EP2452074B1 - Dry screw driver - Google Patents

Dry screw driver Download PDF

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Publication number
EP2452074B1
EP2452074B1 EP10747261.5A EP10747261A EP2452074B1 EP 2452074 B1 EP2452074 B1 EP 2452074B1 EP 10747261 A EP10747261 A EP 10747261A EP 2452074 B1 EP2452074 B1 EP 2452074B1
Authority
EP
European Patent Office
Prior art keywords
compressor
rotor
male rotor
shaft
rotors
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.)
Revoked
Application number
EP10747261.5A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP2452074A2 (en
Inventor
Paolo Cavatorta
Umberto Tomei
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.)
Gardner Denver SRL
Original Assignee
Gardner Denver SRL
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
Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=41723031&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP2452074(B1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by Gardner Denver SRL filed Critical Gardner Denver SRL
Priority to PL10747261T priority Critical patent/PL2452074T3/pl
Publication of EP2452074A2 publication Critical patent/EP2452074A2/en
Application granted granted Critical
Publication of EP2452074B1 publication Critical patent/EP2452074B1/en
Revoked legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F04C18/084—Toothed wheels
    • 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
    • F04C2240/00—Components
    • F04C2240/50—Bearings
    • F04C2240/52—Bearings for assemblies with supports on both sides

Definitions

  • the present invention relates to a dry screw compressor for a gas, in particular air, for use in pressure applications (e.g. in the conveyance of granulates or powders, or in water treatment, where large amounts of air must be conveyed to start and help aerobic reactions) and in vacuum applications (e.g. in gas, fume or steam exhaust systems).
  • the present dry screw compressor is used in applications with low differential pressures comprised between 1 bar and 3 bars and under vacuum to a threshold absolute pressure of 150 mbars.
  • lobe compressors As already known, low differential pressure applications (lower than 1 bar) use lobe compressors. These are compressors wherein two lobe rotors (usually two or three lobes) with parallel axes mesh together and synchronically rotate in opposite directions.
  • a normal screw compressor under high pressures comprises at least a male rotor and at least a female rotor meshing together during the rotation around respective axes and housed within a casing body.
  • Each of the two rotors has screw-shaped ribs that mesh with corresponding screw-shaped grooves of the other rotor.
  • Both the male and female rotor show, in cross section, a predetermined number of teeth corresponding to their ribs and a predetermined number of valleys corresponding to their grooves.
  • the casing body has an inlet for the gas to be taken in and an outlet (also called “delivery outlet”) for the compressed gas. The intake gas is compressed between the two moving rotors and arrives to the outlet under the requested pressure.
  • dry screw compressors generally indicated as “oil-free”
  • oil injection compressors are largely used in applications wherein the level of contaminants must be kept below a determined percentage threshold (usually very low).
  • the manufacture of such dry screw compressors is quite sophisticated and expensive, since it must take into account the remarkable mechanical and thermal stresses to which the rotors are' subjected.
  • the ratio between the length and the external diameter of the male rotor is usually comprised between 1.5 and 1.8; this requirement strongly limits the compressor capacity and requires the insertion in the compressor structure of a gear multiplier in order to start the rotors at very high peripheral speeds, usually > 150 m/s.
  • the aforesaid compressors can be also used under differential pressures comprised between 1 bar and 3 bars.
  • the drawback of these low pressure compressors is represented by their having the same structural complexity of high-pressure compressors.
  • the technical task object of the present invention is proposing a dry screw compressor which can work under low pressure, with a high flow and a thermodynamic efficiency typical of this kind of machines.
  • the main aim of the present invention is providing for a dry screw compressor under low differential pressures (comprised between 1 and 3 bars) and with a high flow, which is structurally simple, economical and easy to maintain.
  • a further aim of the present invention is proposing a dry screw compressor which is also suitable for under vacuum applications, up to a threshold of 150 mbar of absolute pressure.
  • 1 indicates a dry screw compressor for gas, in particular air, according to the invention.
  • the compressor 1 can be used both under pressure and under vacuum.
  • the compressor 1 comprises at least a male rotor 2 and at least a female rotor 3, meshed together ( figures 1 , 2 , 3 ).
  • the embodiment here described and illustrated provides for a single male rotor 2 and a single female rotor 3 housed' within a single casing body 4.
  • this casing body 4 is obtained by coupling two communicating cylinders (not shown) so that they define a single cavity 5 housing the rotors 2, 3.
  • An alternative embodiment (not shown) provides for a plurality of conjugated pairs of male rotors 2 and female rotors 3.
  • the female rotor 3 is keyed on a shaft 17 (having an axis of rotation (01)), whereas the male rotor 2 is keyed on a shaft 18 (having an axis of rotation (02)).
  • the first axis of rotation (01) is arranged at a certain distance (I) (generally known as "centre distance") from the second axis of rotation (02).
  • the first axis of rotation (01) and the second axis of rotation (02) are parallel to each other.
  • Each of said rotors 2, 3 has screw-shaped ribs meshing with screw-shaped grooves formed between corresponding screw-shaped ribs of the other rotor 2, 3.
  • the male rotor 2 shows lobes 6 (or teeth) and valleys 7 meshing with corresponding valleys 8 and lobes 9 (or teeth) of the female rotor 3.
  • figure 3 shows some main dimensional parameters characterizing the profiles of the rotors 2, 3.
  • the length (Lm) of the male rotor 2 corresponds to the length (Lf) of the female rotor 3.
  • the "winding angle" ( ⁇ ) is formed by the angle of a generic helix 40 (described by the head of a generic tooth) comprised between a segment OA, connecting the axis (02) of the male rotor 2 to the helix 40 on a first end plane (n1) of the rotor 2, and a segment O'B', also connecting the axis (02) to the helix 40 on a second end plane (n2) of the rotor 2 opposed to the first end plane (n1).
  • the rotor 2 comprises three helixes 30, 40, 50, parallel to each other, described by the heads of the relative teeth.
  • the term "length (Lm)" of the male rotor 2 defines the distance between the two end planes (n1), (n2), the term “pitch (Pz)" between two helixes 30, 40 defines the distance between point B and point B1, and the term “angle of the helix” ( ⁇ ) defines the angle comprised between the tangent (r) to the helix 40 in any point (P) and the axis (02) of the male rotor 2.
  • the ratio between the length (Lm) and the external diameter (Dm) of the male rotor 2 must be higher than or equal to 2, to maximise the compressor capacity and, therefore, together with the conjugated profiles of the lobes of the rotors, to guarantee high gas flows.
  • said (Lm)/(Dm) ratio is comprised between 2 and 3.
  • external diameter (Dm) means the diameter of the external circumference (Cem) of the male rotor 2 ( figure 3 ).
  • the maximum value of the winding angle ( ⁇ ) must be 300°; in fact, by increasing the value of the winding angle ( ⁇ ), and with an equal length (Lm), an equal diameter (Dm) and an equal profile of the tooth of the male rotor 2, the overlap between the teeth of the two rotors 2, 3 consequently increases, with a following reduction of the total capacity of the compressor 1.
  • the number of lobes 6 of the male rotor 2 is different from the number of lobes 9 of the female rotor 3.
  • the number of lobes 6 of the male rotor 2 is lower than the number of lobes 9 of the female rotor 3 by at least one unity.
  • the number of lobes 6 of the male rotor 2 corresponds to three, whereas the number of lobes 9 of the female rotor 3 corresponds to five.
  • the number of lobes 6 of the male rotor 2 corresponds to four, whereas the number of lobes 9 of the female rotor 3 corresponds to six.
  • the two rotors 2, 3 are kept in the reciprocal position by means of the synchronization gear formed by two toothed wheels 20a and 20b of the known kind ( figure 1 ).
  • the transmission ratio between the synchronization gears 20a, 20b must be equal to the ratio existing between the number of teeth of the two rotors 2, 3.
  • the driving shaft is the shaft 17 on which the female rotor 3 is keyed because it is the one with more teeth, so that each rotation of this shaft 17 corresponds to the filling of a larger number of gaps and, in short, to a larger volume conveyed by the compressor 1.
  • the casing body 4 has an inlet 10 for a gaseous fluid to be taken in, flowing according to an arrow (F1), and at least an outlet 11 (or delivery outlet) for the compressed fluid flowing according to an arrow (F2).
  • Said outlet 11 defines an opening 12 formed in the casing body 4.
  • the compressor 1 uses bearings of a known kind.
  • the radial loads are sustained by a first group 19a of radial ball bearings arranged close to the inlet 10 and by a second group 19b of cylindrical ball bearings arranged close to the outlet 11.
  • the axial loads are sustained by a third group-19c of oblique contact ball bearings arranged beside the bearings of the second group 19b.
  • the compressor 1 is provided with an electric motor 16 whose rotor is advantageously keyed on the shaft 17 of the female rotor 3 for starting its rotation around the first axis of rotation (01).
  • the motor 16 is of a permanent magnet motor.
  • the permanent magnet motor 16 is of the kind cooled by water circulation. As an alternative, it can be used a permanent magnet motor of the air-cooled kind.
  • the motor 16 is preferably keyed on the shaft 17 of the female rotor 3, namely it is aligned with said shaft 17.
  • the compressor 1 can be coupled to an electric motor (not shown) by means of a "belt and pulley" drive (not shown).
  • the gas e.g. air
  • the gas is taken in by the compressor 1 and, through the inlet 10, enters into the casing body 4 ( figures 1 , 2 ).
  • the screw-shaped ribs of the female rotor 3 mesh together with the screw-shaped grooves of the male rotor 2, and vice versa.
  • the correct transmission/multiplication ratio between the rotors 2, 3 is actuated by means of the synchronization gears 20a, 20b.
  • Both embodiments can be provided with shaping means (not shown) defining the actual dimension of opening 12 corresponding to the desired compression ratio (R).
  • the ratio between the length and the external diameter of the male rotor (higher than or equal to two) is made possible by low differential pressures (comprised between 1 bar and 3 bars) or by the threshold absolute pressure of 150 mbars for under vacuum applications.
  • the choice of the profile geometry and the operation of the compressor by means of the shaft of the female rotor allow to maximize the compressor capacity, with rotors of the same length, thus allowing to reach the requested high flow at a peripheral speed of the male rotor 2 lower than 80 m/s.
  • the geometry of the profiles of the two coupled' rotors allows to get a shorter contact line between the rotors with a better seal, thus reducing the blow by.
  • the compressor works at peripheral speeds of the male rotor lower than 80 m/s, the peripheral speed of the female rotor is even lower, and therefore the rotor of the electric motor can be directly keyed on the shaft of the female rotor (namely with no interposition of multiplying gears), thus obtaining a compressor which is structurally simple, compact and having a higher energetic efficiency.
  • the energetic efficiency of the compressor is also provided by the use of a permanent magnet motor, characterized by low consumptions over a large range of speeds.
  • this kind of permanent magnet motor has higher efficiencies than the three-phase asynchronous electric motor used in the known art, specially at reduced speeds.
  • the use of a water-cooled permanent magnet motor allows a reduction in size and weight of the motor, thus allowing its direct arrangement of the shaft of the female rotor, exploiting the radial bearings of the compressor.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Compressor (AREA)
  • Drying Of Solid Materials (AREA)
  • Separation By Low-Temperature Treatments (AREA)
EP10747261.5A 2009-07-10 2010-07-09 Dry screw driver Revoked EP2452074B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PL10747261T PL2452074T3 (pl) 2009-07-10 2010-07-09 Działający na sucho napęd śrubowy

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
IT000054A ITPR20090054A1 (it) 2009-07-10 2009-07-10 Compressore a vite a secco
PCT/IB2010/001706 WO2011004257A2 (en) 2009-07-10 2010-07-09 Dry screw driver

Publications (2)

Publication Number Publication Date
EP2452074A2 EP2452074A2 (en) 2012-05-16
EP2452074B1 true EP2452074B1 (en) 2013-07-03

Family

ID=41723031

Family Applications (1)

Application Number Title Priority Date Filing Date
EP10747261.5A Revoked EP2452074B1 (en) 2009-07-10 2010-07-09 Dry screw driver

Country Status (14)

Country Link
US (1) US20120201708A1 (zh)
EP (1) EP2452074B1 (zh)
JP (1) JP5647239B2 (zh)
KR (1) KR101799411B1 (zh)
CN (1) CN102575673B (zh)
AU (2) AU2010269955A1 (zh)
BR (1) BR112012000602A2 (zh)
DK (1) DK2452074T3 (zh)
ES (1) ES2429526T3 (zh)
HK (1) HK1170286A1 (zh)
IT (1) ITPR20090054A1 (zh)
PL (1) PL2452074T3 (zh)
RU (1) RU2547211C2 (zh)
WO (1) WO2011004257A2 (zh)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE202013001817U1 (de) * 2013-02-26 2014-06-04 Vemag Maschinenbau Gmbh Anordnung von dichtschließenden Förderschnecken
WO2016164989A1 (en) * 2015-04-17 2016-10-20 Atlas Copco Airpower, Naamloze Vennootschap Screw compressor, compressor element and gearbox applied thereby
CN107923398A (zh) 2015-08-11 2018-04-17 开利公司 制冷压缩机配件
CN109931263A (zh) * 2019-03-08 2019-06-25 西安航天动力研究所 一种干式屏蔽真空泵

Family Cites Families (28)

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NO117317B (zh) * 1964-03-20 1969-07-28 Svenska Rotor Maskiner Ab
FR1528286A (fr) * 1966-06-22 1968-06-07 Atlas Copco Ab Perfectionnements aux machines à rotors hélicoïdaux
US3424373A (en) * 1966-10-28 1969-01-28 John W Gardner Variable lead compressor
US3807911A (en) * 1971-08-02 1974-04-30 Davey Compressor Co Multiple lead screw compressor
US3913346A (en) * 1974-05-30 1975-10-21 Dunham Bush Inc Liquid refrigerant injection system for hermetic electric motor driven helical screw compressor
JPS61152990A (ja) * 1984-12-26 1986-07-11 Hitachi Ltd スクリユ−真空ポンプ
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JPH08296578A (ja) * 1995-04-26 1996-11-12 Kobe Steel Ltd スクリュ圧縮機／冷凍機の吸気音低減機構
US5580232A (en) * 1995-05-04 1996-12-03 Kobelco Compressors (America), Inc. Rotor assembly having a slip joint in the shaft assembly
JP2001140784A (ja) * 1999-11-17 2001-05-22 Teijin Seiki Co Ltd 真空ポンプ
JP4282867B2 (ja) * 2000-03-15 2009-06-24 ナブテスコ株式会社 スクリューロータおよびスクリュー機械
JP4190721B2 (ja) * 2000-12-04 2008-12-03 株式会社日立製作所 無給油式スクリュー圧縮機
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CN102203553B (zh) 2008-10-31 2015-06-10 高通股份有限公司 对定位系统使用磁力计

Also Published As

Publication number Publication date
PL2452074T3 (pl) 2013-12-31
EP2452074A2 (en) 2012-05-16
JP5647239B2 (ja) 2014-12-24
RU2012104612A (ru) 2013-08-20
AU2016216518A1 (en) 2016-09-01
BR112012000602A2 (pt) 2020-08-11
JP2012533016A (ja) 2012-12-20
CN102575673A (zh) 2012-07-11
CN102575673B (zh) 2015-12-16
KR101799411B1 (ko) 2017-11-20
RU2547211C2 (ru) 2015-04-10
KR20120065999A (ko) 2012-06-21
HK1170286A1 (zh) 2013-02-22
AU2010269955A1 (en) 2012-03-01
ITPR20090054A1 (it) 2011-01-11
WO2011004257A3 (en) 2011-10-27
WO2011004257A2 (en) 2011-01-13
US20120201708A1 (en) 2012-08-09
DK2452074T3 (da) 2013-09-30
ES2429526T3 (es) 2013-11-15

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