WO2016139796A1 - 圧縮機 - Google Patents

圧縮機 Download PDF

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Publication number
WO2016139796A1
WO2016139796A1 PCT/JP2015/056498 JP2015056498W WO2016139796A1 WO 2016139796 A1 WO2016139796 A1 WO 2016139796A1 JP 2015056498 W JP2015056498 W JP 2015056498W WO 2016139796 A1 WO2016139796 A1 WO 2016139796A1
Authority
WO
WIPO (PCT)
Prior art keywords
compression mechanism
reed valve
port
groove
discharge port
Prior art date
Application number
PCT/JP2015/056498
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
祐一朗 今川
寿史 柬理
宏樹 長澤
貴也 木本
勝巳 遠藤
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 PCT/JP2015/056498 priority Critical patent/WO2016139796A1/ja
Priority to CN201610099436.XA priority patent/CN105937496A/zh
Priority to CN201620136050.7U priority patent/CN205503461U/zh
Publication of WO2016139796A1 publication Critical patent/WO2016139796A1/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
    • 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
    • F04B39/10—Adaptations or arrangements of distribution 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
    • F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • F04C29/124—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps
    • F04C29/126—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps of the non-return type
    • F04C29/128—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps of the non-return type of the elastic type, e.g. reed valves
    • 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
    • F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet

Definitions

  • the present invention relates to a compressor with improved compression efficiency and reliability.
  • a compressor in which the thickness of the discharge port for discharging the refrigerant is reduced to improve the compression efficiency.
  • a reinforcing portion having a thickness larger than the thickness of the valve seat portion is formed in a part of the circumferential direction outside the valve seat portion, The thin valve seat part and the part around the valve seat part are reinforced.
  • the present invention has been made against the background of the above problems, and an object thereof is to obtain a compressor with improved compression efficiency and reliability.
  • a compressor according to the present invention includes a compression chamber that compresses a fluid, a discharge port that discharges the fluid compressed in the compression chamber, a fixed portion that is fixed to the compression mechanism portion, and a discharge port.
  • a reed valve that is disposed outside the compression chamber, and the compression mechanism has a groove that accommodates at least a portion of the reed valve.
  • the thickness of the portion of the compression mechanism portion where the reinforcing portion is formed gradually increases from the port peripheral portion toward the outside, including a port peripheral portion surrounding the discharge port and a reinforcing portion surrounding the port peripheral portion. It ’s thick.
  • FIG. 5 is a diagram schematically showing a groove portion of the AA cross section of FIG. 4.
  • FIG. 5 is a diagram schematically showing a recessed portion of the BB cross section of FIG. 4.
  • FIG. 8 is a diagram schematically showing a groove portion of a CC cross section in FIG. 7.
  • FIG. 1 is a diagram schematically illustrating an example of a longitudinal section of a compressor according to Embodiment 1 of the present invention.
  • a compressor 100 illustrated in FIG. 1 compresses a fluid such as a refrigerant gas.
  • the compressor 100 compresses the low-pressure refrigerant gas sucked from the suction pipe 25 and discharges the compressed high-pressure refrigerant gas from the discharge pipe 26 to the outside of the sealed container 1.
  • the compressor 100 includes an electric motor unit 2 and a compression unit 30 that are accommodated in the sealed container 1.
  • the compressor 100 is not limited to the hermetic compressor as shown in FIG. 1, and may be an open compressor in which the electric motor unit 2 is disposed outside the hermetic container 1. .
  • the electric motor unit 2 transmits power to the compression unit 30 via the rotary shaft 4, and includes a stator 2a and a rotor 2b.
  • the compression part 30 receives power from the electric motor part 2 and compresses the refrigerant gas in the compression chamber 14, and includes the cylinder part 7, the upper bearing 12, the lower bearing 13, and the rolling piston 9.
  • the compression unit 30 according to this embodiment includes a first compression mechanism unit 3a and a second compression mechanism unit 3b stacked with the partition plate 5 interposed therebetween.
  • the compressor 100 may include any one of the first compression mechanism unit 3a and the second compression mechanism unit 3b.
  • the first compression mechanism section 3a compresses the refrigerant gas sucked into the first compression chamber 14a inside the first cylinder section 7a, and is driven by receiving power from the electric motor section 2 and is a first rolling piston. 9a is included.
  • the second compression mechanism portion 3b compresses the refrigerant gas sucked into the second compression chamber 14b inside the second cylinder portion 7b, and is driven by receiving power from the electric motor portion 2.
  • a rolling piston 9b is included.
  • the 1st compression mechanism part 3a and the 2nd compression mechanism part 3b are the same structures, in order to make an understanding of this embodiment easy in the following description, only about the 1st compression mechanism part 3a. And the description of the second compression mechanism 3b is omitted.
  • FIG. 2 is a diagram schematically illustrating an example of a cross section of the first compression mechanism section illustrated in FIG. 1, and FIG. 3 is a schematic diagram illustrating an enlarged vertical section of the discharge port portion of FIG. 1.
  • FIG. 2 the 1st compression mechanism part 3a is provided with the 1st rolling piston 9a and the vane 11 in the 1st compression chamber 14a inside the 1st cylinder part 7a.
  • the first rolling piston 9a is attached to the eccentric shaft portion 8 of the rotating shaft 4, and the power from the electric motor portion 2 is transmitted to the first rolling piston 9a.
  • the eccentric shaft portion 8 is formed of a member different from the rotation shaft 4 and is attached to the rotation shaft 4.
  • the eccentric shaft part 8 and the rotating shaft 4 may be integrally comprised by the same member.
  • a vane groove 10 and a suction port 15 are formed in the first cylinder portion 7a.
  • the vane 11 is movably held in the vane groove 10 and divides the first compression chamber 14a into a chamber communicating with the suction port 15 and a chamber communicating with the discharge port 16 shown in FIG. It is.
  • the upper bearing 12 attached to the first cylinder portion 7a is formed with a discharge port 16 for discharging the high-pressure refrigerant gas compressed in the first compression chamber 14a.
  • a groove portion 20 that accommodates at least a part of the reed valve 17 is formed on the outer surface of the first compression chamber 14 a of the upper bearing 12.
  • the reed valve 17 is a sheet-like member that operates to open and close the discharge port 16 to prevent the backflow of the refrigerant gas.
  • the reed valve 17 closes the discharge port 16 so that the pressure inside the first compression chamber 14a is sealed.
  • the reed valve 17 has a fixed portion 17 a fixed to the upper bearing 12 and a movable portion 17 b that opens and closes the discharge port 16.
  • the movable portion 17b of the reed valve 17 may include a protruding portion (not shown) that protrudes toward the discharge port 16 and contacts the peripheral portion of the discharge port 16.
  • a reed valve pressing member 18 that restricts the range in which the reed valve 17 moves is disposed.
  • the reed valve 17 and the reed valve pressing member 18 are fixed to the upper bearing 12 with a fixing member 19 such as a bolt, for example.
  • FIG. 4 is a diagram schematically showing the upper surface of the upper bearing shown in FIG. 1
  • FIG. 5 is a diagram schematically showing the groove portion of the AA cross section of FIG.
  • FIG. 5 is a diagram schematically showing a recess portion of the BB cross section of FIG.
  • a groove portion 20 and a recess portion 22 communicating with the groove portion 20 are formed on the upper surface, which is the outer surface of the first compression chamber 14 a of the upper bearing 12.
  • the groove portion 20 includes a valve seat portion 21, a port peripheral portion 20a surrounding the valve seat portion 21, and a reinforcing portion 23 surrounding the port peripheral portion 20a.
  • the valve seat portion 21 is a portion that contacts the reed valve 17 when the reed valve 17 is closed.
  • the thickness of the portion of the upper bearing 12 where the valve seat portion 21 is formed is slightly thicker than the thickness of the portion around the valve seat portion 21 where the port peripheral portion 20a is formed.
  • the valve seat portion 21 slightly protrudes from the port peripheral portion 20a toward the reed valve 17 side.
  • the thickness of the portion of the upper bearing 12 where the reinforcing portion 23 is formed gradually increases from the port peripheral portion 20a toward the outside.
  • the port peripheral portion 20a and the reinforcing portion 23 are formed so that the reed valve 17 does not contact the wall portion of the groove portion 20 including the reinforcing portion 23 when the reed valve 17 opens and closes.
  • the reinforcing portion 23 is formed to have an inclined surface that is inclined outward from the port peripheral portion 20 a as shown in FIG. 5, the reed valve 17 contacts the wall portion of the groove portion 20.
  • the area of the port peripheral portion 20a can be reduced, the thickness of the portion of the upper bearing 12 where the port peripheral portion 20a and the valve seat portion 21 are formed can be reduced.
  • the reinforcing portion 23 has an inclined surface that is inclined outward from the port peripheral portion 20a, the refrigerant gas discharged from the discharge port 16 flows smoothly along the inclined surface of the reinforcing portion 23. Therefore, pressure loss is reduced.
  • the recessed portion 22 communicates with the groove portion 20 on the side of the groove portion 20 facing the tip portion on the movable portion 17 b side of the reed valve 17.
  • the recess portion 22 is formed deeper than the wall portions on both sides of the reed valve 17 of the groove portion 20, and the refrigerant gas discharged from the discharge port 16 is easily discharged from the front end side of the reed valve 17. Yes.
  • the hollow part 22 may be connected with the reinforcing part 23 of the groove part 20. Further, the thickness of the portion of the upper bearing 12 where the recess 22 is formed is thicker than the thickness of the portion where the port peripheral portion 20a is formed.
  • a dent reinforcing portion 24 is formed at an edge other than a portion communicating with the groove portion 20 of the dent portion 22.
  • the thickness of the portion of the upper bearing 12 where the recess reinforcing portion 24 is formed is gradually increased outward, and the recess 22 and the portion of the groove 20 formed continuously with the recess 22 are formed. Deformation is suppressed. As a result, the thickness of the portion of the upper bearing 12 where the port peripheral portion 20a and the valve seat portion 21 are formed can be reduced.
  • FIG. 7 when the hollow reinforcement part 24 is formed so that it may have an inclined surface inclined outward, the refrigerant gas discharged from the discharge port 16 is made into the hollow reinforcement part 24. Since it flows smoothly through the inclined surface, pressure loss is reduced.
  • the groove portion 20 that accommodates at least a part of the reed valve 17 is formed around the discharge port 16 of the upper bearing 12.
  • the groove portion 20 includes a port peripheral portion 20a surrounding the discharge port 16 and a reinforcing portion 23 surrounding the port peripheral portion 20a. As shown in FIG. 5, the reinforcing portion 23 of the upper bearing 12 is formed.
  • the thickness of the portion gradually increases from the port peripheral portion 20a toward the outside. Therefore, in this embodiment, the thickness of the portion of the upper bearing 12 where the discharge port 16 is formed can be reduced.
  • FIG. 7 is a diagram schematically illustrating Comparative Example 1 of FIG. 4, and FIG. 8 is a diagram schematically illustrating a groove portion of the CC cross section of FIG. As shown in FIGS. 7 and 8, in Comparative Example 1, unlike the embodiment described in FIGS. 4, 5, etc., the reinforcing portion is not formed in the groove portion 200 of the upper bearing 120.
  • Comparative Example 1 when the thickness of the portion where the valve seat portion 210 and the port peripheral portion 200a of the upper bearing 120 are simply reduced, the port peripheral portion 200a is deformed. Gas leakage may occur, and the upper bearing 120 may be damaged. Therefore, in Comparative Example 1, the thickness of the portion where the valve seat portion 210 and the port peripheral portion 200a are formed must be increased.
  • the reinforcing portion 23 is formed around the port peripheral portion 20a of the groove portion 20, and therefore the upper bearing 12 The thickness of the portion where the discharge port 16 is formed can be reduced. As a result, according to this embodiment, the compressor 100 with improved compression efficiency can be obtained.
  • the port peripheral portion 20a surrounding the discharge port 16 is formed around the discharge port 16, and the reinforcing portion 23 surrounding the port peripheral portion 20a is formed around the port peripheral portion 20a. ing. Therefore, according to this embodiment, since the refrigerant gas discharged from the discharge port 16 is discharged uniformly from the periphery of the discharge port 16, a force in the twist direction acts when the reed valve 17 is opened and closed. The risk of doing so has been reduced. Therefore, according to this embodiment, the risk of the reed valve 17 being deformed or damaged by the force in the torsional direction acting on the reed valve 17 is reduced, so that the reliability of the compressor 100 is improved. Yes.
  • a recess 22 that communicates with the groove 20 is formed.
  • the hollow portion 22 is a portion including the portion of the groove portion 20 that faces the tip of the reed valve 17 on the movable portion 17b side, and communicates with the groove portion 20, and the refrigerant gas discharged from the discharge port 16 17 easily flows out from the tip end side.
  • the tip side of the reed valve 17 bends smoothly, so that the possibility that a force in the twisting direction acts on the reed valve 17 is reduced. Yes.
  • the tip of the reed valve 17 is bent smoothly, the pressure loss is reduced, and the possibility that the reed valve 17 is deformed or broken is also reduced.
  • the present invention is not limited to the above embodiment, and can be variously modified within the scope of the present invention. That is, the configuration of the above embodiment may be improved as appropriate, or at least a part of the configuration may be replaced with another configuration. Further, the configuration requirements that are not particularly limited with respect to the arrangement are not limited to the arrangement disclosed in the embodiment, and can be arranged at a position where the function can be achieved.
  • the protruding ports are, for example, other compression mechanisms 3 such as the cylinder unit 7. You may form in the part. In that case, a groove portion for accommodating at least a part of the reed valve may be formed around the portion where the discharge port of the compression mechanism portion 3 is formed, and a recess portion communicating with the groove portion may be formed.

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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/JP2015/056498 2015-03-05 2015-03-05 圧縮機 WO2016139796A1 (ja)

Priority Applications (3)

Application Number Priority Date Filing Date Title
PCT/JP2015/056498 WO2016139796A1 (ja) 2015-03-05 2015-03-05 圧縮機
CN201610099436.XA CN105937496A (zh) 2015-03-05 2016-02-23 压缩机
CN201620136050.7U CN205503461U (zh) 2015-03-05 2016-02-23 压缩机

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2015/056498 WO2016139796A1 (ja) 2015-03-05 2015-03-05 圧縮機

Publications (1)

Publication Number Publication Date
WO2016139796A1 true WO2016139796A1 (ja) 2016-09-09

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Application Number Title Priority Date Filing Date
PCT/JP2015/056498 WO2016139796A1 (ja) 2015-03-05 2015-03-05 圧縮機

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CN (2) CN205503461U (zh)
WO (1) WO2016139796A1 (zh)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2016139796A1 (ja) * 2015-03-05 2016-09-09 三菱電機株式会社 圧縮機
JP7032864B2 (ja) * 2017-03-22 2022-03-09 三菱重工サーマルシステムズ株式会社 圧縮機
WO2021111546A1 (ja) * 2019-12-04 2021-06-10 三菱電機株式会社 圧縮機

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH02291485A (ja) * 1989-03-09 1990-12-03 Empresa Brasileira De Compressores Sa Embraco 転動ピストン回転圧縮機のための出口弁
JPH03217686A (ja) * 1990-01-23 1991-09-25 Mitsubishi Heavy Ind Ltd ロータリ圧縮機
JP2000087893A (ja) * 1998-09-10 2000-03-28 Toshiba Corp 冷凍サイクル用圧縮機
JP2006105040A (ja) * 2004-10-06 2006-04-20 Matsushita Electric Ind Co Ltd 圧縮機
JP2010151026A (ja) * 2008-12-25 2010-07-08 Daikin Ind Ltd 圧縮機
JP2012255370A (ja) * 2011-06-08 2012-12-27 Toshiba Carrier Corp 回転式圧縮機及び冷凍サイクル装置
JP2014070595A (ja) * 2012-09-28 2014-04-21 Fujitsu General Ltd ロータリ圧縮機

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2016139796A1 (ja) * 2015-03-05 2016-09-09 三菱電機株式会社 圧縮機

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH02291485A (ja) * 1989-03-09 1990-12-03 Empresa Brasileira De Compressores Sa Embraco 転動ピストン回転圧縮機のための出口弁
JPH03217686A (ja) * 1990-01-23 1991-09-25 Mitsubishi Heavy Ind Ltd ロータリ圧縮機
JP2000087893A (ja) * 1998-09-10 2000-03-28 Toshiba Corp 冷凍サイクル用圧縮機
JP2006105040A (ja) * 2004-10-06 2006-04-20 Matsushita Electric Ind Co Ltd 圧縮機
JP2010151026A (ja) * 2008-12-25 2010-07-08 Daikin Ind Ltd 圧縮機
JP2012255370A (ja) * 2011-06-08 2012-12-27 Toshiba Carrier Corp 回転式圧縮機及び冷凍サイクル装置
JP2014070595A (ja) * 2012-09-28 2014-04-21 Fujitsu General Ltd ロータリ圧縮機

Also Published As

Publication number Publication date
CN105937496A (zh) 2016-09-14
CN205503461U (zh) 2016-08-24

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