EP0768465A1 - Compresseur à gaz - Google Patents

Compresseur à gaz Download PDF

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Publication number
EP0768465A1
EP0768465A1 EP96307357A EP96307357A EP0768465A1 EP 0768465 A1 EP0768465 A1 EP 0768465A1 EP 96307357 A EP96307357 A EP 96307357A EP 96307357 A EP96307357 A EP 96307357A EP 0768465 A1 EP0768465 A1 EP 0768465A1
Authority
EP
European Patent Office
Prior art keywords
side plate
passage
discharge opening
rear side
sectional area
Prior art date
Legal status (The legal status 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 status listed.)
Granted
Application number
EP96307357A
Other languages
German (de)
English (en)
Other versions
EP0768465B1 (fr
Inventor
Koichi Seiko Seiki K.K. Shimada
Seiichiro Seiko Seiki K.K. Yoda
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Seiko Seiki KK
Original Assignee
Seiko Seiki KK
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 Seiko Seiki KK filed Critical Seiko Seiki KK
Publication of EP0768465A1 publication Critical patent/EP0768465A1/fr
Application granted granted Critical
Publication of EP0768465B1 publication Critical patent/EP0768465B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/06—Silencing
    • F04C29/068—Silencing the silencing means being arranged inside the pump housing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/10—Outer members for co-operation with rotary pistons; Casings
    • 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
    • F04C29/0021—Systems for the equilibration of forces acting on the pump
    • F04C29/0035—Equalization of pressure pulses
    • 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
    • F04C18/344—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 inner member
    • F04C18/3446—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 inner member the inner and outer member being in contact along more than one line or surface

Definitions

  • This invention relates to a gas compressor suitable for use as a cooling medium compressor of an air conditioning unit for a vehicle, and particularly to a gas compressor having reduced discharge pulsation and consequently reduced noise.
  • Fig. 5 is a vertical sectional view of a conventional gas compressor
  • Fig. 6 is a sectional view on the line A-A in Fig. 5.
  • This gas compressor has at its centre a cylinder 4 made up of a housing 1 having a substantially elliptical inner peripheral surface and a front side housing side plate 2 and a rear side housing side plate 3 to which front and rear end faces of the housing 1 are respectively fixed.
  • a rotor 6 rotatably supported by a shaft 5 and vanes 7 fitted radially protrudably in the rotor 6 are disposed inside the cylinder 4.
  • Two compression chambers 8 are formed in substantially symmetrical positions between the rotor 6 and the cylinder 4.
  • the housing 1 fixed to the front side housing side plate 2 and the rear side housing side plate 3 is mounted inside a rear housing 9.
  • a front housing 10 is fixed to the outer end face of the front side housing side plate 2.
  • An oil separator 11 for separating oil from the cooling medium gas is fixed to the outer end face of the rear side housing side plate 3.
  • a cooling medium gas discharge port 12 is formed in the upper side of the rear housing 9 and a cooling medium gas intake port 13 is formed in the upper side of the front housing 10.
  • the discharge port 12 connects with a discharge chamber 14 formed by the rear side housing side plate 3 and the rear housing 9, and the intake port 13 connects with an intake chamber 15 formed by the front side housing side plate 2 and the front housing 10.
  • a cylinder discharge opening 16 formed in the housing 1 for discharging compressed cooling medium gas and a reed valve 17 having one end able to open and close the discharge side of the cylinder discharge opening 16 and the other end fixed to the housing 1 are provided in each of two positions substantially symmetrical in the circumferential direction of the housing 1.
  • cooling medium gas compressed in the compression chambers 8 passes through the cylinder discharge openings 16 and the reed valves 17 and then through a first discharge opening, not shown in the drawings, which passes through the rear side housing side plate 3. After that, the cooling medium gas is delivered into the discharge chamber 14 through a metal mesh oil extractor 19 fitted to the oil separator 11. At this time, oil contained in the cooling medium gas is extracted and cooling medium gas having thus had oil removed from it is sent through the discharge port 12 and through a hose not shown in the drawings to a condenser or the like.
  • the rotor 6 shown in Fig. 6 is fitted with five vanes 7, and these perform the processes of intake, compression and discharge of the cooling medium gas. Because the cylinder discharge openings 16 are disposed in substantially opposite positions in the housing 1, five gas pressure fluctuations per rotation of the rotor 6 occur at each one of the cylinder discharge openings 16 as the rotor 6 rotates. Also, because an odd number of vanes 7 are used, gas pressure fluctuations whose phase is different by 180° occur at the respective other, opposite cylinder discharge opening 16. Therefore, compounded gas pressure fluctuations, or pulsations, amounting to 10 per one rotation of the rotor 6 are emitted from the discharge port 12.
  • the number of pulsations per second fluctuates over a wide range because the shaft 5 of the gas compressor is driven by being connected to an engine mounted in the vehicle.
  • the engine speed fluctuates over a range of from about 1000rpm during idling to about 7000 to 8000rpm in the red range. That is, pulsation corresponding to the engine speed occurs and at the same time is the cause of noise which fluctuates greatly in frequency.
  • the present invention was made in view of the kinds of problem described above, and it is an object of the invention to accompany vehicle quietening having been taking place in recent years, to provide a gas compressor from which pulsations leaking to outside are small and which therefore is quiet, and which is small, lightweight and cheap to manufacture.
  • this invention provides a gas compressor comprising a cylinder having a housing both open sides of which are blocked by a rear side housing side plate having a first discharge opening for a gas to pass through and a front side housing side plate, a rotating rotor supported inside the cylinder by a shaft, a compression chamber formed by an outer peripheral surface of the rotor and an inner peripheral surface of the cylinder, an oil separator fixed to an outer end face of the rear side housing side plate and having a second discharge opening for discharging gas compressed in the compression chamber and separating oil from the gas, and a discharge chamber formed by the rear side housing side plate and a rear housing fixed to a peripheral surface of the rear side housing side plate, and characterised in that a silencing passage made small in passage cross-sectional area and long in passage length within such a limit that the silencing passage does not excessively raise the internal pressure of the compression chamber is provided from the first discharge opening in the rear side housing side plate to the second discharge opening in the oil separator.
  • the silencing passage is provided in the outer end face of the rear side housing side plate of the inner end face of the oil separator.
  • this invention provides a gas compressor comprising a cylinder having a housing both open sides of which are blocked by a rear side housing side plate having a first discharge opening for a gas to pass through and a front side housing side plate, a rotating rotor supported inside the cylinder by a shaft, a compression chamber formed by an outer peripheral surface of the rotor and an inner peripheral surface of the cylinder, an oil separator fixed to an outer end face of the rear side housing side plate and having a second discharge opening for discharging gas compressed in the compression chamber and separating oil from the gas, and a discharge chamber formed by the rear side housing side plate and a rear housing fixed to a peripheral surface of the rear side housing side plate, and characterised in that the cross-sectional area of the second discharge opening in the oil separator is made small within such a limit that it does not excessively raise the internal pressure of the compression chamber.
  • the silencing passage is divided into a plurality of passages and the total cross-sectional area of the silencing passage is made small within such a limit that the silencing passage does not excessively raise the internal pressure of the compression chamber.
  • one or more cavities having a larger cross-sectional area than the passage cross-sectional area of the silencing passage are provided in the silencing passage.
  • the cross-sectional area of the second discharge opening in the oil separator is made small within such a limit that the silencing passage does not excessively raise the internal pressure of the compression chamber.
  • a compressing mechanism is equivalent to a cylinder 4 comprising a front side housing side plate 2 and a rear side housing side plate 3 respectively blocking the front and rear ends of a housing 1 and containing a rotor 6 fitted with vanes 7.
  • An oil separator 11 for separating oil from a cooling medium gas is fixed to the outer end face of the rear side housing side plate 3.
  • a metal mesh oil extractor 19 fitted in the oil separator 11 one end of a, for example, copper pipe 25 made small in pipe cross-sectional area and long in pipe length within such a limit that it does not abnormally raise the pressure inside the compression chambers 8 is connected to a discharge opening 20 of the oil separator 11.
  • the other end of the copper pipe 25 is open inside a discharge chamber 14.
  • a coefficient ⁇ of this damping according to Kirchhof is: where C is the speed of sound [m/s] and R is the radius of the pipe.
  • copper pipes 25 were employed by trial and error and made small in pipe cross-sectional area and long in length within such a limit that the pipe did not abnormally raise the pressure inside the compression chambers 8.
  • the present inventors considered the open area of the reed valve 17 when fully open as a pipe cross-sectional area small within such a limit that the pipe does not abnormally raise the pressure inside the compression chambers 8 (and similarly hereinafter).
  • Fig. 2 (A) is a simplified view of the construction of a gas compressor and Fig. 2 (B) is a view of the outer face of a rear side housing side plate 3.
  • the rear side housing side plate 3 is provided with a silencing passage 21 leading from a first discharge opening 18 to a second discharge opening 20 of an oil separator 11.
  • the silencing passage 21 is made small in passage cross-sectional area and long in passage length within such a limit that the passage does not excessively raise the pressure inside a compression chamber 8.
  • the upper surface of the silencing passage 21 is formed by the oil separator 11.
  • the cross-sectional area S1 of the second discharge opening 20 of the oil separator 11 is made small within such a limit that it does not abnormally raise the pressure inside the compression chamber 8.
  • the silencing passage 21 was disposed snaking in a shape avoiding the bolt holes (not shown) as shown in Fig. 2 (B).
  • the passage length of the silencing passage 21 in this preferred embodiment was made 15 centimetres by trial and error. As a result, it was possible to reduce the noise to a considerable degree.
  • a cover for blocking the upper side of the silencing passage 21 may be separately provided, but by utilising the oil separator 11 for this it is possible to reduce the number of parts.
  • silencing passage 21 was disposed in the outer end face of the rear side housing side plate 3, the same results can be obtained by disposing the silencing passage 21 in the inner end face of the oil separator 11.
  • This preferred embodiment has merits such as that compared to the first preferred embodiment the number of parts is reduced because no copper pipe 25 is used, the assembly process is also the same as conventionally, the manufacturing cost does not increase significantly and the reliability and durability of the gas compressor are also the same as conventionally.
  • the amount of damping in this case is related to the ratio of change in cross-sectional area of the pipe. According to calculations based on acoustic impedance, when the ratio of change in cross-sectional area of the pipe S2/S1 is two the amount of damping is about 0.5dB, when it is three the amount of damping is about 2dB and when it is ten the amount of damping is about 5dB.
  • the cross-sectional area S of the second discharge opening 20 of the oil separator 11 small within such a limit that it does not abnormally raise the pressure inside the compression chambers 8 and by discharging the cooling medium gas into a discharge chamber 14 having a different cross-sectional area S2 it is possible to obtain a sound damping effect caused by the change in cross-sectional area S2/S1.
  • the cross-sectional area of the discharge port 12 is the same as conventionally, but nevertheless is amply small compared with the cross-sectional area S2. Since the volume of the discharge chamber 14 is large, a large change in cross-sectional area S2/S 1 can be provided and the sound damping effect is therefore also large.
  • FIG. 3 a third preferred embodiment of the invention is shown in Fig. 3.
  • a rear side housing side plate 3 and an oil separator 11 are of the same construction as in the second preferred embodiment described above, but an auxiliary side plate 22 further provided with a silencing passage 21 is interposed between the rear side housing side plate 3 and the oil separator 11.
  • the effect of this is that it is possible to make the passage length of the silencing passage 21 longer than in the second preferred embodiment by the length by which the silencing passage 21 is extended by the auxiliary side plate 22 and it is thereby possible to reduce the noise even more.
  • the number of auxiliary side plates 22 increases the volume of the discharge chamber 14 decreases it is necessary to achieve a balance of these two considerations.
  • FIGs. 4 (A) to (F) show cases wherein the gas compressor has two compression chambers 8A, 8B and the rear side housing side plate 3 has two first discharge openings 18A, 18B corresponding with these compression chambers.
  • Fig. 4(A) a case wherein cooling medium gas discharged through the two first discharge openings 18A, 18B passes through two silencing passages 21A, 21B and is discharged through two respective second discharge openings 20A, 20B is shown.
  • pulsation components having a phase difference of half a wavelength arising in the two compression chambers 8A, 8B converge inside the discharge chamber 14.
  • the silencing passages 21A, 21B are preferably made small in passage cross-sectional area and long in passage length within such a limit that the passages do not excessively raise the pressure inside the compression chambers 8A, 8B (this point of making the silencing passages small in passage cross-sectional area and long in passage length also applies hereinafter).
  • a case wherein cooling medium gas discharged through two first discharge openings 18A, 18B passes through respective silencing passages 21A, 21B and converges inside the face of the rear side housing side plate 3 and then passes through a single silencing passage 21C and is discharged through a single second discharge opening 20 is shown.
  • pulsation components having a phase difference of half a wavelength arising in the compression chambers 8A, 8B converge inside the face of the rear side housing side plate 3 and the peaks and troughs in the pulsations mutually interfere. That is, a cancelling-out effect caused by the phase difference can be expected.
  • a cooling medium gas discharged through two first discharge openings 18A, 18B passes through respective silencing passages 21A, 21B and converges just before being discharged through a single second discharge opening 20 is shown.
  • pulsation components having a phase difference of half a wavelength arising in the compression chambers 8A, 8B converge and the phases cancel each other out just before being discharged through the single second discharge opening 20 in the rear side housing side plate 3.
  • Fig. 4(D) a case wherein cooling medium gas discharged through two first discharge openings 18A, 18B passes through respective silencing passages 21a, 21b each made up of a plurality of passages and converges just before being discharged through a single second discharge opening 20 is shown. That is, this case is equivalent to a case wherein the silencing passages 21A, 21B of Fig. 4(C) have each been divided up into a plurality of silencing passages 21a, 21b. This dividing up of silencing passages can also be applied to the passages shown in Fig. 4(A) and 4(B).
  • the divided silencing passages may alternatively be disposed individually away from each other.
  • silencing passages 21A, 21B with a plurality of cavities 30 having a cross-sectional area S4 different from the cross-sectional area S3 of the silencing passages, in addition to the effects of making the passage cross-sectional area small and the passage length long in the preferred embodiments described above, it is possible to obtain a sound damping effect caused by the change in ratio of cross-sectional area S4/S3.
  • the cavities 30 may be formed using both the rear side housing side plate 3 and the oil separator 11.
  • Fig. 4(F) a case wherein pluralities of cavities 30 having a cross-sectional area S4 different from the passage cross-sectional area S3 of the silencing passages are provided in the pluralities of silencing passages 21a, 21b shown in Fig. 4(D) is shown.
  • this case in addition to the effects of dividing up the silencing passages and making the passage cross-sectional area of each silencing passage small, it is possible to also obtain a sound damping effect caused by the change in ratio of cross-sectional area S4/S3.
  • the passage cross-sectional area may be changed continuously in the passage length direction to form the cavities 30 (not shown).
  • the damping effect may be improved by changing this to another material.
  • the number of compression chambers and first and second discharge openings is not limited to one or two, and the same effects of the invention can be obtained when there are more than this.
  • the cross-sectional area of the discharge opening of the oil separator is made small, the ratio of the cross-sectional area of the discharge chamber to the cross-sectional area of the discharge opening of the oil separator is larger than conventionally. As a result, it is possible to dampen noise generated along with pulsations by utilising the discharge chamber as a cavity.
  • the silencing passage is divided into a plurality of passages and the total passage cross-sectional area is made small, it is possible to form silencing passages having a much smaller passage cross-sectional area and it is possible to dampen sound more effectively in the silencing passages.
  • the silencing passage is disposed in a rear side housing side plate or the like and the cross-sectional area of a discharge opening of an oil separator is made small, it is possible to obtain the effects of both sound damping caused by the silencing passage and sound damping resulting from the utilisation of the discharge chamber as a cavity. Also, because there are no additional parts, the gas compressor can be made lightweight and small.
  • a gas compressor according to the invention can be constructed without any large design changes and without changing the external appearance at all, and the same reliability of the gas compressor as conventionally can be maintained.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Rotary Pumps (AREA)
EP19960307357 1995-10-09 1996-10-09 Compresseur à gaz Expired - Lifetime EP0768465B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP7286385A JP2858302B2 (ja) 1995-10-09 1995-10-09 気体圧縮機
JP28638595 1995-10-09
JP286385/95 1995-10-09

Publications (2)

Publication Number Publication Date
EP0768465A1 true EP0768465A1 (fr) 1997-04-16
EP0768465B1 EP0768465B1 (fr) 2001-12-12

Family

ID=17703719

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19960307357 Expired - Lifetime EP0768465B1 (fr) 1995-10-09 1996-10-09 Compresseur à gaz

Country Status (3)

Country Link
EP (1) EP0768465B1 (fr)
JP (1) JP2858302B2 (fr)
DE (1) DE69617865T2 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2568180A1 (fr) * 2011-09-12 2013-03-13 Pierburg Pump Technology GmbH Pompes à cellules battantes
CN107869459A (zh) * 2017-11-14 2018-04-03 美的集团股份有限公司 水泵
CN108626098A (zh) * 2018-06-28 2018-10-09 安徽美芝制冷设备有限公司 排气消音器及压缩机

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4505108B2 (ja) * 2000-05-10 2010-07-21 株式会社フジ医療器 マッサージ器用空気供給排出装置
KR100953626B1 (ko) * 2009-06-18 2010-04-20 캄텍주식회사 차량용 진공펌프
WO2011126032A2 (fr) * 2010-03-31 2011-10-13 ナブテスコオートモーティブ株式会社 Pompe à vide
KR101347742B1 (ko) * 2012-04-19 2014-01-03 캄텍주식회사 펌프유닛 및 차량용 진공 펌프
JP7128426B1 (ja) * 2021-03-31 2022-08-31 ダイキン工業株式会社 圧縮機

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
BE402771A (fr) *
GB1180079A (en) * 1967-09-29 1970-02-04 Niles Pressluftwerkzeuge Berli Improvements in or relating to Pneumatic Rotary-Piston Motors.
DE3903054A1 (de) * 1988-02-10 1989-08-24 Diesel Kiki Co Rotationskolbenverdichter
DE9113962U1 (de) * 1991-11-09 1992-02-27 Wilms, Peter, 4355 Waltrop Schalldämpfer für einen Schraubenverdichter
DE4421771A1 (de) * 1993-06-23 1995-01-12 Toyoda Automatic Loom Works Drehschieber-Kompressor

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
BE402771A (fr) *
GB1180079A (en) * 1967-09-29 1970-02-04 Niles Pressluftwerkzeuge Berli Improvements in or relating to Pneumatic Rotary-Piston Motors.
DE3903054A1 (de) * 1988-02-10 1989-08-24 Diesel Kiki Co Rotationskolbenverdichter
DE9113962U1 (de) * 1991-11-09 1992-02-27 Wilms, Peter, 4355 Waltrop Schalldämpfer für einen Schraubenverdichter
DE4421771A1 (de) * 1993-06-23 1995-01-12 Toyoda Automatic Loom Works Drehschieber-Kompressor

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2568180A1 (fr) * 2011-09-12 2013-03-13 Pierburg Pump Technology GmbH Pompes à cellules battantes
CN107869459A (zh) * 2017-11-14 2018-04-03 美的集团股份有限公司 水泵
CN108626098A (zh) * 2018-06-28 2018-10-09 安徽美芝制冷设备有限公司 排气消音器及压缩机

Also Published As

Publication number Publication date
EP0768465B1 (fr) 2001-12-12
JP2858302B2 (ja) 1999-02-17
DE69617865D1 (de) 2002-01-24
DE69617865T2 (de) 2002-04-25
JPH09105393A (ja) 1997-04-22

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