WO2015156144A1 - Compresseur - Google Patents

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Publication number
WO2015156144A1
WO2015156144A1 PCT/JP2015/059534 JP2015059534W WO2015156144A1 WO 2015156144 A1 WO2015156144 A1 WO 2015156144A1 JP 2015059534 W JP2015059534 W JP 2015059534W WO 2015156144 A1 WO2015156144 A1 WO 2015156144A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve
seat plate
valve seat
port
compressor
Prior art date
Application number
PCT/JP2015/059534
Other languages
English (en)
Japanese (ja)
Inventor
池田　英明
康輔 貞方
Original Assignee
株式会社日立産機システム
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 株式会社日立産機システム filed Critical 株式会社日立産機システム
Priority to CN201580017575.7A priority Critical patent/CN106164488B/zh
Priority to JP2016512662A priority patent/JP6581567B2/ja
Publication of WO2015156144A1 publication Critical patent/WO2015156144A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/10—Adaptations or arrangements of distribution members

Definitions

  • the present invention relates to a compressor.
  • Patent Document 1 JP 2007-146761
  • an annular valve seat surface surrounding the discharge hole is formed on the valve plate, an annular seal surface surrounding the annular valve seat surface is formed on the valve plate, and the annular valve seat surface is on the cylinder bore side relative to the annular seal surface.
  • the shape of the annular valve seat surface surrounding the discharge hole of the reciprocating compressor of Patent Document 1 and the annular seal surface surrounding the annular valve seat surface is constant regardless of the circumferential position.
  • the pressure difference applied to the valve increases, and the amount of deformation of the valve increases between the open end side and the fixed end side of the valve.
  • the discharge hole of the reciprocating compressor of Patent Document 1 is not shaped to follow the deformation of the valve, the sealing performance was lowered.
  • the reciprocating compressor of Patent Document 1 cannot improve the compression efficiency because the compressed air flows backward from the discharge chamber side of the cylinder to the compression chamber side particularly when trying to obtain high-pressure compressed air. It was.
  • an object of the present invention is to provide a compressor that improves the sealing performance between a valve and a discharge (suction) port, suppresses the backflow of compressed air, and improves the compression efficiency.
  • the present invention provides a reciprocating compressor in which a motor compresses fluid by driving a piston, and a valve seat plate provided with a port through which fluid passes as the piston reciprocates;
  • the valve seat plate is provided with a valve that opens and closes the port, and an inclined surface that is lowered toward the center of the port is formed on a surface of the valve seat plate that contacts the valve.
  • the present invention it is possible to provide a compressor that improves the sealing performance between the valve and the discharge (suction) port, suppresses the backflow of compressed air, and improves the compression efficiency.
  • Sectional drawing (top dead center) of the compression part of the compressor concerning the Example of this invention Sectional drawing (bottom dead center) of the compression part of the compressor concerning the Example of this invention Detailed view of valve seat plate and valve of compressor according to embodiment of the present invention
  • Sectional drawing of the compressor concerning the Example of this invention Detailed view of valve seat plate and valve of compressor according to modification of the present invention
  • the piston 21 provided in the cylinder 11 so as to be able to reciprocate is constituted by a disk-like retainer 24 fastened to a connecting rod 22 by a bolt 23.
  • the cylinder 11 is connected to the crankcase 1.
  • the crankcase 1 accommodates a drive source such as a motor, and the piston 21 is connected to a rotating shaft 2 of the motor via an eccentric shaft 3 and a bearing 4.
  • the motor is driven, the rotary shaft 2 rotates, and the rotary motion of the rotary shaft 2 is converted into the eccentric motion of the eccentric shaft 3 via the bearing 4.
  • the piston 21 connected to the eccentric shaft 3 reciprocates while swinging in the cylinder 11.
  • the piston 21 compresses a fluid such as air by reciprocating while swinging in the cylinder 11.
  • the lip ring 25 provided on the outer peripheral side of the swing piston 21 is formed in a ring shape using a resin material. Further, the lip ring 25 is sandwiched between the connecting rod 22 and the retainer 24 and is fixed in a state of being fastened by the bolt 23. Further, the lip ring 25 is in sliding contact with the inner peripheral surface of the cylinder 11 with a tightening margin. The lip ring 25 expands and contracts following the swing of the swing piston 21 and seals between the piston 21 and the cylinder 11.
  • valve seat plate 14 fixed between the cylinder 11 and the cylinder head 12 is provided with a discharge port 17. Further, a valve 18 that opens and closes the discharge port due to a pressure difference is fixed to the valve seat plate 14 by a bolt 19.
  • valve 18 contacts the valve seat plate 14 and the discharge port 17 is closed.
  • the pressure inside the cylinder 11 rises and the pressure difference between the upper and lower sides of the valve 18 increases, the valve 18 is pushed up and the valve seat plate 14 is raised.
  • the discharge port 17 is opened. At this time, air is discharged from the compression chamber 7 to the discharge chamber 6, and the air is compressed.
  • the valve 18 opens and closes the discharge port, and the air sucked in the suction process is discharged from the cylinder to the tank connected to the outside in the discharge process, thereby compressing the air.
  • valve seat plate in the present embodiment will be described with reference to FIG.
  • the pressure on the discharge chamber 6 side of the valve 18 (the upper side when the valve 18 is placed on the valve seat plate 14) is high, and the pressure on the compression chamber 7 side (the valve 18 on the valve seat plate 14).
  • the pressure on the lower side is low, the pressure difference applied to the valve 18 becomes large, and the valve 18 is deformed by strongly contacting the valve seat plate 14.
  • the valve seat plate 14 is not formed in a shape considering the deformation of the valve 18, a gap is formed between the valve 18 and the valve seat plate 14, and the sealing performance of the discharge port 17 is lowered.
  • the valve 18 is a fixed end with one end fixed by a bolt 19 and the other end is an open end.
  • the deformation of the valve 18 around the discharge port 17 varies depending on the circumferential direction of the discharge port 17.
  • the deformation angle ⁇ on the open end side 18a of the valve 18 and the deformation angle ⁇ on the fixed end side 18b have a relationship of ⁇ > ⁇ . That is, the closer to the open end, the larger the deformation angle, and the closer to the fixed end, the smaller the deformation angle.
  • the inclined portion 14a is provided on the surface of the valve seat plate 14 on the side in contact with the valve 18 to form an inclined surface.
  • the valve 18 is arranged so as to be above the valve seat plate 14, the inclined surface is formed so as to become lower as it approaches the discharge port 17.
  • the inclined surface is not formed as a chamfer at the time of forming the discharge port 17, but is formed to improve the sealing performance by contacting the valve 18 and the valve seat plate 14 with a width as described above. Although it depends on the dimensions of the valve 18 and the valve seat plate, the inclination angle of the inclined surface is 10 ° or less. Further, in order to further improve the sealing performance, the inclination angle of the inclined surface is made different depending on the position in the circumferential direction corresponding to the deformation of the valve 18. Specifically, the inclined portion 14a of the valve seat plate 14 has a shape in which the inclination angle on the open end side of the valve 18 is large ( ⁇ ) and the inclination angle on the fixed end side is small ( ⁇ ). That is, the closer to the open end, the greater the inclination angle, and the closer to the fixed end, the smaller the inclination angle.
  • the ratio h / r is h / r. r differs depending on the position in the circumferential direction. At this time, h / r increases as it approaches the open end of the valve 18 and decreases as it approaches the fixed end.
  • the inclination angles ( ⁇ ) and ( ⁇ ) and the ratio h / r of the inclined portion are preferably determined by taking into consideration the deformation amount and sealing performance of the valve 18 by simulation and measurement.
  • the inclination angle of the inclined portion and the ratio h / r may be a constant value regardless of the position in the circumferential direction, and the valve 18 and the valve seat plate 14 are in contact with each other with a width, so that the sealing performance can be improved. .
  • valve seat plate 14 corresponds to the deformation of the valve 18, the valve 18 is not deformed such as minute undulations or wrinkles in the circumferential direction, and the valve 18 and the valve seat shown in FIG.
  • the valve 18 and the valve seat plate 14 come into contact with each other with a certain width over the entire circumference as in the surface pressure distribution of the contact portion with the plate 14 (becomes surface contact), and the clearance between the valve seat plate 14 and the valve 18 is reduced. Can be small. Therefore, in the suction process, the backflow from the discharge chamber 6 to the compression chamber 6 can be effectively prevented, and the discharge performance can be improved.
  • the deformation (swell) of the fixed end side portion 18c of the valve 18 is reduced, and the stress generated in this portion can be reduced. For this reason, the thickness of the valve 18 can be reduced, the sound of the valve 18 hitting the valve seat plate 14 can be suppressed, and the noise during operation of the compressor can be suppressed.
  • the inclined portion 14a of the valve seat plate 14 is configured to be smoothly connected to the circumferential direction. Since the amount of deformation of the valve 18 continuously changes in the circumferential direction, the inclination angle of the inclined portion 14a of the valve seat plate 14 and the ratio h / r of h and r also change correspondingly. By doing so, the backflow from the discharge chamber 6 to the compression chamber 6 can be more effectively prevented, and the discharge performance can be improved.
  • valve seat plate 14 on the discharge port 17 side has been described.
  • the same configuration is applied to the shape of the valve seat plate on the suction port side, thereby improving the sealing performance between the valve and the suction port. Compression performance can be improved.
  • the flat inclined portion 14a is formed on the valve seat plate 14.
  • the inclined portion 14a may be curved instead of flat.
  • the ratio h / r is h / r. r differs depending on the position in the circumferential direction. h / r increases as it approaches the open end of the valve 18 and decreases as it approaches the fixed end.
  • the inclined portion 14a is formed on the valve seat plate 14, but a stepped portion may be used instead of the inclined portion 14a.
  • the valve seat plate 14 is provided with a plurality of step portions 14b, and the difference in height between the radially outer side and the radially inner side viewed from the center of the discharge port 17 (because there are a plurality of steps in FIG. 5).
  • the difference in height between the highest and the lowest) is h
  • the radial length of the step is r (in FIG. 5, there are multiple steps, so the difference between the closest and farthest to the port)
  • H / r ratio h / r varies depending on the position in the circumferential direction.
  • h / r increases as it approaches the open end of the valve 18 and decreases as it approaches the fixed end.
  • the stepped portion 14b is provided in a plurality of steps, the stepped corner 14c of the valve 18 and the valve seat plate 14 is in line contact with each other in a circumferential shape, and a plurality of line contacts are formed.
  • a plurality of minute gaps can be formed in the leakage passage, backflow (leakage) from the discharge chamber 6 to the compression chamber 6 can be effectively prevented by the labyrinth effect and the discharge performance can be improved.
  • a combination of an inclined portion and a step portion may be formed on the valve seat plate.
  • the sealing performance is improved by reducing the gap between the valve 18 and the valve seat plate 14. It is possible to improve the discharge performance by effectively preventing the backflow of compressed air.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)

Abstract

　L'invention concerne un compresseur dans lequel l'étanchéité d'une soupape et d'un orifice d'évacuation (admission) est améliorée, le refoulement d'air comprimé est réduit au minimum, et l'efficacité de la compression est améliorée. Pour atteindre cet objectif, l'invention concerne un compresseur pour comprimer un fluide dans l'entraînement d'un moteur. Le compresseur est caractérisé en ce qu'il comprend : une plaque de siège de soupape pourvue d'un orifice traversé par le fluide, et une soupape située sur la plaque de siège de soupape, la soupape ouvrant et fermant l'orifice, une surface inclinée qui descend vers le centre de l'orifice étant formée dans la surface de la plaque de siège de soupape qui est en contact avec la soupape.
PCT/JP2015/059534 2014-04-07 2015-03-27 Compresseur WO2015156144A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
CN201580017575.7A CN106164488B (zh) 2014-04-07 2015-03-27 压缩机
JP2016512662A JP6581567B2 (ja) 2014-04-07 2015-03-27 圧縮機

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2014-078300 2014-04-07
JP2014078300 2014-04-07

Publications (1)

Publication Number Publication Date
WO2015156144A1 true WO2015156144A1 (fr) 2015-10-15

Family

ID=54287721

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2015/059534 WO2015156144A1 (fr) 2014-04-07 2015-03-27 Compresseur

Country Status (3)

Country Link
JP (1) JP6581567B2 (fr)
CN (1) CN106164488B (fr)
WO (1) WO2015156144A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2021065038A1 (fr) * 2019-10-01 2021-04-08 株式会社日立産機システム Compresseur

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN111120266B (zh) * 2018-10-31 2022-04-15 广东美芝制冷设备有限公司 压缩机的排气结构和具有其的压缩机

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2003120563A (ja) * 2001-10-09 2003-04-23 Seiko Instruments Inc 気体圧縮機
JP2007146761A (ja) * 2005-11-28 2007-06-14 Sanden Corp 往復動圧縮機
WO2012043017A1 (fr) * 2010-09-27 2012-04-05 大豊工業株式会社 Pompe à palettes

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE69200356T2 (de) * 1991-01-28 1995-02-16 Sanden Corp Schiefscheibenverdichter mit einer Vorrichtung zur Hubveränderung.
US5586874A (en) * 1994-11-15 1996-12-24 Sanden Corporation Reed valve arrangement for a reciprocating compressor
CN1083063C (zh) * 1995-04-20 2002-04-17 Lg电子株式会社 密闭式压缩机的带有阀装置的气缸盖

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2003120563A (ja) * 2001-10-09 2003-04-23 Seiko Instruments Inc 気体圧縮機
JP2007146761A (ja) * 2005-11-28 2007-06-14 Sanden Corp 往復動圧縮機
WO2012043017A1 (fr) * 2010-09-27 2012-04-05 大豊工業株式会社 Pompe à palettes

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2021065038A1 (fr) * 2019-10-01 2021-04-08 株式会社日立産機システム Compresseur

Also Published As

Publication number Publication date
JP6581567B2 (ja) 2019-09-25
JPWO2015156144A1 (ja) 2017-04-13
CN106164488A (zh) 2016-11-23
CN106164488B (zh) 2019-05-07

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