WO2016151769A1 - 回転式密閉型圧縮機 - Google Patents

回転式密閉型圧縮機 Download PDF

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Publication number
WO2016151769A1
WO2016151769A1 PCT/JP2015/058946 JP2015058946W WO2016151769A1 WO 2016151769 A1 WO2016151769 A1 WO 2016151769A1 JP 2015058946 W JP2015058946 W JP 2015058946W WO 2016151769 A1 WO2016151769 A1 WO 2016151769A1
Authority
WO
WIPO (PCT)
Prior art keywords
shaft
cylinder
bearing
compression chamber
hermetic compressor
Prior art date
Application number
PCT/JP2015/058946
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
佐藤　幸一
Original Assignee
三菱電機株式会社
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 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to CZ2017-673A priority Critical patent/CZ307910B6/cs
Priority to PCT/JP2015/058946 priority patent/WO2016151769A1/ja
Priority to JP2017507224A priority patent/JPWO2016151769A1/ja
Priority to CN201610096224.6A priority patent/CN106014991B/zh
Priority to CN201620133087.4U priority patent/CN205423162U/zh
Publication of WO2016151769A1 publication Critical patent/WO2016151769A1/ja

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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
    • 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
    • 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
    • F04C18/3562—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 the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation
    • F04C18/3564—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 the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the working space, being surfaces of revolution
    • 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
    • F04C18/32—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 both the movement defined in group F04C18/02 and relative reciprocation between the co-operating members
    • F04C18/324—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 both the movement defined in group F04C18/02 and relative reciprocation between the co-operating members with vanes hinged to the inner member and 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
    • F04C29/0042—Driving elements, brakes, couplings, transmissions specially adapted for pumps
    • F04C29/005—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
    • F04C29/0071—Couplings between rotors and input or output shafts acting by interengaging or mating parts, i.e. positive coupling of rotor and shaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/60—Shafts

Definitions

  • the present invention relates to a rotary hermetic compressor for compressing refrigerant gas used in a refrigeration cycle.
  • the value obtained by subtracting the eccentric amount of the eccentric shaft relative to the center of the main shaft or the sub shaft from the radius of the eccentric shaft is the radius of the main shaft or the sub shaft. Must be the same or larger. If the value obtained by subtracting the amount of eccentricity from the radius of the eccentric shaft is smaller than the radius of the main shaft or the sub shaft, trying to fit the piston into the eccentric shaft by passing through the main shaft or the sub shaft, The outer diameter of the eccentric shaft and the inner diameter of the piston interfere and cannot be fitted.
  • the amount of eccentricity is such that the value obtained by subtracting the amount of eccentricity from the eccentric shaft radius is smaller than the radius of the main shaft or the sub shaft due to the restriction at the time of fitting the piston to the eccentric shaft as described above. There was a problem that it could not be increased.
  • the value obtained by subtracting the eccentric amount from the radius of the eccentric shaft is the same as the radius of the auxiliary shaft by making the diameter of the crankshaft auxiliary shaft smaller than the diameter of the main shaft.
  • a hermetic compressor that is larger or larger is shown (see, for example, FIGS. 1 and 7 of Patent Document 1).
  • the hermetic compressor described in Patent Document 1 has a high possibility that the bearing portion will seize due to a decrease in the diameter of the auxiliary shaft, and also increases the displacement volume, that is, increases the length of the eccentric shaft. Therefore, there is a problem that bending is likely to occur. If the length of the eccentric shaft is increased to increase the displacement volume, the eccentric shaft that receives the gas load in the compression chamber will be microscopically bent, but if the eccentric shaft is largely bent, The countershaft will be tilted, the oil film thickness in the bearing will be reduced, the lubrication of the bearing will deteriorate, the shaft and bearing will seize during compressor operation, and the compressor will stop operating, making it impossible to restart. There is a problem of fear. With respect to these problems, the technique described in Patent Document 1 does not give consideration to the relationship between the length of the auxiliary bearing and the length of the eccentric shaft.
  • the present invention has been made to solve the above-described problems, and increases the displacement volume of the compressor and enables high output while maintaining the reliability so that the seizure of the auxiliary bearing does not occur.
  • An object is to provide a rotary hermetic compressor.
  • a rotary hermetic compressor houses an electric motor in an upper part of a hermetic container and a compression mechanism connected to the lower part of the electric motor by a crankshaft, and the compression mechanism is fixed to the electric motor.
  • a crankshaft comprising a main shaft, a subshaft having the same central axis as the main shaft, and an eccentric shaft formed between the main shaft and the subshaft and eccentric with respect to the central axis of the main shaft;
  • a rolling piston that fits into an eccentric shaft, a cylinder that is inserted into a cylindrical space inside the rolling piston, and is fixed in a sealed container, and an inner surface of the cylinder and the rolling piston that swings in the cylinder
  • a vane that defines a compression chamber formed by the outer periphery of the suction side compression chamber and the discharge side compression chamber, a main bearing that closes the axial opening of the cylinder from above and supports the rotation of the main shaft,
  • the cylinder A secondary bearing that closes the axial opening from below and supports the rotation of the secondary
  • the displacement volume of the compressor is increased while maintaining the reliability that does not cause the seizure of the bearing.
  • a rotary hermetic compressor that enables output can be provided.
  • FIG. 1 is a longitudinal sectional view of a rotary hermetic compressor according to a first embodiment.
  • 2 is a schematic diagram illustrating a piston and a vane type compression chamber according to Embodiment 1.
  • FIG. 3 is a diagram showing a crankshaft of the rotary hermetic compressor according to the first embodiment. It is a figure which shows the relationship between the value of l / L and the generation
  • FIG. 1 is a longitudinal sectional view of a rotary hermetic compressor 100 according to the present embodiment.
  • the rotary hermetic compressor 100 includes a motor 2 composed of a stator 2a and a rotor 2b, and a motor 2 in a hermetic container 1 composed of an upper container 1a and a lower container 1b that seals a high-pressure atmosphere.
  • the compression mechanism part 3 to be driven is accommodated.
  • Rotational force of the electric motor 2 is transmitted to the compression mechanism unit 3 through the crankshaft 4.
  • the crankshaft 4 is formed between a main shaft 4 a fixed to the rotor 2 b of the electric motor 2, a sub shaft 4 b provided on the opposite side of the main shaft 4 a across the compression mechanism portion 3, and the main shaft 4 a and the sub shaft 4 b.
  • the eccentric shaft 4c The central axis of the sub shaft 4b is the same as the main shaft 4a.
  • the dimensional relationship of the outer diameters of the main shaft 4a, the sub shaft 4b, and the eccentric shaft 4c is obtained by subtracting the eccentric amount of the eccentric shaft from the center of the main shaft and the sub shaft from the radius of the eccentric shaft 4c. Is set to be the same as or larger than.
  • An oil supply hole is provided in the crankshaft 4.
  • the main bearing 5 is fitted to the main shaft 4a of the crankshaft 4 with a clearance for sliding, and rotatably supports the main shaft 4a.
  • the auxiliary bearing 6 is fitted to the auxiliary shaft 4b of the crankshaft 4 with a clearance for sliding, and rotatably supports the auxiliary shaft 4b.
  • the axial length of the main bearing 5 is set as long as possible in the space between the compression mechanism 3 and the electric motor 2.
  • the auxiliary bearing 6 is set in the space below the compression mechanism portion 3 as long as possible in accordance with the axial length of the auxiliary shaft 4b.
  • FIG. 2 is a schematic view showing a piston and a vane type compression chamber according to the present embodiment.
  • the compression mechanism unit 3 includes a cylinder 7 and a vane 13.
  • the cylinder 7 is fixed to the inner periphery of the sealed container 1.
  • the cylinder 7 has a cylindrical internal space, and a rolling piston 8 that is rotatably fitted to the eccentric shaft 4c of the crankshaft 4 is disposed in the internal space.
  • the vane 13 moves along a groove provided in the cylinder 7.
  • the vane 13 follows the movement of the rolling piston 8 oscillating inside the cylinder 7, and the compression chamber 9 formed by the inner wall of the cylinder 7 and the rolling piston 8 is replaced with a suction side compression chamber 9 a and a discharge side compression chamber. 9b.
  • An accumulator 12 is provided adjacent to the sealed container 1.
  • the suction connection pipe 10 connects the cylinder 7 and the accumulator 12.
  • the refrigerant gas compressed by the rolling piston 8 and the vane 13 fitted to the eccentric shaft 4c of the crankshaft 4 that rotates eccentrically by the rotation of the crankshaft 4 in the cylinder 7 is discharged into the hermetic container 1 and discharged from the discharge pipe. 11 is sent to a refrigeration cycle such as a refrigeration air conditioner.
  • FIG. 3 is a diagram illustrating a crankshaft of the rotary hermetic compressor 100 according to the present embodiment.
  • the central axes of the main shaft 4a and the sub shaft 4b are coaxial, and the central axis of the eccentric shaft 4c is deviated from the central axes of the main shaft 4a and the sub shaft 4b.
  • the length l of the eccentric shaft 4c of the crankshaft 4 and the length L of the auxiliary shaft 4b are 1 / L, the length is 0.75 or less.
  • the rotary hermetic compressor 100 is configured as described above, for example, when the displacement volume is increased in order to increase the capacity of the compressor, if the length of the eccentric shaft 4c is increased, the gas in the compression chamber 9 is increased.
  • the eccentric shaft 4c that receives the load bends microscopically.
  • the auxiliary shaft 4b supported by the inner diameter of the auxiliary bearing 6 tilts. As a result, a portion where the oil film thickness of the contact portion between the sub bearing 6 and the sub shaft 4b becomes thin is generated, and the lubricating performance of the sub bearing 6 is lowered.
  • the ratio l / L of the length L of the countershaft 4b of the crankshaft 4 to the length l of the eccentric shaft is set to 0.75 or less, when the gas load is received.
  • the rigidity of the crankshaft 4 can be increased, and the auxiliary shaft 4b can be prevented from being inclined on the inner diameter side of the auxiliary bearing 6.
  • FIG. 4 is a diagram showing the relationship between the value of 1 / L and the occurrence of surface roughness of the countershaft in the rotary hermetic compressor 100 according to the present embodiment.
  • o indicates that the contact surface of the sub shaft 4b with the sub bearing is not rough
  • x indicates that the contact surface of the sub shaft with the sub bearing is rough.
  • the longitudinal elastic modulus of the material of the crankshaft 4 of the rotary hermetic compressor 100 is 150,000 to 220,000 N / mm 2 .
  • the lower the I / L value the higher the rigidity of the crankshaft 4 and the more advantageous for the seizure of the bearing.
  • each part of the crankshaft 4 is as follows.
  • the length l of the auxiliary shaft 4b is 10 mm to 100 mm, and the diameter of the auxiliary shaft 4b is 10 mm to 50 mm.
  • the lengths of the auxiliary shaft 4b and the auxiliary bearing 6 affect the magnitude of the pressure caused by the load supported by the bearing portion, and the shorter the length, the higher the pressure and the more likely that seizure will occur.
  • the diameters of the sub shaft 4b and the sub bearing 6 affect the relative speed of the contact surface between the sub shaft 4b and the sub bearing 6, and the higher the relative speed, the more likely the bearing portion will seize. The smaller the diameter of the sub shaft 4b and the sub bearing 6, the higher the relative speed.
  • the diameter of the eccentric shaft 4c is 20 to 80 mm.
  • the diameter of the eccentric shaft 4c affects the displacement volume. The larger the displacement shaft, the larger the displacement volume, and the larger the load received by the eccentric shaft 4c. If the load is large, there is a high possibility that the bearing portion will be seized.
  • the outer diameter of the auxiliary shaft 4b is set to be smaller by about 0 to 5 mm in diameter than the outer diameter of the main shaft 4a. By setting the sub shaft 4b to be smaller than the main shaft 4a, the eccentric amount of the eccentric shaft 4c can be increased as compared with the case where the main shaft 4a and the sub shaft 4b are configured with the same diameter, and the displacement volume Can be increased.
  • the value obtained by subtracting the eccentric amount of the eccentric shaft 4c with respect to the center of the auxiliary shaft 4b from the radius of the eccentric shaft 4c needs to be the same as or larger than the radius of the auxiliary shaft 4b. It may be smaller than the radius. If this condition is satisfied, the rolling piston 8 can be assembled from the auxiliary shaft 4b side.
  • the operating conditions (the number of revolutions, the refrigerant used, and the lubricating oil) of the rotary hermetic compressor 100 are the same as those of the rotary hermetic compressor 100 used in general refrigerators.
  • the ratio l / L of the length L of the auxiliary shaft 4b of the crankshaft 4 to the length l of the eccentric shaft is set to 0.75 or less.
  • the bending due to the gas load applied to the eccentric shaft 4c portion of the shaft 4 can be suppressed.
  • FIG. 5 is a schematic view showing a swing type compression chamber 9. A portion corresponding to the rolling piston 8 and the vane 13 is integrated with the compression mechanism portion 3 described above to form a swing type rolling piston 8a.
  • the cylinder 7 is also structured in accordance with the swing type rolling piston 8a.
  • the refrigerant that is sucked and compressed by the rotary hermetic compressor 100 is a gas that is a compressible fluid, but when the rotary hermetic compressor 100 is started up or at a low ambient temperature, A liquid refrigerant that is an incompressible fluid may be sucked into the rotary hermetic compressor 100 from the refrigeration cycle side.
  • the liquid refrigerant, which is an incompressible fluid is sucked and compressed, the pressure inside the compression chamber 9 rapidly rises, and accordingly, an excessive load is also applied to the main bearing 5 and the sub-bearing 6 that receive the compression load. It will be.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
PCT/JP2015/058946 2015-03-24 2015-03-24 回転式密閉型圧縮機 WO2016151769A1 (ja)

Priority Applications (5)

Application Number Priority Date Filing Date Title
CZ2017-673A CZ307910B6 (cs) 2015-03-24 2015-03-24 Hermetický rotační kompresor
PCT/JP2015/058946 WO2016151769A1 (ja) 2015-03-24 2015-03-24 回転式密閉型圧縮機
JP2017507224A JPWO2016151769A1 (ja) 2015-03-24 2015-03-24 回転式密閉型圧縮機
CN201610096224.6A CN106014991B (zh) 2015-03-24 2016-02-22 旋转式密闭型压缩机
CN201620133087.4U CN205423162U (zh) 2015-03-24 2016-02-22 旋转式密闭型压缩机

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2015/058946 WO2016151769A1 (ja) 2015-03-24 2015-03-24 回転式密閉型圧縮機

Publications (1)

Publication Number Publication Date
WO2016151769A1 true WO2016151769A1 (ja) 2016-09-29

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Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2015/058946 WO2016151769A1 (ja) 2015-03-24 2015-03-24 回転式密閉型圧縮機

Country Status (4)

Country Link
JP (1) JPWO2016151769A1 (cs)
CN (2) CN106014991B (cs)
CZ (1) CZ307910B6 (cs)
WO (1) WO2016151769A1 (cs)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPWO2016151769A1 (ja) * 2015-03-24 2017-09-14 三菱電機株式会社 回転式密閉型圧縮機

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1623315A (en) * 1927-04-05 Assigetob to kinney
JPH08512114A (ja) * 1993-06-30 1996-12-17 エンプレサ・ブラジレイラ・デイ・コンプレソレス・エシ・ア−エンブラク 固定ベーン回転圧縮機
JP2003262192A (ja) * 2002-03-07 2003-09-19 Daikin Ind Ltd 密閉型圧縮機

Family Cites Families (8)

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Publication number Priority date Publication date Assignee Title
DE102004054186B3 (de) * 2004-11-10 2006-06-14 Danfoss Compressors Gmbh Kompressor-Kurbelwelle
JP5117503B2 (ja) * 2007-08-28 2013-01-16 東芝キヤリア株式会社 多気筒回転式圧縮機及び冷凍サイクル装置
KR101271272B1 (ko) * 2008-08-29 2013-06-04 도시바 캐리어 가부시키가이샤 밀폐형 압축기, 2기통 회전식 압축기 및 냉동 사이클 장치
CN102748288A (zh) * 2011-04-22 2012-10-24 广东美芝制冷设备有限公司 使用r290冷媒的旋转式压缩机
IN2014CN02690A (cs) * 2011-10-24 2015-07-31 Mitsubishi Electric Corp
US9435337B2 (en) * 2012-12-27 2016-09-06 Panasonic Intellectual Property Management Co., Ltd. Scroll compressor
KR102051094B1 (ko) * 2013-06-03 2019-12-02 엘지전자 주식회사 스크롤 압축기
JPWO2016151769A1 (ja) * 2015-03-24 2017-09-14 三菱電機株式会社 回転式密閉型圧縮機

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1623315A (en) * 1927-04-05 Assigetob to kinney
JPH08512114A (ja) * 1993-06-30 1996-12-17 エンプレサ・ブラジレイラ・デイ・コンプレソレス・エシ・ア−エンブラク 固定ベーン回転圧縮機
JP2003262192A (ja) * 2002-03-07 2003-09-19 Daikin Ind Ltd 密閉型圧縮機

Also Published As

Publication number Publication date
CZ307910B6 (cs) 2019-08-07
CZ2017673A3 (cs) 2017-11-22
CN205423162U (zh) 2016-08-03
CN106014991A (zh) 2016-10-12
JPWO2016151769A1 (ja) 2017-09-14
CN106014991B (zh) 2019-03-08

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