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EP0460578A1 - Machine à vis pour liquide - Google Patents

Machine à vis pour liquide Download PDF

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Publication number
EP0460578A1
EP0460578A1 EP91109051A EP91109051A EP0460578A1 EP 0460578 A1 EP0460578 A1 EP 0460578A1 EP 91109051 A EP91109051 A EP 91109051A EP 91109051 A EP91109051 A EP 91109051A EP 0460578 A1 EP0460578 A1 EP 0460578A1
Authority
EP
European Patent Office
Prior art keywords
lubricating oil
oil
gas
cooling means
oil reservoir
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.)
Withdrawn
Application number
EP91109051A
Other languages
German (de)
English (en)
Inventor
Seiji Tsuru
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 Ltd
Original Assignee
Hitachi 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
Application filed by Hitachi Ltd filed Critical Hitachi Ltd
Publication of EP0460578A1 publication Critical patent/EP0460578A1/fr
Withdrawn legal-status Critical Current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
    • F04C29/02—Lubrication; Lubricant separation
    • 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
    • F01C21/06—Heating; Cooling; Heat insulation
    • 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
    • F04C2220/00—Application
    • F04C2220/40—Pumps with means for venting areas other than the working chamber, e.g. bearings, gear chambers, shaft seals

Definitions

  • the present invention relates to a screw fluid machine, and more particularly to a screw fluid machine and a multi-stage screw fluid machine suitable to reduce an amount of oil fumes produced from oil in a bearing chamber for oil-cooling a delivery side bearing of the screw fluid machine and oil in an oil reservoir.
  • a conventional screw machine is arranged such that lubricating oil pumped up by an oil pump from an oil reservoir passes through an oil cooler and an oil filter to lubricate and cool bearings of a screw rotor, a timing gear, a speed-up gear, etc., following which the oil is directly returned to the oil reservoir.
  • the lubricating oil deprives not only the friction heat produced by the bearings, the gears, etc., but also the heat produced from the rotor and casing of high temperature, and thus becomes high in temperature when returned to the oil reservoir. Further, a part of high-temperature air compressed within the rotor flows into the oil reservoir.
  • an enclosed bearing chamber which surrounds the bearings and the gears is filled with high-temperature gas, containing oil vapor, that is subjected to the heat radiated from the rotor and casing of high temperature and flows into the chamber from a contactless shaft sealing portion after passing through a high-temperature section. The gas then flows into the oil reservoir with the lubricating oil.
  • the prior art has suffered from a problem that the oil reservoir is also filled with gas of high temperature, containing oil vapor, resulted from the high-temperature lubricating oil and the above high-temperature gas, and that a large amount of oil fumes is produced in the oil reservoir and spread through a vent of the bearing chamber.
  • An object of the present invention is to provide a screw fluid machine and a multi-stage screw fluid machine which can reduce an amount of oil fumes produced in a bearing chamber and an oil reservoir.
  • lubricating oil cooling means adapted to cool lubricating oil is provided in a lubricating oil return passage connecting a bearing chamber, in which bearings and the like are housed, and an oil reservoir.
  • a gas release passage for releasing the gas from the bearing chamber to the atmosphere through the oil reservoir or an oil separator, and released gas cooling means located in the gas release passage between the bearing chamber and the oil reservoir or oil separator for cooling the released gas.
  • the lubricating oil cooling means and the released gas cooling means may be constructed integrally with each other.
  • an end of the lubricating oil return passage on the side open to the oil reservoir may be positioned below the level of the lubricating oil in the oil reservoir.
  • an end of the gas release passage on the side open to the oil reservoir may be positioned above the level of the lubricating oil in the oil reservoir.
  • second lubricating oil cooling means may be provided in an oil reservoir portion of the bearing chamber.
  • the second lubricating oil cooling means and the bearing chamber may be constructed integrally with each other.
  • the lubricating oil cooling means and the released gas cooling means of each stage may be constructed integrally with each other to simplify a construction of the lubricating oil cooling means and the released gas cooling means.
  • the oil temperature in the oil reservoir can be lowered to thereby reduce an amount of oil vapor produced.
  • the gas release passage for releasing the high-temperature gas from the bearing chamber to the atmosphere and the released gas cooling means located in the gas release passage between the bearing chamber and the oil reservoir, the atmospheric temperature in the oil reservoir can be lowered and the volumetric flow rate of gas can be decreased, thereby reducing an amount of the gas released to the atmosphere from the oil reservoir.
  • the lubricating oil can be returned to the oil reservoir with an increased distance from the level of the lubricating oil, and the scatter of oil mist can be prevented when the lubricating oil is injected into the oil reservoir. It is thus possible to prevent increase of oil content in the gas residing within the oil reservoir, make the temperature of the lubricating oil in the oil reservoir more uniform while suppressing a temperature rise of the oil in the vicinity of the oil level, and keep a partial pressure of the oil vapor low.
  • a screw rotor 1 comprising one set of a male rotor and a female rotor rotatably held in mesh with each other.
  • the male rotor is driven by a motor 9 to rotate via a speed-up gear 8.
  • the female rotor is rotated synchronously with the male rotor via a timing gear 4, whereby air sucked through an intake port 6 is compressed and delivered through a delivery port 7.
  • shaft sealing units 5a, 5b for preventing leakage of the compressed air in the compression chamber 2a
  • a delivery side bearing 3a and an intake side bearing 3b for respectively supporting the female and male rotors in a rotatable manner.
  • a gear case 10 having an upper portion in which the speed-up gear 8 is housed and a bottom portion which defines an oil reservoir 10a therein.
  • a bearing chamber 11 supported to the end face of the casing 2 on the delivery side is a bearing chamber 11 in which the delivery side bearing 3a and the timing gear 4 are both housed.
  • Lubricating oil is circulated through a route indicated by one-dot-chain lines in Fig. 1.
  • the lubricating oil delivered by an oil pump 18 from the oil reservoir 10a under pressure is cooled by a main oil cooler 19 and filtered by an oil filter 20, following which it is supplied to the delivery side bearing 3a, the intake side bearing 3b, the speed-up gear 8 in the gear case 10 and the timing gear 4 in the bearing chamber 11. Then, after lubricating the intake side bearing 3b and the speed-up gear 8, the lubricating oil directly naturally falls downward to return into the oil reservoir 10a located thereunder.
  • the lubricating oil after having lubricated the intake side bearing 3b is kept at a low temperature. Therefore, the direct return of the lubricating oil into the oil reservoir 10a results in a small temperature rise of the lubricating oil in the oil reservoir 10a. Further, because the sucked air through the intake port 6 is at a low pressure and low temperature, an amount of air leaking from the intake side shaft sealing unit 5b into the oil reservoir 10a through the intake side bearing 3b is small.
  • a temperature rise of the lubricating oil caused by rotation of the speed-up gear 8 is also very small. Accordingly, even if the lubricating oil after having lubricated the intake side bearing 3b and the speed-up gear 8 is directly returned to the oil reservoir 10a, a temperature rise of the lubricating oil can be held so small that no problem will occur in practical use.
  • the vicinity of the delivery side bearing 3a of the casing 1 is heated by high-temperature air compressed by the male and female rotors up to a high temperature, and the lubricating oil deprives the heat from the resultant high-temperature casing 1 to become itself high in temperature.
  • the high-temperature air compressed in the compression chamber 2a leaks into the bearing chamber 11 from the delivery side shaft sealing unit 5a through the delivery side bearing 3a, whereby the interior of the bearing chamber 11 is filled with the high-temperature air containing oil vapor.
  • the high-temperature lubricating oil is discharged through a discharge port 13 defined in a bottom wall of the bearing chamber 11 and cooled by an oil cooler 14a, before returning to the oil reservoir 10a through an oil return port 15.
  • the high-temperature air, containing oil vapor, in the bearing chamber 11 is discharged through a discharge port 12 defined in an upper wall of the bearing chamber 11.
  • the discharged air is cooled by an oil fume cooler 14b so that the volumetric flow rate thereof is reduced and a part of the oil vapor is condensed, followed by flowing into the gear case 10 through a vent port 16 defined in a side wall of the gear case 10 at a position above the level of the lubricating oil in the oil reservoir 10a.
  • the temperature in the gear case 10 and the oil reservoir 10a is kept low and a pressure rise is also held small, with the result that an amount of fumes discharged through a discharge port 17 defined in a top wall of the gear case 10 is reduced and so is the oil content. Accordingly, the fumes discharged through the discharge port 17 can be treated by a simple device.
  • the oil cooler 14a and the oil fume cooler 14b integrally with each other as shown in Fig. 1A, for example, they can be manufactured inexpensively.
  • the oil fumes after entering through the oil fume inlet 40, the oil fumes is cooled by the oil fume cooler 14b and discharged through an oil fume outlet 29. Meanwhile, after entering through an oil inlet 30, the oil is cooled by the oil fume cooler 14a and discharged through an oil outlet 31. Further, water is introduced through a water inlet 32 and discharged through a water outlet 33.
  • the oil cooler 14a and the oil fume cooler 14b are constructed within the same tube nest, and both the fluids are partitioned from each other by a partition plate 34. Oil drops produced upon cooling of the oil fumes are separated by a demister 35 and discharged through a drain discharge port 36.
  • the head of the lubricating oil i.e., the distance between the oil return port 15 and the level of the lubrication oil
  • the head of the lubricating oil can be increased so as to prevent the scatter of oil mist when the lubricating oil is injected into the oil reservoir 10a through the oil return port 15.
  • denoted by 28 in Fig. 2 is a nozzle through which the lubricating oil is injected to the timing gear 4.
  • a second oil cooler 22 is provided in an oil reservoir portion 11a defined at the bottom of the bearing chamber 11. Cooling water cooled by a cooler 27 is supplied to the second oil cooler 22 by a pump 26 under pressure and then heated while cooling the high-temperature lubricating oil in the oil reservoir portion 22. The heated water is cooled again by the cooler 27, followed by repeating the above process.
  • this embodiment can simplify the construction of the oil cooler 14a shown in Fig. 1 and also reduce an amount of the oil fumes produced in the bearing chamber 11.
  • a cooling water jacket 23 is provided in surrounding relation to the bearing chamber 11 and a number of fins 24 are provided on the inner upper and side surfaces of the bearing chamber 11.
  • Water cooled by a cooler 27A is supplied to the cooling water jacket 23 by a pump 26A under pressure and then heated while cooling the high-temperature lubricating oil and the high-temperature oil fumes in the bearing chamber 11. The heated water is cooled again by the cooler 27A, followed by repeating the above process.
  • this embodiment can simplify the construction of the oil cooler 14a and the oil fume cooler 14b shown in Fig. 1.
  • the oil fumes of high temperature produced in the bearing chamber 11 filled with oil vapor is discharged through the discharge port 12 and cooled by the oil fume cooler 14b, following which a component of lubricating oil in the oil fumes is removed by an oil separator 25 and the remaining gas is released to the atmosphere.
  • this embodiment can further reduce an amount of the oil fumes released to the atmosphere through the discharge port 17 in the top wall of the gear case 10.
  • the present invention is not limited thereto. As shown in Fig. 6, by way of example, the present invention is also applicable to each stage of a multi-stage screw compressor.
  • FIG. 6 shows one example of the multi-stage screw machine which comprises a first-stage compressor 41 and a second-stage compressor 42.
  • the oil cooler 14a and the oil fume cooler 14b are constructed integrally with each other and shared by both the compressors as shown. This results in an advantage of saving the space and reducing the production cost.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
EP91109051A 1990-06-08 1991-06-03 Machine à vis pour liquide Withdrawn EP0460578A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2148703A JPH0443891A (ja) 1990-06-08 1990-06-08 スクリュー流体機械および多段スクリュー流体機械
JP148703/90 1990-06-08

Publications (1)

Publication Number Publication Date
EP0460578A1 true EP0460578A1 (fr) 1991-12-11

Family

ID=15458710

Family Applications (1)

Application Number Title Priority Date Filing Date
EP91109051A Withdrawn EP0460578A1 (fr) 1990-06-08 1991-06-03 Machine à vis pour liquide

Country Status (3)

Country Link
EP (1) EP0460578A1 (fr)
JP (1) JPH0443891A (fr)
KR (1) KR920001120A (fr)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5401149A (en) * 1992-09-11 1995-03-28 Hitachi, Ltd. Package-type screw compressor having coated rotors
CN1062056C (zh) * 1994-02-19 2001-02-14 株式会社日立制作所 箱型成套螺杆压缩机
US6551082B2 (en) * 2000-11-22 2003-04-22 Hitachi, Ltd. Oil free type screw compressor
BE1014461A3 (nl) * 2001-11-08 2003-10-07 Atlas Copco Airpower Nv Oliegeinjecteerde schroefcompressor.
US20120156079A1 (en) * 2010-12-15 2012-06-21 Kabushiki Kaisha Kobe Seiko Sho (Kobe Steel, Ltd.) Screw compressor
EP3392478A1 (fr) * 2017-04-21 2018-10-24 ATLAS COPCO AIRPOWER, naamloze vennootschap Circuit d'huile, compresseur sans huile muni d'un tel circuit d'huile et procédé de réglage de la lubrification et/ou le refroidissement d'un tel compresseur sans huile par l'intermédiaire d'un tel circuit d'huile

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2004346864A (ja) * 2003-05-23 2004-12-09 Taiko Kikai Industries Co Ltd 廃熱回収用膨張機関
JP4701200B2 (ja) * 2007-03-26 2011-06-15 株式会社日立産機システム 無給油式スクリュー圧縮機とその運転方法
JP4717048B2 (ja) * 2007-10-26 2011-07-06 株式会社神戸製鋼所 スクリュ圧縮機
JP5478153B2 (ja) * 2009-08-27 2014-04-23 株式会社日立産機システム スクリュー圧縮機
JP5798331B2 (ja) * 2011-02-08 2015-10-21 株式会社神戸製鋼所 水噴射式スクリュ圧縮機
JP5155421B2 (ja) * 2011-03-28 2013-03-06 株式会社神戸製鋼所 スクリュ圧縮機
JP2014046897A (ja) * 2012-09-04 2014-03-17 Panasonic Corp 車両用ヒートポンプ装置
JP6778581B2 (ja) * 2016-10-25 2020-11-04 株式会社神戸製鋼所 オイルフリースクリュ圧縮機
CN115917155A (zh) * 2020-09-02 2023-04-04 伊顿智能动力有限公司 后驱动egr泵

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB393977A (en) * 1931-12-16 1933-06-16 Thomas Winter Nichols Improvements in rotary air pumps or compressors
GB785860A (en) * 1955-01-17 1957-11-06 Manfred Dunkel Improvements in or relating to rotary piston blowers
EP0156951A2 (fr) * 1983-12-13 1985-10-09 Leybold Aktiengesellschaft Pompe à vide avec deux arbres et avec obtention du vide de l'espace d'engrenage

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB393977A (en) * 1931-12-16 1933-06-16 Thomas Winter Nichols Improvements in rotary air pumps or compressors
GB785860A (en) * 1955-01-17 1957-11-06 Manfred Dunkel Improvements in or relating to rotary piston blowers
EP0156951A2 (fr) * 1983-12-13 1985-10-09 Leybold Aktiengesellschaft Pompe à vide avec deux arbres et avec obtention du vide de l'espace d'engrenage

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5401149A (en) * 1992-09-11 1995-03-28 Hitachi, Ltd. Package-type screw compressor having coated rotors
US5613843A (en) * 1992-09-11 1997-03-25 Hitachi, Ltd. Package-type screw compressor
CN1062056C (zh) * 1994-02-19 2001-02-14 株式会社日立制作所 箱型成套螺杆压缩机
US6551082B2 (en) * 2000-11-22 2003-04-22 Hitachi, Ltd. Oil free type screw compressor
BE1014461A3 (nl) * 2001-11-08 2003-10-07 Atlas Copco Airpower Nv Oliegeinjecteerde schroefcompressor.
US20120156079A1 (en) * 2010-12-15 2012-06-21 Kabushiki Kaisha Kobe Seiko Sho (Kobe Steel, Ltd.) Screw compressor
US9022748B2 (en) * 2010-12-15 2015-05-05 Kobe Steel, Ltd. Screw compressor
EP3392478A1 (fr) * 2017-04-21 2018-10-24 ATLAS COPCO AIRPOWER, naamloze vennootschap Circuit d'huile, compresseur sans huile muni d'un tel circuit d'huile et procédé de réglage de la lubrification et/ou le refroidissement d'un tel compresseur sans huile par l'intermédiaire d'un tel circuit d'huile
WO2018193325A1 (fr) * 2017-04-21 2018-10-25 Atlas Copco Airpower, Naamloze Vennootschap Circuit d'huile, compresseur sans huile doté d'un tel circuit d'huile et procédé de commande de lubrification et/ou de refroidissement d'un tel compresseur sans huile par l'intermédiaire d'un tel circuit d'huile

Also Published As

Publication number Publication date
KR920001120A (ko) 1992-01-30
JPH0443891A (ja) 1992-02-13

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