country Link
JP (1) JP2018003762A (fr)
WO (1) WO2018008495A1 (fr)

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0719187A (ja) * 1993-07-01 1995-01-20 Hitachi Ltd スクロール流体機械
JPH0821380A (ja) * 1994-07-01 1996-01-23 Mitsubishi Electric Corp スクロール流体機械
JPH08326668A (ja) * 1995-06-01 1996-12-10 Matsushita Electric Ind Co Ltd スクロール圧縮機
JP2002155877A (ja) * 2000-11-22 2002-05-31 Matsushita Electric Ind Co Ltd スクロール圧縮機
WO2014155646A1 (fr) * 2013-03-29 2014-10-02 日立アプライアンス株式会社 Compresseur à spirales
JP2016003645A (ja) * 2014-06-19 2016-01-12 日立アプライアンス株式会社 スクロール圧縮機および空気調和機

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0719187A (ja) * 1993-07-01 1995-01-20 Hitachi Ltd スクロール流体機械
JPH0821380A (ja) * 1994-07-01 1996-01-23 Mitsubishi Electric Corp スクロール流体機械
JPH08326668A (ja) * 1995-06-01 1996-12-10 Matsushita Electric Ind Co Ltd スクロール圧縮機
JP2002155877A (ja) * 2000-11-22 2002-05-31 Matsushita Electric Ind Co Ltd スクロール圧縮機
WO2014155646A1 (fr) * 2013-03-29 2014-10-02 日立アプライアンス株式会社 Compresseur à spirales
JP2016003645A (ja) * 2014-06-19 2016-01-12 日立アプライアンス株式会社 スクロール圧縮機および空気調和機

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