WO2012001989A1 - 回転式圧縮機 - Google Patents

回転式圧縮機 Download PDF

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Publication number
WO2012001989A1
WO2012001989A1 PCT/JP2011/003773 JP2011003773W WO2012001989A1 WO 2012001989 A1 WO2012001989 A1 WO 2012001989A1 JP 2011003773 W JP2011003773 W JP 2011003773W WO 2012001989 A1 WO2012001989 A1 WO 2012001989A1
Authority
WO
WIPO (PCT)
Prior art keywords
piston
rotary compressor
cylinder
end surface
refrigerant
Prior art date
Application number
PCT/JP2011/003773
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
大輔 船越
洋 杉浦
孝正 先本
飯田　登
Original Assignee
パナソニック株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by パナソニック株式会社 filed Critical パナソニック株式会社
Priority to JP2011551339A priority Critical patent/JP4928016B2/ja
Priority to CN201180003212.XA priority patent/CN102483066B/zh
Priority to EP11800459.7A priority patent/EP2589810B1/en
Publication of WO2012001989A1 publication Critical patent/WO2012001989A1/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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/02—Lubrication; Lubricant separation
    • F04C29/028—Means for improving or restricting lubricant flow
    • 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
    • F04C2250/00—Geometry
    • F04C2250/30—Geometry of the stator

Definitions

  • the present invention relates to a rotary compressor used in devices such as an air conditioner, a refrigeration device, a blower device, and a hot water supply device.
  • devices such as an air conditioner use a rotary compressor that sucks in gas refrigerant evaporated by an evaporator and compresses the sucked gas refrigerant.
  • a rotary compressor is known as one of such rotary compressors (see, for example, Patent Document 1).
  • FIG. 15 is a cross-sectional view of an essential part showing an example of a rotary compressor.
  • the electric motor 2 and the compression mechanism unit 3 are connected and stored by a crankshaft 31.
  • An oil reservoir 6 is formed at the bottom of the sealed container 1.
  • the compression mechanism unit 3 includes a cylinder 30 that forms a cylindrical internal space, a piston 32 that is disposed in the internal space of the cylinder 30, an end plate 34 of an upper bearing 34 a that closes the upper end surface of the cylinder 30, and the cylinder 30.
  • the end plate 35 of the lower bearing 35a that closes the lower end surface of the lower bearing 35 and the vane 33 that partitions the inside of the compression chamber 39 into a low-pressure part and a high-pressure part.
  • the compression chamber 39 is formed by the internal space of the cylinder 30, the piston 32, the end plate 34, and the end plate 35.
  • the crankshaft 31 is supported by an upper bearing 34a and a lower bearing 35a.
  • An eccentric portion 31 a is formed on the crankshaft 31.
  • the eccentric portion 31 a is disposed between the end plate 34 and the end plate 35.
  • the piston 32 is fitted to the eccentric portion 31a.
  • the vane 33 reciprocates in a slot provided in the cylinder 30.
  • the tip of the vane 33 is in pressure contact with the outer periphery of the piston 32, and the vane 33 reciprocates following the eccentric rotation of the piston 32 to partition the inside of the compression chamber 39 into a low pressure portion and a high pressure portion.
  • An oil hole 41 is provided in the axial portion of the crankshaft 31. Oil (lubricating oil) in the oil reservoir 6 is supplied to the oil hole 41.
  • oil supply holes 42 and 43 communicating with the oil hole 41 are provided in the wall portion of the crankshaft 31.
  • the oil supply hole 42 is formed in a wall portion corresponding to the upper bearing 34a
  • the oil supply hole 43 is formed in a wall portion corresponding to the lower bearing 35a.
  • an oil supply hole (not shown) communicating with the oil hole 41 and an oil groove (not shown) are formed in the wall portion of the eccentric portion 31a.
  • the cylinder 30 is formed with a suction port 40 for sucking low-pressure gas.
  • the suction port 40 communicates with a low pressure portion (suction chamber) in the compression chamber 39.
  • a discharge port 38 for discharging the high-pressure gas compressed in the compression chamber 39 is formed in the upper bearing 34a.
  • the discharge port 38 communicates with a high pressure portion in the compression chamber 39.
  • the discharge port 38 is formed as a circular hole passing through the upper bearing 34a in plan view.
  • a discharge valve 36 is provided on the upper surface of the discharge port 38. The discharge valve 36 is released when it receives a pressure of a predetermined magnitude or more.
  • the discharge valve 36 is covered with a cup muffler 37.
  • the low pressure portion (suction chamber) of the compression chamber 39 gradually expands after the sliding contact portion between the piston 32 and the cylinder 30 passes through the suction port 40 and sucks gas from the suction port 40.
  • the discharge valve 36 opens and the discharge port 38 is opened. Out of gas. The gas flowing out from the discharge port 38 is discharged into the sealed container 1 through the cup muffler 37.
  • an upper piston inner space is formed by the eccentric portion 31a of the crankshaft 31, the end plate 34 of the upper bearing 34a, and the inner peripheral surface of the piston 32. 35 and the inner peripheral surface of the piston 32 form a lower piston inner space. Oil in the oil hole 41 leaks from the oil supply hole 42 to the upper space in the piston, and oil in the oil hole 41 leaks from the oil supply hole 43 to the lower space in the piston.
  • the upper space in the piston and the lower space in the piston are almost always higher than the pressure in the compression chamber 39.
  • the height of the cylinder 30 must be set slightly larger than the height of the piston 32 so that the piston 32 can slide inside.
  • the upper and lower end surfaces of the piston 32, the end plate 34, the end A gap is generated between the plate 35 and the plate 35. Therefore, oil leaks into the compression chamber 39 from the upper space in the piston and the lower space in the piston through this gap. In order to achieve high efficiency, it is necessary to maintain reliability while suppressing this leakage.
  • FIGS. 10 to 14 show a state in which the crankshaft 31 is removed for the sake of simplicity of explanation, and the gap between the piston 32 and the upper and lower end plates 34 and 35 (represented by exaggerating the vertical direction, actually It is a schematic diagram showing the relationship of several tens of ⁇ m. As shown in FIG. 10, chamfers having substantially the same size at the upper end portion and the lower end portion are provided at the end portion of the inner peripheral surface of the piston 32.
  • the upper and lower chamfering difference of the piston 32 is set to BA> 0. Then, when an upward force is generated by providing a chamfering difference (BA> 0) that balances the weight of the piston 32, the piston 32 floats.
  • BA> 0 a chamfering difference
  • the space between the piston 32 and the upper and lower end plates 34 and 35 is reduced to about several ⁇ m.
  • leakage can be suppressed and efficiency can be improved.
  • the piston 32 behaves unstable during actual operation, problems such as specular wear and seizure are likely to occur particularly on the lower end plate 35 by reducing the gap. Therefore, as shown in FIG. 13, the chamfering of the lower end portion of the piston 32 is increased, the oil holding area between the piston 32 and the lower end plate 35 is increased, and the cooling effect by the oil is enhanced to increase the reliability. It is necessary to improve.
  • the first problem is that when adjusting the vertical chamfering difference so as to balance the weight of the piston 32 as shown in FIG. It is very difficult to manage the dimensions.
  • the second problem is that when the upper and lower gaps of the piston 32 are reduced, both the upper and lower chamfers of the piston 32 need to be increased.
  • the inner surface of the piston 32 and the discharge port 38 are If the seal length is not secured, the efficiency of the return of the high-pressure gas to the suction will be reduced, so that the upper side surface cannot be made so large. In the end, only the lower side chamfer of the same size as the upper side chamfer can be set, so that the reliability cannot be greatly increased.
  • the present invention solves such problems, and improves productivity, improves leakage by suppressing leakage of the upper and lower end faces of the piston, and improves reliability by suppressing wear and seizure of the end plate. It is for the purpose.
  • the present invention provides a cylinder, an eccentric part of a shaft disposed in the cylinder, a piston fitted in the eccentric part, and following the eccentric rotation of the piston.
  • a rotary compressor having a vane that reciprocates in a slot provided in the slot, and two end plates that close the upper and lower end surfaces of the cylinder, and a lower inner corner formed on the lower end surface of the piston,
  • a second area surrounded by the end plate closing the lower end surface of the cylinder is surrounded by an upper inner surface corner formed on the upper end surface of the piston and the end plate closing the upper end surface of the cylinder.
  • the angle between the lower end surface of the piston and the lower inner surface corner is smaller than the angle between the upper end surface of the piston and the upper inner surface corner.
  • the longitudinal cross-sectional view of the rotary compressor in Embodiment 1 of this invention Enlarged sectional view of the compression mechanism of the rotary compressor Cross section of piston of the same rotary compressor
  • the figure which shows the distribution of the pressure applied to the top and bottom of the piston of the rotary compressor Schematic diagram showing the positional relationship between the clearance between the piston and the upper and lower end plates and the discharge port when the upper and lower clearances of the piston of the rotary compressor are reduced.
  • an upper inner surface corner portion formed on the upper end surface of the piston, and a second area surrounded by a lower inner surface corner portion formed on the lower end surface of the piston and an end plate closing the lower end surface of the cylinder.
  • the angle between the lower end surface of the piston and the lower inner surface corner is made larger than the first area surrounded by the end plate closing the upper end surface of the cylinder, and the angle between the upper end surface of the piston and the upper inner surface corner It is a smaller one.
  • the upper inner corner is formed by chamfering and the lower inner corner is formed by counterbore.
  • the angle between the upper end surface of the piston and the upper inner surface corner is in the range of 132 to 138 degrees.
  • the first area and the second area are set so as to balance the weight of the piston.
  • the piston floats, and the two gaps between the upper and lower end surfaces of the piston and the end plate are made uniform.
  • gas leakage is proportional to the cube of the gap, when the gaps above and below the piston are evenly distributed and when they are unevenly distributed, the latter has a larger amount of gas leakage.
  • gas and oil leaking into the suction chamber through the gap between the upper and lower end surfaces of the piston are suppressed, so compression loss can be reduced, and it is equivalent to reducing the gap without reducing the upper and lower gaps.
  • the efficiency is further improved, and the reliability is further improved as compared with the case where the efficiency is improved by reducing the gap.
  • the differential pressure is particularly large, and sliding loss and leakage loss are large. Even CO 2 can be more effectively increased in efficiency.
  • a single refrigerant comprising a refrigerant having a base component of a hydrofluoroolefin having a double bond between carbon and carbon as the working refrigerant, or A mixed refrigerant containing a refrigerant is used as a working refrigerant.
  • This refrigerant has the property of being easily decomposed at high temperatures, but by reducing leakage loss and sliding loss, it is possible to improve the reliability of the compressor more effectively while suppressing high temperature decomposition of the refrigerant. Become. Moreover, since this refrigerant has no ozone destruction and a low global warming potential, it can contribute to the configuration of an air-conditioning cycle that is friendly to the earth.
  • FIG. 1 is a longitudinal sectional view of a rotary compressor according to Embodiment 1 of the present invention
  • FIG. 2 is an enlarged view of the compression mechanism section.
  • An oil supply hole 44 communicating with the oil hole 41 and an oil groove 45 are formed in the wall portion of the eccentric portion 31 a of the crankshaft 31.
  • the piston inner upper space 46 is formed by the eccentric portion 31a of the crankshaft 31, the end plate 34 of the upper bearing 34a, and the inner peripheral surface of the piston 32, and the ends of the eccentric portion 31a of the crankshaft 31 and the lower bearing 35a.
  • a piston inner lower space 47 is formed by the plate 35 and the inner peripheral surface of the piston 32.
  • Oil in the oil hole 41 leaks from the oil supply hole 42 into the piston upper space 46, and oil in the oil hole 41 leaks from the oil supply hole 43 into the piston lower space 47.
  • the piston upper space 46 and the piston lower space 47 are almost always higher than the pressure inside the compression chamber 39.
  • the height of the cylinder 30 must be set slightly larger than the height of the piston 32 so that the piston 32 can slide inside.
  • the end surface of the piston 32 and the end plate of the upper bearing 34a. 34, and between the end face of the piston 32 and the end plate 35 of the lower bearing 35a Therefore, oil leaks from the upper piston inner space 46 and the lower piston inner space 47 to the compression chamber 39 through the gap.
  • action are demonstrated below.
  • the area is larger than the first area 32 a surrounded by the corners and the end plate 34.
  • the angle D between the lower end surface of the piston 32 and the lower inner surface corner is made smaller than the angle C between the upper end surface of the piston 32 and the upper inner surface corner.
  • the first embodiment is configured as described above to improve efficiency and reliability.
  • FIG. 4 shows the pressure distribution applied to the piston 32 in the first embodiment.
  • the high pressure is uniformly distributed on the inner surface side, and the end surface side is linearly distributed from the high pressure to the intermediate pressure.
  • the high pressure is uniformly distributed on the inner surface side, but the end surface side is linearly distributed from the medium high pressure (pressure lower than the high pressure) to the intermediate pressure. That is, since the angle D between the lower end surface of the piston 32 and the lower inner surface corner is smaller than the angle C on the lower side of the piston 32, the oil flow becomes worse and a pressure drop occurs. Therefore, as shown in FIG.
  • FIG. 7 is a cross-sectional view showing a piston of a rotary compressor according to Embodiment 2 of the present invention. Since other configurations are the same as those of the first embodiment, description thereof is omitted.
  • a second area 32 b surrounded by a lower inner surface corner formed on the lower end surface of the piston 32 and the end plate 35 is formed on the upper end surface of the piston 32. It is made larger than the first area 32 a surrounded by the upper inner corner and the end plate 34.
  • the angle D between the lower end surface of the piston 32 and the lower inner surface corner is made smaller than the angle C between the upper end surface of the piston 32 and the upper inner surface corner.
  • the upper inner surface corner portion is formed by chamfering the upper end surface and the upper inner surface of the piston 32
  • the lower inner surface corner portion is formed by counterboring the lower end surface and the lower inner surface of the piston 32.
  • the angle C between the upper end surface of the piston 32 and the upper inner corner is preferably in the range of 132 degrees to 138 degrees, and more preferably 135 degrees.
  • the angle D between the lower end surface of the piston 32 and the lower inner corner portion is 90 degrees.
  • the upper inner corner is formed by chamfering and the lower inner corner is formed by counterbore, so that it is possible to determine whether the piston 32 is up or down visually during assembly. Can be reduced.
  • the BA when generating a force that balances the weight of the piston 32, when the upper and lower sides of the piston 32 are chamfered, the BA is about 0.1 mm, whereas if only the lower side is a counterbore, the BA is The tolerance range can be expanded to about 0.4 to 0.8 mm, which improves mass productivity.
  • FIG. 8 shows a rotary compressor having a configuration different from that of the first embodiment of the present invention.
  • symbol is attached
  • the rotary compressor shown in FIG. 8 is connected to the outer peripheral portion of the piston 132 in a protruding manner, and partitions the compression chamber 39 into a low pressure side and a high pressure side, and the vane 133 is swingable and retractable.
  • the swing bush 130 is supported. Also in the rotary compressor shown in FIG. 8, the configurations of the first embodiment and the second embodiment can be applied, and an equivalent effect can be obtained.
  • FIG. 9 shows a rotary compressor having a further different configuration.
  • symbol is attached
  • the rotary compressor shown in FIG. 9 includes a piston 232 and a vane 233 that is swingably connected at the tip. Also in the rotary compressor shown in FIG. 9, the configurations of the first embodiment and the second embodiment can be applied, and an equivalent effect can be obtained.
  • this refrigerant is easily decomposed at high temperatures and is unstable.
  • the lubricity of the sliding portion between the end face of the piston 32 and the end plate 35 is improved, so that the temperature rise at the sliding portion can be efficiently suppressed, and the refrigerant can be decomposed. And the reliability can be improved more effectively.
  • a mixed refrigerant in which the hydrofluoroolefin is tetrafluoropropene (HFO1234yf or HFO1234ze) or trifluoropropene (HFO1243zf) and the hydrofluorocarbon is difluoromethane (HFC32) may be used as the working refrigerant.
  • a mixed refrigerant in which the hydrofluoroolefin is tetrafluoropropene (HFO1234yf or HFO1234ze) or trifluoropropene (HFO1243zf) and the hydrofluorocarbon is pentafluoroethane (HFC125) may be used as the working refrigerant.
  • a three-component mixed refrigerant in which the hydrofluoroolefin is tetrafluoropropene (HFO1234yf or HFO1234ze) or trifluoropropene (HFO1243zf) and the hydrofluorocarbon is pentafluoroethane (HFC125) and difluoromethane (HFC32) is the working refrigerant. It is good.
  • a single-piston rotary compressor with one cylinder has been described as an example.
  • a rotary compressor such as a rotary compressor having a plurality of cylinders may be used.
  • the rotary compressor according to the present invention suppresses deterioration of reliability such as wear and seizure, and simultaneously reduces leakage loss and sliding loss, thereby improving the efficiency of the compressor. It becomes possible.
  • the present invention can be applied to an application such as an air conditioner using a natural refrigerant CO 2 or a heat pump type hot water heater.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
PCT/JP2011/003773 2010-07-02 2011-07-01 回転式圧縮機 WO2012001989A1 (ja)

Priority Applications (3)

Application Number Priority Date Filing Date Title
JP2011551339A JP4928016B2 (ja) 2010-07-02 2011-07-01 回転式圧縮機
CN201180003212.XA CN102483066B (zh) 2010-07-02 2011-07-01 旋转式压缩机
EP11800459.7A EP2589810B1 (en) 2010-07-02 2011-07-01 Rotary compressor

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2010151756 2010-07-02
JP2010-151756 2010-07-02

Publications (1)

Publication Number Publication Date
WO2012001989A1 true WO2012001989A1 (ja) 2012-01-05

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ID=45401727

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2011/003773 WO2012001989A1 (ja) 2010-07-02 2011-07-01 回転式圧縮機

Country Status (4)

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EP (1) EP2589810B1 (zh)
JP (1) JP4928016B2 (zh)
CN (1) CN102483066B (zh)
WO (1) WO2012001989A1 (zh)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP7358674B1 (ja) * 2023-06-07 2023-10-10 日立ジョンソンコントロールズ空調株式会社 圧縮機および空気調和装置

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN113565761B (zh) * 2021-08-30 2023-04-25 广东美芝制冷设备有限公司 活塞、旋转式压缩机及制冷设备

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0861276A (ja) 1994-08-12 1996-03-08 Toshiba Corp ロータリコンプレッサ
JP2010031733A (ja) * 2008-07-29 2010-02-12 Panasonic Corp ロータリ圧縮機

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3702686B2 (ja) * 1999-01-21 2005-10-05 ダイキン工業株式会社 ロータリ圧縮機
JP2004225578A (ja) * 2003-01-21 2004-08-12 Matsushita Electric Ind Co Ltd ロータリ圧縮機
JP2005002832A (ja) * 2003-06-10 2005-01-06 Daikin Ind Ltd ロータリー流体機械
JP2006177227A (ja) * 2004-12-22 2006-07-06 Hitachi Home & Life Solutions Inc ロータリ式２段圧縮機
CN201301810Y (zh) * 2008-11-06 2009-09-02 松下·万宝(广州)压缩机有限公司 压缩机

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0861276A (ja) 1994-08-12 1996-03-08 Toshiba Corp ロータリコンプレッサ
JP2010031733A (ja) * 2008-07-29 2010-02-12 Panasonic Corp ロータリ圧縮機

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP7358674B1 (ja) * 2023-06-07 2023-10-10 日立ジョンソンコントロールズ空調株式会社 圧縮機および空気調和装置

Also Published As

Publication number Publication date
CN102483066A (zh) 2012-05-30
EP2589810A4 (en) 2016-05-18
JP4928016B2 (ja) 2012-05-09
JPWO2012001989A1 (ja) 2013-08-22
EP2589810A1 (en) 2013-05-08
CN102483066B (zh) 2014-08-06
EP2589810B1 (en) 2018-05-02

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