WO2010064377A1 - ロータリ流体機械 - Google Patents

ロータリ流体機械 Download PDF

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Publication number
WO2010064377A1
WO2010064377A1 PCT/JP2009/006314 JP2009006314W WO2010064377A1 WO 2010064377 A1 WO2010064377 A1 WO 2010064377A1 JP 2009006314 W JP2009006314 W JP 2009006314W WO 2010064377 A1 WO2010064377 A1 WO 2010064377A1
Authority
WO
WIPO (PCT)
Prior art keywords
cylinder
compression mechanism
fluid machine
rotary fluid
roller
Prior art date
Application number
PCT/JP2009/006314
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
土屋直洋
岸康弘
寺井利行
中田裕吉
Original Assignee
日立アプライアンス株式会社
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 日立アプライアンス株式会社 filed Critical 日立アプライアンス株式会社
Priority to KR1020117012398A priority Critical patent/KR101300920B1/ko
Priority to JP2010541207A priority patent/JP5469612B2/ja
Priority to CN200980147309.0A priority patent/CN102224345B/zh
Publication of WO2010064377A1 publication Critical patent/WO2010064377A1/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
    • 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
    • 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
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/02—Lubrication; Lubricant separation
    • 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
    • F04C2240/00—Components
    • F04C2240/30—Casings or housings

Definitions

  • the present invention relates to a rotary fluid machine mounted on a refrigeration air conditioner or the like.
  • the cylinder volume of the on-board compressor is adjusted according to the refrigeration capacity of the air conditioner.
  • the compressor mounted on the compressor is combined in an optimal manner by changing the external dimensions of the compressor for each required cylinder volume.
  • the current product is similar. It was common to design by a method of reducing the size.
  • the cylinder volume is increased, it is inevitable to increase the diameter of the compressor.
  • the relationship between the cylinder volume of the existing rotary compressor and the outer diameter of the compressor is approximately ⁇ 90 for approximately less than 10 cc and approximately ⁇ 110 for approximately 8 to 18 cc.
  • Patent Document 1 a technique disclosed in Patent Document 1 is known as a conventional technique.
  • the lower part of the sealed container in which the compression mechanism part is accommodated is mainly used for lubrication or cooling of the sliding part of the compression mechanism part in a space formed by the inner wall of the sealed container and the outer wall of the compression mechanism part. It is necessary to store refrigeration oil.
  • the liquid level height from the bottom of the compressor of the refrigerating machine oil in the sealed container determined by the storage amount of the refrigerating machine oil has an appropriate position for ensuring the performance and reliability of the compressor.
  • the motor is stirred by the rotational movement of the motor part provided in the upper part of the sealed container, the efficiency is reduced due to the occurrence of compressor power loss, and the refrigeration cycle is brought out of the chiller oil out of the sealed container.
  • This causes a heat exchange hindrance and pressure loss, resulting in a decrease in efficiency and a decrease in reliability due to a shortage of refrigerating machine oil in the compressor.
  • the liquid level is too small, a sufficient amount cannot be supplied to the vane sliding portion of the cylinder that requires oil supply from the side surface of the compression mechanism, leading to a decrease in reliability.
  • the refrigerating machine oil is mixed with the refrigerant in the refrigerating cycle and diluted to cause a decrease in viscosity, the amount of refrigerating machine oil to be stored must be maintained. For this reason, when the compressor diameter is reduced or the cylinder volume is increased, the space volume for storing the refrigerating machine oil becomes smaller and the liquid level of the refrigerating machine oil tends to be excessive, so that it is necessary to secure the space volume.
  • the engagement between the closed container and the compression mechanism housed therein is used as a closing member, and the diameter of the outer wall of the vane housing portion of the cylinder can be stored in the vane housing portion.
  • the plurality of recesses are (minimum distance between the recess and the cylinder inner diameter) ⁇ (minimum distance between the cylinder inner diameter and the hole).
  • ⁇ minimum distance between the cylinder inner diameter and the hole.
  • a recess is provided that satisfies the minimum distance) ⁇ 2.5 mm.
  • the reliability of the vane sliding portion can be ensured.
  • the space volume can be increased.
  • the compressor outer diameter can be reduced without causing a reduction in efficiency and reliability due to the stirring of the refrigerating machine oil.
  • Sectional drawing of the compression mechanism part periphery by this invention Sectional drawing of the compression mechanism part periphery by a prior art.
  • an air conditioner rotary compressor having the following structure will be described as an example.
  • a motor part is housed in a sealed container, a crankshaft having an eccentric part for transmitting the rotation of the motor part, a compression mechanism part driven by the eccentric part, and a closure for closing the compression mechanism part in the crankshaft direction A member, and the compression mechanism section includes a cylinder, a roller disposed in the cylinder and driven to rotate by an eccentric portion of the crankshaft, and extends to an outer periphery of the roller according to the eccentric motion of the roller.
  • the closing member includes a bearing for holding the crankshaft, and includes an upper bearing and a lower bearing for closing the upper and lower sides of the cylinder, or a partition plate when there are a plurality of the compression mechanism portions, and a compression chamber in the compression mechanism portion.
  • a discharge hole for discharging the compressed gas into the sealed container is provided in the upper bearing or the lower bearing.
  • the compression mechanism part is single or plural, and the refrigerating machine oil whose main purpose is lubrication or cooling of the sliding part of the compression mechanism part is provided in the sealed container.
  • FIG. 1 shows a sectional view around a compression mechanism as an embodiment of the present invention
  • FIG. 2 shows a sectional view around a compression mechanism according to the prior art.
  • the diameter of the compressor is reduced while maintaining the cylinder volume of the compression mechanism, and the inner diameter of the sealed container 50 in each compressor is ⁇ 80 in FIG.
  • the form is described as ⁇ 112.
  • a cylinder 10 includes a cylinder inner wall 11, a substantially circular cylinder outer wall 12, a vane storage portion 13 for storing a vane 30 that partitions the compression chamber 20 into a low pressure side and a high pressure side, a vane storage portion outer wall 14, and the cylinder inner wall 11 and the cylinder outer wall 12 have a plurality of holes 15 such as a hole 15a used for fastening a closing member for each application, a hole 15b used as a fluid flow path, a hole 15c used as a reference during processing, and the like. Is formed of a suction hole 16 for taking the gas into the cylinder inner wall 11.
  • the compression chamber 20 is formed by the cylinder inner wall 11 and the outer wall of the roller 40, and the volume of the compression chamber 20 in the state shown in the figure becomes the cylinder volume of the compressor.
  • the vane 30 is pressed toward the inner wall center of the cylinder by a spring in order to ensure contact with the outer wall of the roller 40 that is eccentrically moved by a crankshaft.
  • the compression chamber 20 in each figure has the same cylinder volume by making the diameter ⁇ 43 of the cylinder inner wall 11 and the outer wall diameter of the roller 40 equal, and an air conditioner at the same operating frequency. The ability to equalize has been achieved.
  • the average diameter ⁇ 69 of the substantially cylindrical outer wall 12 is also set to the same value.
  • the inner diameter of the sealed container 50 is ⁇ 80 in the embodiment of the present invention and ⁇ 112 in the prior art, and the diameter of the outer wall 14 of the vane housing portion of the cylinder is substantially equal to the inner diameter of the sealed container.
  • the cylinder 10 according to the prior art shown in FIG. 2 has a protrusion 17 having the same diameter as the vane storage portion outer wall 14 in a direction substantially shifted by 180 ° from the vane storage portion outer wall 14 of the cylinder and the vane storage portion 13 of the cylinder.
  • the outer wall 14 and the protrusion 17 of the vane storage portion are used for the purpose of engaging the sealed container 50 and the compression mechanism portion 100 by welding (point 18) or shrink fitting or cold fitting. Therefore, the diameters of the vane storage portion outer wall 14 and the protrusion 17 need to be larger than the diameter of the cylinder inner wall 11 in order to suppress deformation of the cylinder inner wall 11 due to welding heat or fastening stress.
  • the vane is formed by applying an engagement between the sealed container 50 and the compression mechanism 100 by welding, shrink fitting, cold fitting or the like to an upper bearing which is one of the closing members 60.
  • the diameter of the storage section outer wall 14 can be set to a minimum diameter that allows the vane storage section to be disposed and has a size that can withstand the load caused by the movement of the vanes, and the diameter of the sealed container can be reduced.
  • the refrigerating machine oil 70 is sealed in the space 51 in the sealed container represented by the hatched portion formed by the inner wall of the sealed container 50 and the outer shape of the cylinder 10, it is necessary to guarantee a certain volume of the space 51. There is. Since the required amount of the refrigeration oil 70 is determined by the amount of refrigerant according to the cycle capacity of the air conditioner, in order to maintain the performance of the air conditioner, the amount of the refrigeration oil enclosed is reduced simultaneously with the diameter reduction of the compressor. It is difficult to reduce the reliability. For this reason, when the inside diameter of the sealed container 50 is made small, if the same amount of the refrigerating machine oil 70 is sealed, the refrigerating machine oil 70 flows in the axial direction of the compressor.
  • the liquid level height it becomes difficult to set the liquid level height to the upper end of the compression mechanism unit, which is the upper limit.
  • the ratio of the diameter of the cylinder 10 to the inner diameter of the sealed container 50 increases. Therefore, the space 51 is reduced, and in particular, the inner diameter of the sealed container 50 and the inner diameter of the cylinder 10 are (the inner diameter of the cylinder) / (the inner diameter of the sealed container) ⁇ 0.4. In such a case, it is difficult to ensure the liquid level.
  • FIG. 3 shows a comparison between the inner diameter of the sealed container 50 and the height of the liquid surface 71 depending on the length of the sealed container 50 or the crankshaft 80, using a longitudinal sectional view of the compressor.
  • a partition plate 62 for closing the lower end of the cylinder 10a on the inner motor section 90 side of the cylinder 10 and the upper end of the cylinder 10b on the bottom face side of the compressor is provided. ing.
  • the liquid surface 71 has a lower limit as a lower end 71a of the cylinder 10a because the sealing performance and the lubricity with the vane 30 are increased by performing oil supply to the vane storage portion 13 from the side surface of the cylinder 10,
  • the upper limit is set to the upper end 71b of the cylinder 10 to obtain an appropriate position.
  • FIG. 3A is a longitudinal sectional view when the inner diameter of the sealed container 50 according to the prior art is ⁇ 112.
  • 3B is a longitudinal sectional view when the inner diameter of the sealed container 50 is set to ⁇ 80 using the above-described method, and the liquid level 71 exceeds the upper end 71b of the cylinder which is the upper limit.
  • the liquid level 71 exceeds the upper end 71b of the cylinder which is the upper limit.
  • a plurality of recesses 19 are provided in the cylinder outer wall 12 as shown in FIG.
  • the space 51 can be expanded without extending the closed container 50 or the crankshaft 80, which is a conventional technique, which is effective in reducing the height of the liquid level 71.
  • a pressure difference is generated between the space 51 and the compression chamber 20 by the high pressure gas equivalent to the approximate discharge pressure and the low pressure gas equivalent to the approximate suction pressure, a thickness to suppress leakage is required.
  • the setting of 19 requires the following conditions.
  • the pressure in the space 51 is, for example, a high-pressure gas in the case of a high-pressure chamber system, and the fluid flow path hole 15b of the hole 15 is filled with a substantially equivalent high-pressure gas.
  • the pressure in the compression chamber 20 is discharged from the low-pressure gas having the suction pressure and filled with the high-pressure gas having the pressure according to the compression process.
  • the distance between the hole 15b and the cylinder inner wall 11 is secured to prevent leakage due to the pressure difference, so that the recess 19 serving as the wall surface of the space 51 and the outer wall of the compression chamber 20 are provided.
  • the distance between the cylinder inner walls 11 is based on the distance between the hole 15b and the cylinder inner wall 11, By setting a condition that (distance between the recess 19 and the cylinder inner wall 11) ⁇ (distance between the hole 15b and the cylinder inner wall 11), leakage between the recess 19 and the cylinder inner wall 11 can be prevented.
  • the space 51 is filled with low-pressure gas, and the distance between the recess 19 and the hole 15b is set to prevent leakage between the holes 15b.
  • (Distance between recess 19 and hole 15b) ⁇ (Distance between hole 15b and cylinder inner wall 11) Is a condition.
  • FIG. 3D is a longitudinal sectional view according to the embodiment of the present invention.
  • the concave portion 19 is set to the substantially circular cylinder outer wall 12 .
  • the present invention is not limited to this.
  • the concave portion 19 can be applied to the vane storage portion outer wall 14. it can.
  • Sealed container of compressor 51 ... Space formed by cylinder outer wall and sealed container inner wall, 60 ... Closure member, 61 ... Upper bearing, 62 ... Partition plate, 63 ... Lower bearing, 70 ... Refrigerating machine oil, 71 ... Liquid level when the refrigerating machine oil is enclosed in the compressor, 80 ... Crankshaft, 90 ... Electric motor part, 1 0 compression mechanism.

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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)
PCT/JP2009/006314 2008-12-01 2009-11-24 ロータリ流体機械 WO2010064377A1 (ja)

Priority Applications (3)

Application Number Priority Date Filing Date Title
KR1020117012398A KR101300920B1 (ko) 2008-12-01 2009-11-24 로터리 유체 기계
JP2010541207A JP5469612B2 (ja) 2008-12-01 2009-11-24 ロータリ流体機械
CN200980147309.0A CN102224345B (zh) 2008-12-01 2009-11-24 回转式流体机械

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2008-305837 2008-12-01
JP2008305837 2008-12-01

Publications (1)

Publication Number Publication Date
WO2010064377A1 true WO2010064377A1 (ja) 2010-06-10

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ID=42233036

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2009/006314 WO2010064377A1 (ja) 2008-12-01 2009-11-24 ロータリ流体機械

Country Status (4)

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JP (1) JP5469612B2 (ko)
KR (1) KR101300920B1 (ko)
CN (1) CN102224345B (ko)
WO (1) WO2010064377A1 (ko)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105114301B (zh) * 2015-09-09 2017-06-23 山东科灵新能源发展有限公司 无外泄漏的转子液体泵

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2003161278A (ja) * 2001-11-22 2003-06-06 Hitachi Ltd 密閉形ロータリ圧縮機
JP2008208262A (ja) * 2007-02-27 2008-09-11 Nippon Oil Corp 冷凍機油組成物および冷凍機用作動流体組成物

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2862260B2 (ja) * 1989-03-16 1999-03-03 株式会社日立製作所 ロータリ圧縮機
KR19990025773A (ko) * 1997-09-18 1999-04-06 구자홍 밀폐형 회전식 압축기의 실린더 고정구조
CN1538071A (zh) * 2003-04-16 2004-10-20 松下电器产业株式会社 旋转压缩机

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2003161278A (ja) * 2001-11-22 2003-06-06 Hitachi Ltd 密閉形ロータリ圧縮機
JP2008208262A (ja) * 2007-02-27 2008-09-11 Nippon Oil Corp 冷凍機油組成物および冷凍機用作動流体組成物

Also Published As

Publication number Publication date
KR101300920B1 (ko) 2013-08-27
JP5469612B2 (ja) 2014-04-16
KR20110073620A (ko) 2011-06-29
JPWO2010064377A1 (ja) 2012-05-10
CN102224345A (zh) 2011-10-19
CN102224345B (zh) 2014-12-03

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