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WO2018131436A1 - Compresseur doté de support d'arbre - Google Patents

Compresseur doté de support d'arbre Download PDF

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Publication number
WO2018131436A1
WO2018131436A1 PCT/JP2017/046209 JP2017046209W WO2018131436A1 WO 2018131436 A1 WO2018131436 A1 WO 2018131436A1 JP 2017046209 W JP2017046209 W JP 2017046209W WO 2018131436 A1 WO2018131436 A1 WO 2018131436A1
Authority
WO
WIPO (PCT)
Prior art keywords
shaft support
compressor
rotor
compression mechanism
dimension
Prior art date
Application number
PCT/JP2017/046209
Other languages
English (en)
Japanese (ja)
Inventor
直人 富岡
Original Assignee
ダイキン工業株式会社
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 ダイキン工業株式会社 filed Critical ダイキン工業株式会社
Publication of WO2018131436A1 publication Critical patent/WO2018131436A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • 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
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
    • 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

  • Patent Document 1 Japanese Patent Application Laid-Open No. 2006-144731 describes that a phenomenon occurs in a reciprocating compressor that the torque greatly fluctuates during a period in which the crankshaft rotates once. Such torque fluctuations cause vibrations or noise. Similar problems can occur with other types of compressors, such as rotary compressors.
  • One solution to reduce vibrations due to torque fluctuations is to ensure rotational inertia by enlarging the rotor of the motor and increasing the weight of the rotor.
  • An object of the present invention is to suppress the vibration of the compressor.
  • the compressor according to the first aspect of the present invention includes a casing, a motor, a crankshaft, a compression mechanism, and a shaft support.
  • the casing has a cylindrical portion having an inner diameter of a first dimension.
  • the motor has a rotor having an outer diameter of the second dimension.
  • the crankshaft is fixed to the rotor and rotates around the rotation axis.
  • the compression mechanism generates a high-pressure refrigerant by compressing the low-pressure refrigerant.
  • the shaft support part rotatably supports the crankshaft.
  • the ratio of the first dimension to the second dimension is 1.8 or less.
  • the total length of the shaft support portion in the extending direction of the rotation axis is 10 mm or more and 40 mm or less.
  • the overall length of the shaft support is short. Therefore, interference between the rotor and the shaft support, which is an obstacle when the rotor and the shaft support are arranged close to each other, is less likely to occur, which is convenient for suppressing vibration of the compressor.
  • a compressor according to a second aspect of the present invention is the compressor according to the first aspect, wherein the rotor has a first surface far from the compression mechanism and a second surface close to the compression mechanism. The end closest to the first surface of the shaft support is farther from the first surface by a predetermined distance than the second surface. The predetermined distance is 3 mm or less.
  • the compressor which concerns on the 3rd viewpoint of this invention WHEREIN: The compressor which concerns on a 2nd viewpoint WHEREIN: The location which opposes the edge part of a shaft support part in the 2nd surface of a rotor is 1st surface compared with a 2nd surface. A recess is formed which is defined by a surface located closer to the.
  • the rotor and the compression mechanism can be arranged close to each other without interfering with each other due to the presence of the recess. Therefore, since the distance from the fixed part to the casing of the shaft support or the compression mechanism to the center of gravity of the rotor is shorter, vibration of the compressor can be further suppressed.
  • the distance between the end portion and the second surface is short. This means that the surface that defines the concave portion and the end portion of the shaft support portion are appropriately separated. Therefore, the freedom degree of arrangement
  • positioning can be increased about both of them under various restrictions.
  • the compressor according to the fifth aspect of the present invention is the compressor according to any one of the second to fourth aspects, wherein the rotor has a rotor core.
  • the first surface is the surface farthest from the compression mechanism in the rotor core.
  • the second surface is the surface closest to the compression mechanism in the rotor core.
  • the first surface and the second surface belong to the rotor core. Therefore, the distance from the fixed part to the casing of the shaft support or the compression mechanism to the center of gravity of the rotor can be further shortened.
  • the compressor according to the sixth aspect of the present invention is the compressor according to any one of the first to fifth aspects, wherein the first dimension is not less than 60 mm and not more than 120 mm.
  • the total length of the shaft support portion is 37 mm or less.
  • the overall length of the shaft support is even shorter. Therefore, since the distance from the fixed part to the shaft support or the casing of the compression mechanism to the center of gravity of the rotor is further short, vibration of the compressor can be further suppressed.
  • the shaft support portion exists only on the compression mechanism side with respect to the rotor.
  • the shaft support portion does not exist on the opposite side of the compression mechanism with respect to the rotor. Therefore, cost reduction of the compressor can be achieved.
  • the compression mechanism and the shaft support are very close to each other. Therefore, the rotation of the piston in the compression mechanism is stabilized.
  • the shaft support portion is directly fixed to the cylindrical portion.
  • the shaft support is directly fixed to the casing. Therefore, since the fixing part which fixes the assembly of a compression mechanism and a shaft support part to a casing is close to a rotor, the vibration of a compressor can be suppressed more.
  • the compression mechanism is directly fixed to the casing. Therefore, the phenomenon that the compression mechanism having a large weight swings can be suppressed.
  • the compressor according to the thirteenth aspect of the present invention is a rotary compressor in the compressor according to any one of the first to twelfth aspects.
  • the compressor according to the first aspect, the second aspect, the third aspect, the sixth aspect, the seventh aspect, the eleventh aspect, and the thirteenth aspect of the present invention can suppress the vibration of the compressor.
  • the distance from the fixed portion of the shaft support or the compression mechanism to the casing to the center of gravity of the rotor can be further shortened.
  • the compressor according to the eighth aspect of the present invention can reduce the cost of the compressor.
  • the revolution of the piston in the compression mechanism is stabilized.
  • FIG. 3 is a plan view of a cylindrical portion 11 and a motor 20 of the compressor 5.
  • FIG. 3 is a cross-sectional view of a stator 21 of the compressor 5.
  • FIG. 3 is a cross-sectional view of a rotor 22 of the compressor 5.
  • FIG. 3 is a partial cross-sectional view of the compressor 5.
  • FIG. It is sectional drawing of the compressor 5A which concerns on the modification of this invention. It is sectional drawing of the rotor 22 of 5 A of compressors. It is a fragmentary sectional view of compressor 5A.
  • FIG. 1 shows a compressor 5 according to an embodiment of the present invention.
  • the compressor 5 is a rotary compressor that is mounted on a refrigerating apparatus such as an air conditioner or a refrigerator and compresses a gaseous refrigerant.
  • the compressor 5 includes a casing 10, a motor 20, a crankshaft 30, a compression mechanism 40, a shaft support 61, and an auxiliary shaft support 62.
  • the casing 10 accommodates other components of the compressor 5 and can withstand the high pressure of the refrigerant.
  • the casing 10 has a cylindrical part 11, an upper part 12, and a lower part 13.
  • the cylindrical portion 11 is the largest of the components of the casing 10 and has a cylindrical shape. Both the upper part 12 and the lower part 13 are joined to the cylindrical part 11.
  • an oil storage part 14 for storing the refrigerator oil 141 is provided below the casing 10.
  • the motor 20 generates mechanical power using electric power supplied from the terminal 17 via a lead wire (not shown).
  • the motor 20 has a stator 21 and a rotor 22. As shown in FIG. 2, the stator 21 has a cylindrical shape and is fixed to the cylindrical portion 11 of the casing 10. A gap 23 is formed between the stator 21 and the rotor 22. The gap 23 functions as a refrigerant passage.
  • the stator 21 has a stator core 21a, an insulator 21b, and a winding 21c.
  • Stator core 21a consists of a plurality of laminated steel plates.
  • a space 213 for arranging the rotor 22 is formed in the stator core 21a.
  • the insulator 21b is made of resin.
  • the insulators 21b are provided on the stator core upper surface 211 and the stator core lower surface 212, respectively.
  • the winding 21c is for generating an alternating magnetic field, and is wound around a laminate of the stator core 21a and the insulator 21b.
  • the rotor 22 has a rotor core 22a, permanent magnets 22b, end plates 22c, balance weights 22d, and caulking pins 22e.
  • the rotor core 22a is composed of a plurality of laminated steel plates.
  • the rotor core 22 a has a first surface 221 farthest from the compression mechanism 40 and a second surface 222 closest to the compression mechanism 40.
  • the first surface 221 and the second surface 222 are planes parallel to each other.
  • a space 223 for fixing the crankshaft 30 is formed in the rotor core 22a.
  • the permanent magnet 22b is for rotating the entire rotor 22 by interacting with the AC magnetic field generated by the winding 21c.
  • the permanent magnet 22b is disposed in the cavity 224 of the rotor core 22a.
  • the end plates 22c are provided on the first surface 221 and the second surface 222, respectively, and prevent the permanent magnet 22b from going out of the cavity 224.
  • the balance weight 22d is for adjusting the center of gravity of the rotating body composed of the rotor 22 and the components that rotate accompanying the rotor 22.
  • the balance weight 22d is provided on one of the end plates 22c.
  • the caulking pin 22e fixes the end plate 22c or the balance weight 22d to the rotor core 22a.
  • crankshaft 30 is for transmitting the power generated by the motor 20 to the compression mechanism 40.
  • the crankshaft 30 rotates around the rotation axis RA.
  • the crankshaft 30 has a main shaft portion 31 and an eccentric portion 32. A part of the main shaft portion 31 is fixed to the rotor 22.
  • the eccentric part 32 is eccentric with respect to the rotational axis RA.
  • the compression mechanism 40 is for compressing a low-pressure refrigerant to generate a high-pressure refrigerant.
  • the compression mechanism 40 includes a cylinder 41 and a piston 42.
  • the cylinder 41 is a metal member, and has an internal space that communicates with the outside of the casing 10 via the suction pipe 15.
  • the piston 42 is a cylindrical metal member that is smaller than the cylinder 41.
  • the piston 42 is attached to the eccentric part 32.
  • the eccentric portion 32 and the piston 42 are disposed in the internal space of the cylinder 41.
  • a compression chamber 43 is defined by the cylinder 41, the piston 42, a shaft support 61 and an auxiliary shaft support 62 described later.
  • the volume of the compression chamber 43 is increased or decreased by the revolution of the piston 42, whereby the low-pressure refrigerant is compressed and high-pressure refrigerant is generated.
  • the high-pressure refrigerant is discharged from a passage 44 formed in the shaft support portion 61 to a muffler chamber described later.
  • the passage 44 is provided with a discharge valve (not shown). The discharge valve suppresses the high-pressure refrigerant from flowing back from the muffler chamber to the compression chamber 43.
  • the shaft support portion 61 rotatably supports the main shaft portion 31 above the eccentric portion 32.
  • the shaft support 61 also has a function of closing the upper side of the internal space of the cylinder 41.
  • the shaft support portion 61 is fixed to the cylindrical portion 11 at the fixing point F.
  • the fixing method is, for example, welding or shrink fitting.
  • a muffler 63 is attached to the shaft support 61.
  • the shaft support 61 and the muffler 63 define a muffler chamber.
  • the high-pressure refrigerant passes through the passage 44 every time the piston 42 makes one revolution. Such intermittent passage of the high-pressure refrigerant passage 44 can cause noise.
  • the muffler 63 smoothes the pressure fluctuation of the gas refrigerant in the muffler chamber, thereby reducing noise.
  • the high-pressure refrigerant is discharged from a discharge hole 64 formed in the muffler 63.
  • Auxiliary shaft support 62 The auxiliary shaft support portion 62 rotatably supports the main shaft portion 31 below the eccentric portion 32.
  • the auxiliary shaft support part 62 also has a function of closing the lower side of the internal space of the cylinder 41.
  • FIG. 5 shows the dimensions of each part of the compressor 5.
  • the first dimension D1 is the inner diameter of the cylindrical portion 11 of the casing 10.
  • the first dimension D1 is not less than 60 mm and not more than 120 mm.
  • the second dimension D2 is the outer diameter of the rotor core 22a of the rotor 22.
  • the ratio D1 / D2 of the first dimension D1 to the second dimension D2 is designed to be 1.8 or less.
  • the first dimension D1 is 90 mm and the second dimension is 50 mm.
  • the ratio D1 / D2 may be designed to be “less than 1.8”.
  • the end 611 closest to the first surface 221 in the pivot support 61 is farther from the first surface 221 by a predetermined distance H than the second surface 222.
  • This predetermined distance H is, for example, 2 mm or less.
  • the predetermined distance H is, for example, 3 mm or less.
  • the total length L of the shaft support 61 in the extending direction of the rotation axis RA is set short.
  • the total length L is 10 mm or more and 40 mm or less, preferably 10 mm or more and 37 mm or less.
  • the shaft support 61 continuously contacts the crankshaft 30 over the entire length L.
  • the overall length L of the shaft support 61 is short. Therefore, interference between the rotor 22 and the shaft support portion 61 that hinders the rotor 22 and the shaft support portion 61 from being arranged close to each other is unlikely to occur, which is convenient for suppressing vibration of the compressor 5.
  • the first surface 221 and the second surface 222 belong to the rotor core 22a.
  • parts other than the rotor core 22a which is the main part that determines the center of gravity of the rotor 22, are not involved in defining the separation distance between the end 611 of the shaft support 61 and the rotor core 22a. Therefore, the distance from the fixing portion F of the shaft support 61 to the casing 10 to the center of gravity of the rotor 22 can be further shortened.
  • the first dimension D1 is not less than 60 mm and not more than 120 mm. That is, the compressor 5 has a small-diameter casing 10. Therefore, vibration can be suppressed in the small compressor 5.
  • the shaft support 61 contacts the crankshaft 30 over the entire length L. Therefore, the overall length L of the shaft support portion 61 can be shortened compared to the shaft support structure having a non-contact portion.
  • a noise suppression measure can be applied to the compressor 5 which is a rotary compressor that easily generates vibration due to torque fluctuation during rotation.
  • FIG. 6 shows a compressor 5A according to a first modification of the above-described embodiment.
  • the compressor 5A differs from the above-described embodiment in the structure of the rotor 22.
  • a recess 25 is formed in the second surface 222 of the rotor core 22a.
  • the recess 25 is defined by the bottom surface 251 and the side surface 252. Both the bottom surface 251 and the side surface 252 are surfaces located closer to the first surface 221 than the second surface 222.
  • the recess 25 may be defined by a curved surface having a radial or arc-shaped cross section, for example, instead of this configuration.
  • the recessed part 25 is located in the location facing the edge part 611 of the axial support part 61 in the 2nd surface 222 of the rotor core 22a.
  • the end 611 closest to the first surface 221 in the shaft support 61 is farther from the first surface 221 by a predetermined distance H than the second surface 222.
  • the predetermined distance H can be a negative number.
  • the predetermined distance H that is a negative number means a configuration in which the end 611 enters the recess 25.
  • the predetermined distance H is, for example, not less than ⁇ 2 mm and not more than 2 mm. Alternatively, the predetermined distance H is, for example, not less than ⁇ 3 mm and not more than 3 mm.
  • the rotor 22 and the compression mechanism 40 can be arranged close to each other without interfering with each other. Therefore, since the distance from the fixing part F of the shaft support 61 to the casing 10 to the center of gravity of the rotor 22 is shorter, vibration of the compressor 5 can be further suppressed.

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

Abstract

L'invention concerne un compresseur (5) comprenant : un carter (10) ; un moteur (20) ; un vilebrequin (30) ; un mécanisme de compression (40) ; et un support d'arbre (61). Le carter (10) comporte une partie cylindrique (11) présentant un diamètre interne d'une première dimension (D1). Le moteur (20) comporte un rotor (22) présentant un diamètre externe d'une seconde dimension (D2). Le vilebrequin (30) est fixé au rotor (22) et tourne autour d'un axe de rotation (RA). Le mécanisme de compression (40) comprime un fluide frigorigène à basse pression afin de produire un fluide frigorigène à haute pression. Le support d'arbre (61) porte le vilebrequin (30) de manière rotative. Le rapport (D1/D2) de la première dimension (D1) à la seconde dimension (D2) est inférieur ou égal à 1,8. La longueur totale (L) du support d'arbre (61), dans la direction d'extension de l'axe de rotation (RA), est comprise entre 10 et 40 mm.
PCT/JP2017/046209 2017-01-11 2017-12-22 Compresseur doté de support d'arbre WO2018131436A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2017-002548 2017-01-11
JP2017002548A JP2020037869A (ja) 2017-01-11 2017-01-11 軸支部を備える圧縮機

Publications (1)

Publication Number Publication Date
WO2018131436A1 true WO2018131436A1 (fr) 2018-07-19

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ID=62839900

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2017/046209 WO2018131436A1 (fr) 2017-01-11 2017-12-22 Compresseur doté de support d'arbre

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JP (1) JP2020037869A (fr)
WO (1) WO2018131436A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110873053A (zh) * 2018-08-30 2020-03-10 广东美芝制冷设备有限公司 压缩机和具有该压缩机的制冷设备
US20220099080A1 (en) * 2019-02-13 2022-03-31 Mitsubishi Electric Corporation Compressor and air conditioner

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS4930166B1 (fr) * 1969-05-19 1974-08-10
JPS559586U (fr) * 1978-07-06 1980-01-22
JP2009002352A (ja) * 2008-08-22 2009-01-08 Daikin Ind Ltd 圧縮機
JP2009275645A (ja) * 2008-05-16 2009-11-26 Mitsubishi Electric Corp ロータリ圧縮機
WO2014025025A1 (fr) * 2012-08-09 2014-02-13 東芝キヤリア株式会社 Compresseur rotatif et appareil à cycle frigorifique
WO2015056364A1 (fr) * 2013-10-15 2015-04-23 パナソニックＩｐマネジメント株式会社 Compresseur

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS4930166B1 (fr) * 1969-05-19 1974-08-10
JPS559586U (fr) * 1978-07-06 1980-01-22
JP2009275645A (ja) * 2008-05-16 2009-11-26 Mitsubishi Electric Corp ロータリ圧縮機
JP2009002352A (ja) * 2008-08-22 2009-01-08 Daikin Ind Ltd 圧縮機
WO2014025025A1 (fr) * 2012-08-09 2014-02-13 東芝キヤリア株式会社 Compresseur rotatif et appareil à cycle frigorifique
WO2015056364A1 (fr) * 2013-10-15 2015-04-23 パナソニックＩｐマネジメント株式会社 Compresseur

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110873053A (zh) * 2018-08-30 2020-03-10 广东美芝制冷设备有限公司 压缩机和具有该压缩机的制冷设备
US20220099080A1 (en) * 2019-02-13 2022-03-31 Mitsubishi Electric Corporation Compressor and air conditioner
US11976657B2 (en) * 2019-02-13 2024-05-07 Mitsubishi Electric Corporation Compressor and air conditioner

Also Published As

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