EP2390508B1 - Ansaugöffnung eines Schraubenverdichters - Google Patents

Ansaugöffnung eines Schraubenverdichters Download PDF

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Publication number
EP2390508B1
EP2390508B1 EP11167299.4A EP11167299A EP2390508B1 EP 2390508 B1 EP2390508 B1 EP 2390508B1 EP 11167299 A EP11167299 A EP 11167299A EP 2390508 B1 EP2390508 B1 EP 2390508B1
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EP
European Patent Office
Prior art keywords
lobe
female
male
rotor
working chamber
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.)
Active
Application number
EP11167299.4A
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English (en)
French (fr)
Other versions
EP2390508A2 (de
EP2390508A3 (de
Inventor
Masanori Ishikawa
Hirotaka Kameya
Riichi Uchida
Seiji Tsuru
Takashi Saito
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.)
Hitachi Industrial Equipment Systems Co Ltd
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Hitachi Industrial Equipment Systems Co Ltd
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
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Publication of EP2390508A2 publication Critical patent/EP2390508A2/de
Publication of EP2390508A3 publication Critical patent/EP2390508A3/de
Application granted granted Critical
Publication of EP2390508B1 publication Critical patent/EP2390508B1/de
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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
    • F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C18/14—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F04C18/16—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
    • 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
    • F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C18/082—Details specially related to intermeshing engagement type pumps
    • F04C18/086—Carter
    • 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
    • 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
    • F04C2250/10—Geometry of the inlet or outlet
    • F04C2250/101—Geometry of the inlet or outlet of the inlet

Definitions

  • the present invention relates to a screw compressor, and particularly relates to a shape of an axial suction port of an oil free type screw compressor including a timing gear.
  • JP-A-06-288369 describes a contour shape preferable for an axial suction port of a screw compressor including a working chamber in which a volumetric change is temporarily discontinued. Further, JP-A-10-9164 describes a method for increasing a suction flow rate by performing suction operation intermittently.
  • JP-A-06-288369 and JP-A-10-9164 have not been applied widely and generally because certain conditions are required for the structure of the screw compressor to which those can be applied and for the usage thereof. Accordingly, there has been the problem of embodying the structure for increasing the suction amount that can be applied to many screw compressors.
  • US 2457314 A discloses a rotary screw wheel device in which intermeshing rotors having helical lands and grooves cooperate with each other and with an enclosing casing to form working chambers which vary in volume as the rotors revolve.
  • US 2481527 A discloses rotary multiple helical rotor machine which provides working chamber between intermeshing rotors of the screw wheel type mounted in a suitable casing.
  • the teaching of the two latter documents generally relates to the effect of the shape of the suction port opening and closing on pressure waves travelling along the working chambers.
  • an object of the present invention is to propose a configuration which can enhance energy efficiency and volume efficiency in a screw compressor of an ordinary configuration.
  • the invention provides a screw compressor including a male rotor having a helical lobe, a female rotor having a helical lobe, a casing forming a bore for accommodating the lobes of the male female rotors in a state where the lobes mesh with each other, an axial suction port provided on a suction side of the casing, and a delivery port provided on a delivery side of the casing, wherein the axial suction port is configured by a contour line including a line along a male lobe profile and a line along a female lobe profile, and the line along the male lobe profile is disposed at a predetermined displacement angle toward a rotational direction side of the male rotor from a following side contour line position of a male lobe groove in the rotational angle of the male rotor, at which following side contour line position the volume of a working chamber formed by being enclosed by the male lobe groove of the male rotor,
  • the invention provides a screw compressor including a male rotor having a helical lobe, a female rotor having a helical lobe, a casing forming a bore for accommodating the lobes of the male and female rotors in a state where the lobes mesh with each other, an axial suction port provided on a suction side of the casing, and a delivery port provided on a delivery side of the casing, wherein the axial suction port is configured by a contour line including a line along a male lobe profile and a line along a female lobe profile, and the line along the female lobe profile is disposed at a predetermined displacement angle toward a rotational direction side of the female rotor from a following side contour line position of a female lobe groove in the rotational angle of the female rotor, at which following side contour line the volume of a working chamber formed by being enclosed by a male lobe groove of the male rotor, the female lobe groove
  • the compressor which increases the suction amount and is highly efficient can be realized.
  • Fig. 3 is a schematic sectional view of a screw compressor.
  • Reference numeral 1 designates a male rotor having a helical lobe
  • reference numeral 2 designates a female rotor having a helical lobe.
  • the male rotor 1 and the female rotor 2 are housed in a bore 4 formed inside a casing 3 in a state where those mesh with each other.
  • the bore 4 is of a shape of two cylinders of which parts overlapping each other, and more specifically, is configured by four surfaces which are a cylindrical outer peripheral surface with which a lobe portion of the male rotor 1 is covered, a cylindrical outer peripheral surface with which a lobe portion of the female rotor 2 is covered, a suction end 7, and a delivery end 8.
  • the suction end 7 is provided with an axial suction port 11 which will be described later, and the delivery end 8 is provided with a delivery port not illustrated.
  • a timing gear 10 which is provided at one end of a shaft of the male rotor 1 and a timing gear 10 which is provided at one end of a shaft of the female rotor 2 are disposed to mesh with each other, so that the female rotor 2 is configured to be rotationally driven synchronously with rotational drive of the male rotor 1.
  • a space where a male lobe groove 5 of the male rotor 1 and a female lobe groove 6 of the female rotor 2 communicate with each other is covered with the bore 4, and forms a working chamber 9 which is a closed space. Since there are a plurality of spaces where the male lobe groove 5 and the female lobe groove 6 communicate with each other, a plurality of working chambers 9 are formed.
  • Each of the working chambers 9 moves toward the direction of the delivery end 8 from the suction end 7 in accordance with rotation of both rotors.
  • backlash of the timing gears 10 is designed to be smaller than backlash of the lobe portions of the male rotor 1 and the female rotor 2, and the lobe portions of the male rotor 1 and the female rotor 2 are not brought into contact with each other. Therefore, each of the working chambers 9 is not a closed space in strict meaning, and accordingly is connected to the adjacent working chambers through a clearance. However, the amount of gas which leaks into the adjacent working chamber 9 through the clearance is so small that it can be ignored.
  • Figs. 4A and 4B are views explaining an ordinary shape of the axial suction port 11 which is provided in the suction end 7 of the bore 4.
  • the male rotor 1 rotates clockwise
  • the female rotor 2 rotates counterclockwise.
  • the working chamber 9 which is generated in a position where both rotors on the suction end 7 are in contact with each other enlarges its inner volume while a leading head of the working chamber 9 moves toward the delivery end 8 in accordance with rotation of both rotors.
  • gas to be compressed is supplied to the working chamber 9 via the axial suction port 11.
  • a contour line 15 on the male rotor 1 side and a contour line 18 on the female rotor 2 side of the axial suction port 11 are provided at a position where the inner volume of the working chamber 9 is maximum. More specifically, during the time period in which the inner volume of the working chamber 9 is enlarged, the gas to be compressed is supplied to the working chamber 9 communicating with the axial suction port 11, and during the time period in which the inner volume of the working chamber 9 is reduced, new gas to be compressed is not supplied to the working chamber 9 which does not communicate with the axial suction port 11. Thereafter, in accordance with rotation of both rotors, the inner volume of the working chamber 9 is reduced, and therefore, the gas to be compressed in the working chamber 9 is compressed. The gas to be compressed which has been compressed is discharged from the delivery port which is provided in the delivery end 8.
  • FIG. 1A is a view explaining a shape in embodiment 1 of the axial suction port 11 provided in the suction end 7 of the bore 4.
  • the male rotor 1 rotates clockwise, whereas the female rotor 2 rotates counterclockwise.
  • the working chamber 9 which is the nearest to the delivery side and shown by the oblique lines is in a position where the working chamber 9 has the maximum volume, and the working chambers which are located on the suction side from that position are in the suction process by enlargement of the volume.
  • the contour line of the axial suction port 11 is configured by seven contour lines that are a line 13 of a meshing portion, a circular arc 14 along a male lobe bottom diameter, the line 15 along a male lobe profile, a circular arc 16 along a male lobe tip diameter, a circular arc 17 along a female lobe tip diameter, the line 18 along a female lobe profile and a circular arc 19 along a female lobe bottom diameter.
  • the line 15 along the male lobe profile and the line 18 along the female lobe profile which are the contour lines that have a large effect on the performance of the compressor, will be described in detail.
  • the working chamber 9 with the maximum volume shown by hatching in Fig. 1A is in contact with the suction end 7 and the delivery end 8 at both male and female sides.
  • the contour of the groove of each of the rotors in the suction end 7 will be studied by dividing the contour into two on an advance side and a following side with respect to the rotor rotation. Among those, the following side has a large effect on the performance of the compressor, and therefore, attention will be paid on a following side contour line 21 of the male lobe groove 5 and a following side contour line 22 of the female lobe groove 6 hereinafter.
  • the line 15 along the male lobe profile is provided at a position which is displaced clockwise by ⁇ f1 from a position of the following side contour line 21 at the timing when the working chamber 9 has the maximum volume.
  • the positional precision of the line 15 along the male lobe profile has to be within 1/20 of the rotor diameter.
  • the line 18 along the female lobe profile is provided at a position which is displaced counterclockwise by ⁇ f2 from a position of the following side contour line 22 at the timing when the working chamber 9 has the maximum volume.
  • the positional precision of the line 18 along the female lobe profile has to be within 1/20 of the rotor diameter.
  • the positional relation of the working chamber 9 and the axial suction port 11 will be described by using the development of the bore 4 as shown in Fig. 2 .
  • the right side is a development of the male side cylinder
  • the left side is a development of the female side cylinder.
  • a lower end of the development is the suction end 7, whereas an upper end is the delivery end 8.
  • the axial suction port 11 which is adjacent to the suction end 7, and has both ends defined by the line 15 along the male lobe profile and the line 18 along the female lobe profile is opened.
  • a vertical line in the center which is designated by reference numeral 31 is an expansion side cusp which is on an expansion side, of intersection lines of the male side cylinder and the female side cylinder.
  • Vertical lines at both left and right sides designated by reference numerals 32 are compression side cusps which are on a compression side, of the intersection lines of the male side cylinder and the female side cylinder of the bore 4.
  • Oblique lines 24 and 25 and the oblique lines parallel with them show lobe tip lines of each of the rotors.
  • the working chambers facing the axial suction port 11 take the gas to be compressed in, and the working chambers which do not face the axial suction port 11 do not take the gas to be compressed in.
  • FIG. 5 a suction stroke of the gas to be compressed to the working chamber of the screw compressor having the configuration described above will be described.
  • (a) shows the volume of the working chamber when the rotors are rotated.
  • (b) shows the volumetric change rate of the working chamber that is obtained by differentiating (a).
  • (c) shows a volume flow rate which is sucked by the working chamber.
  • the axial suction port 11 of the present embodiment is larger than the ordinary axial suction port by the fact that the axial suction port opening time period is longer than the working chamber volume increasing time period.
  • a rotational angle of the rotors that is generated at a contact point of the suction end 7 and the expansion side cusp 31 by the working chamber formed by the male lobe groove and the female lobe groove communicating with each other is set as ⁇ 0 .
  • the male lobe groove and the female lobe groove are connected to each other at the opening of the working chamber in the suction end 7.
  • the opening of the working chamber in the suction end 7 is separated to a male lobe groove side and a female lobe groove side.
  • Fig. 6 shows the state of the flow of the gas to be compressed which is sucked to the rotors through the suction port from the suction side casing. Since suction in the state close to a stationary state where the inertia effect accompanying the suction is small is conventionally assumed, the flow velocity of the gas to be compressed sucked from the rotors has a sufficiently large inertia effect, and in the present embodiment, the volume efficiency is enhanced by increasing the suction quantity by adopting a shape of the axial suction port 11 which can utilize the inertia effect.
  • a groove length L' in the axial direction of the working chamber can be expressed assuming that the groove bottom radius is minimum as follows ( ⁇ is in a radian unit).
  • L ' 2 ⁇ R ⁇ ⁇ / 2 ⁇ 2 + L 2
  • the gas to be compressed which has flown into the working chamber is considered to have a temperature and a pressure substantially equal to a port temperature and a port pressure before shifting to the compression process.
  • a sound velocity of the gas to be compressed at this time is set as "a". With respect to the case of a non oil free type, the sound velocity is defined by the sound velocity corrected with a vapor quantity of oil, water or the like.
  • the working chamber volume is enlarged the stage at which the working chamber volume is minimum in accordance with rotation of the rotor from, and the volume enlargement of the working chamber becomes maximum at the stage at which the working chamber reaches the delivery end.
  • a displacement angle ⁇ f ⁇ ⁇ 2 ⁇ R ⁇ ⁇ / 2 ⁇ 2 + L 2 / a
  • a male rotor side groove length L'm is shorter than a female rotor side groove length L'f
  • ⁇ t 3.7 ⁇ 10 -4 sec
  • the wrap angle ⁇ f 150°
  • the rotor axial length L 100 mm
  • air is used as the gas to be compressed
  • the sound velocity a 340 m/s
  • the rotational speed of the female rotor is set as 200 rev/sec
  • the suction opening sectional area and the suction time can be increased, and the suction volume efficiency can be enhanced.
  • the working chamber in the suction process can suck the gas to be compressed smoothly with low pressure loss, and the suction quantity can be increased while backflow of the gas to be compressed which is once sucked from the working chamber is prevented.
  • the present invention is applicable to any kind of gas. Further, the condition is defined by the shape (mainly, the length) of the working chamber 9 formed by the male rotor 1 and the female rotor 2, the present invention is applicable to various rotor lobe shapes, and the material of the rotor is not limited.
  • the axial suction port 11 is closed on the male and female sides at the same timing, but in example 1 only the contour line 15 which is the male side contour line of the axial suction port 11 is closed at the closing timing described in embodiment 1.
  • the axial suction port 11 is closed on the male and female sides at the same timing, whereas in example 2 only the contour line 18 which is the female side contour line of the axial suction port 11 is closed at the closing timing described in embodiment 1.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Claims (1)

  1. Schraubenkompressor, der aufweist:
    einen Rotor (1) mit einem konvexen Schraubenprofil;
    einen Rotor (2) mit einem konkaven Schraubenprofil;
    ein Gehäuse (3), in dem eine Bohrung (4) ausgebildet ist zur Aufnahme des Schraubenprofils des Rotors mit konvexem Profil und des Schraubenprofils des Rotors mit konkavem Profil in einem Zustand, in dem die Schraubenprofile miteinander in Eingriff sind;
    einer axialen Ansaugöffnung (11), die auf der Ansaugseite des Gehäuses vorgesehen ist, und
    eine Auslassöffnung, die auf der Auslassseite des Gehäuses vorgesehen ist, wobei
    die axiale Ansaugöffnung (11) durch eine Konturlinie definiert ist, die eine Linie (15) entlang einem konvexen Schraubenprofil und eine Linie (18) entlang einem konkaven Schraubenprofil einschließt,
    dadurch gekennzeichnet, dass
    die Konturlinie der axialen Ansaugöffnung aus sieben Konturlinien aufgebaut ist, die bestehen aus einer Linie (13) eines Eingriffs-Abschnitts, einem Kreisbogen (14) entlang einem Durchmesser des Bodens des konvexen Schraubenprofils, der Linie (15) entlang dem konvexen Schraubenprofil, einem Kreisbogen (16) entlang einem Durchmesser der Spitze des konvexen Schraubenprofils, einem Kreisbogen (17) entlang einem Durchmesser der Spitze des konkaven Schraubenprofils, der Linie (18) entlang dem konkaven Schraubenprofil und einem Kreisbogen (19) entlang einem Durchmesser des Bodens des konkaven Schraubenprofils,
    die Linie (15) entlang dem konvexen Schraubenprofil so ausgebildet ist, dass sie um einen vorgegebenen Versetzungswinkel zu der Drehrichtungsseite des konvexen Rotors hin von einer folgeseitigen Konturlinienposition (21) einer Vertiefung (5) des konvexen Profils bei einem Drehwinkel des konvexen Rotors (1) zu der Zeit versetzt ist, wenn das Volumen einer Arbeitskammer (9), die durch Einschließen durch die Vertiefung (5) des konvexen Profils des konvexen Rotors, eine Vertiefung (6) des konkaven Profils des konkaven Rotors und die Bohrung (4) gebildet wird, maximal ist,
    die Linie (18) entlang dem konkaven Schraubenprofil so ausgebildet ist, dass sie um einen vorgegebenen Versetzungswinkel zu der Drehrichtungsseite des konkaven Rotors hin von einer folgeseitigen Konturlinienposition (22) einer Vertiefung (6) des konkaven Profils bei einem Drehwinkel des konkaven Rotors (2) zu der Zeit versetzt ist, wenn das Volumen der Arbeitskammer (9) maximal ist,
    die axiale Ansaugöffnung (11) so ausgebildet ist, dass die Ansaugöffnung nach einer Zeit geschlossen ist, die erforderlich ist, um das zu komprimierende Gas durch die Länge eines Profilabschnitts des Rotors bei der Schallgeschwindigkeit von der Zeit zu bewegen, wenn die Arbeitskammer das Auslassende (8) erreicht, ferner von einer Position in einem Prozess der Volumenverringerung durch den Drehwinkel, bei dem das Volumen der Arbeitskammer im Wesentlichen maximal ist, und
    die Konturlinie der axialen Ansaugöffnung (11) so ausgebildet ist, dass sie sowohl einen Abschnitt entlang einer Konturlinie an dem Ende, das sich auf der Rückseite der Rotation einer Vertiefung des konvexen Rotors befindet, die eine Teil der Arbeitskammer (9) bildet, als auch einen Abschnitt entlang einer Konturlinie an dem Ende, das sich auf der Rückseite der Rotation einer Vertiefung des konkaven Rotors befindet, einschließt, von einem Drehwinkel der Rotoren, wo die Arbeitskammer (9) nach einer Zeit geschlossen ist, die erforderlich ist, um das zu komprimierende Gas bei der Schallgeschwindigkeit durch die Länge eines Profilabschnitts des Rotors zu bewegen, nachdem die Arbeitskammer (9) das Auslassende erreicht nach dem Drehwinkel des Rotors, bei dem das Volumen der Arbeitskammer im Wesentlichen maximal ist, und sie so ausgebildet ist, dass sie auf der der Drehrichtung entgegengesetzten Seite des konvexen und des konkaven Rotors von den Konturlinien offen ist und auf der Seite der Drehrichtung mit dem Ende der Bohrung geschlossen ist.
EP11167299.4A 2010-05-25 2011-05-24 Ansaugöffnung eines Schraubenverdichters Active EP2390508B1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2010118883A JP5478362B2 (ja) 2010-05-25 2010-05-25 スクリュー圧縮機

Publications (3)

Publication Number Publication Date
EP2390508A2 EP2390508A2 (de) 2011-11-30
EP2390508A3 EP2390508A3 (de) 2014-09-24
EP2390508B1 true EP2390508B1 (de) 2018-03-28

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EP11167299.4A Active EP2390508B1 (de) 2010-05-25 2011-05-24 Ansaugöffnung eines Schraubenverdichters

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EP (1) EP2390508B1 (de)
JP (1) JP5478362B2 (de)
CN (2) CN103541899B (de)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP6619987B2 (ja) * 2015-10-26 2019-12-11 株式会社アルバック スクリューポンプ
JP7189749B2 (ja) * 2018-12-04 2022-12-14 株式会社日立産機システム スクリュー圧縮機

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2457314A (en) * 1943-08-12 1948-12-28 Jarvis C Marble Rotary screw wheel device
US2481527A (en) * 1944-06-29 1949-09-13 Jarvis C Marble Rotary multiple helical rotor machine
JPS5951190A (ja) * 1982-09-17 1984-03-24 Hitachi Ltd オイルフリ−スクリユ−圧縮機の油切り装置
US5269667A (en) * 1993-02-24 1993-12-14 Ingersoll-Rand Company Removabe discharge port plate for a compressor
JPH06288369A (ja) 1993-04-06 1994-10-11 Hitachi Ltd スクリュー圧縮機の吸入ポート
JPH109164A (ja) 1996-06-19 1998-01-13 Hitachi Ltd スクリュー流体機械
DE19724643A1 (de) * 1997-06-11 1998-12-17 Sihi Gmbh & Co Kg Schraubenverdichter und Verfahren zum Betrieb desselben
JP2000337283A (ja) * 1999-05-28 2000-12-05 Tochigi Fuji Ind Co Ltd スクリューコンプレッサ
US8096288B2 (en) * 2008-10-07 2012-01-17 Eaton Corporation High efficiency supercharger outlet

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

Also Published As

Publication number Publication date
CN102261332A (zh) 2011-11-30
CN102261332B (zh) 2015-01-14
EP2390508A2 (de) 2011-11-30
EP2390508A3 (de) 2014-09-24
CN103541899A (zh) 2014-01-29
JP5478362B2 (ja) 2014-04-23
JP2011247115A (ja) 2011-12-08
CN103541899B (zh) 2016-11-23

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