US20070207045A1 - Compressor - Google Patents

Compressor Download PDF

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Publication number
US20070207045A1
US20070207045A1 US10/575,542 US57554204A US2007207045A1 US 20070207045 A1 US20070207045 A1 US 20070207045A1 US 57554204 A US57554204 A US 57554204A US 2007207045 A1 US2007207045 A1 US 2007207045A1
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US
United States
Prior art keywords
compressor
pressure
motor
speed
tank
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.)
Abandoned
Application number
US10/575,542
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English (en)
Inventor
Mats Sundstrom
Henrik Ohman
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.)
Svenska Rotor Maskiner AB
Original Assignee
Individual
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 Individual filed Critical Individual
Assigned to SVENSKA ROTOR MASKINER AB reassignment SVENSKA ROTOR MASKINER AB ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: OHMAN, HENRIK, SUNDSTROM, MATS
Publication of US20070207045A1 publication Critical patent/US20070207045A1/en
Abandoned 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
    • 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
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/08—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by varying the rotational speed

Definitions

  • the present invention relates to a speed-regulated helical screw rotor compressor that is adapted to work against a pressure container whose pressure P lies within the working range of the compressor and which is allowed to vary between a lowest pressure and a highest pressure.
  • the compressor is driven by an electric motor.
  • Compressor speed control is generally used in respect of air compressors that are driven by a high power motor down to a power of 10-30 kW.
  • the compressor speed is controlled with the aid of electronic control means.
  • the aforesaid lower limit of about 10-30 kW in respect of the power of a speed control compressor can, however, be lower with increased energy costs.
  • a smart way of controlling the pressure in the pressure container is to use in the container a pressure sensor which, via appropriate control means, functions to switch-off the compressor motor when the pressure in the container has reached its maximum value and to switch-on the motor when the container pressure has reached a pre-determined lowest value.
  • the aim of speed control is to enable the buffer tank against which the compressor works to be made much smaller than would otherwise be the case.
  • a compressor whose speed is not controlled will thus require a larger buffer tank and larger tank accommodating space, therewith incurring higher investment costs.
  • the aim of the present invention is to provide a motor-driven compressor whose motor has a much smaller power than the aforesaid lowest power and the speed of which can be controlled at least within one working range in the absence of expensive control equipment.
  • FIG. 1 is a longitudinally sectional view of a known helical screw compressor
  • FIG. 2 is a sectional view taken on the line II-II in FIG. 1 ;
  • FIG. 3 is a diagrammatic illustration of a system which includes the compressor
  • FIG. 4 illustrates diagrammatically the torque of a typical compressor motor as a function of its speed (r.p.m.).
  • FIG. 5 is a corresponding diagrammatic illustration of a compressor motor according to the present invention.
  • FIGS. 1 and 2 A brief description of the construction and working principle of a helical screw compressor will now be given with reference to FIGS. 1 and 2 .
  • a pair of mutually engaging screw rotors 101 , 102 are mounted for rotation in a working space delimited by two end walls 103 , 104 and including a barrel wall 105 that extends between said end walls.
  • the barrel wall 105 has a form which corresponds generally to that of two mutually intersecting cylinders, as evident from FIG. 2 .
  • Each rotor 101 , 102 includes a plurality of lobes 106 and 107 respectively, and respective intermediate grooves 111 and 112 that extend in a helical line along the rotor.
  • One rotor 101 is a male type of rotor with the major part of each lobe 106 located outside the pitch circle and the other rotor 102 is a female type rotor with the major part of each lobe 107 located inwardly of the pitch circle.
  • the female rotor 102 will usually have more lobes than the male rotor 101 .
  • a typical combination is one in which the male rotor 101 has four lobes and the female rotor 102 has six lobes.
  • the gas to be compressed normally air, is delivered to a working space of the compressor through an inlet port 108 and is then compressed in V-shaped working chambers formed between the rotors and the walls of the working space.
  • Each working chamber moves to the right in FIG. 1 as the rotors 101 , 102 rotate.
  • the volume of a working chamber will thus decrease continuously during the latter part of its cycle, subsequent to communication with the inlet port having been cut off.
  • the gas is thereby compressed and exits in a compressed state from the compressor through an outlet port 109 .
  • the ratio between outlet pressure and inlet pressure is determined by the inherent volumetric relationship between the volume of a working chamber immediately after its communication with the inlet port 108 has been cut off, and the volume of said chamber when it begins to communicate with the outlet port 109 .
  • FIG. 3 illustrates a compressor K, preferably a helical screw compressor, which is driven by a motor M via a shaft or axle 1 .
  • the compressor includes an inlet port 6 into which an inlet line 2 opens.
  • the line 2 includes a check valve 3 which allows air to enter the compressor, while preventing the flow of air in the opposite direction.
  • the compressor has at its other end an outlet port 7 which is connected to a pressure tank T via a line 4 .
  • One or more tools V driven by compressed air, are supplied with pressure from the tank T via a line 5 .
  • the tank is provided with a pressure sensor 9 which is connected via a signal transmitting line 10 to a control means 8 that functions to control starting and stopping of the motor.
  • the pressure in the tank T shall vary between a highest pressure P1 and a lowest pressure P 2 .
  • the motor M drives the compressor K until the pressure in the tank has reached said highest pressure P 1 , whereupon the motor M is switched off.
  • the motor M is restarted and again drives the compressor and therewith deliver compressed air to the tank T.
  • the check valve 3 prevents compressed air from flowing from the tank T back through the compressor K and the inlet line 2 .
  • FIG. 4 illustrates diagrammatically a torque curve as a function of the rotational speed of an asynchronous motor.
  • the axes are not graduated.
  • the motor has a speed of N 4 for a torque of M 2A .
  • M 1A the motor speed will drop to N 3 .
  • the relationship with respect to this asynchronous motor is at least substantially linear in one working range of said motor.
  • the motor will be started when the tank pressure has fallen to the pressure P 2 , wherewith the compressor begins to compress air. Because of the small increase in speed required to raise the motor torque from M 2A to M 1A , the compressor will work at almost maximum capacity in this torque range. This results in a rapid increase in tank pressure. A compressor driven by an asynchronous motor will thus result in a short compressor operating time in achieving the desired highest pressure in the tank T. Only a relatively small volume of air responsible in lowering the tank pressure will be consumed during this relatively short period of time. This will result in frequent starting of the motor, in order to keep the tank pressure within the desired pressure range. These moments of frequent starting and stopping of the motor will significantly shorten its useful life, for instance as a result of overheating of the motor windings.
  • FIG. 5 illustrates diagrammatically a torque curve as a function of motor speed.
  • the illustrated curve of FIG. 5 relates to a commutator motor.
  • the axes shown in FIG. 5 are not graduated.
  • the torques M 1k and M 2k in FIG. 5 correspond to the torques M 1A and M 2A in FIG. 4 .
  • the commutator motor has a speed of N2 in respect of torque M 2k .
  • the rpm of the motor will have fallen to N1. This relationship is at least substantially linear for the commutator in the working range.
  • the tank pressure will have fallen to P 2k when the motor is started (see FIG. 3 ) wherewith the compressor begins to compress air. Due to the significant increase in rpm. or motor speed, necessary for increasing the motor torque from M 2k to M 1k , it is necessary for the compressor to work over a significantly longer period of time to achieve maximum pressure than that required by an asynchronous motor. This means that it will take far longer to achieve a tank pressure P 1 when the compressor is driven by a commutator motor. During this longer compressor working time the volume of air consumed is much greater than when a compressor is driven by an asynchronous motor, with which the maximum tank pressure is reached much more quickly. Thus, the number of starts involved when using a commutator motor is far less than the number of starts involved when driving the same compressor with an asynchronous motor in order to maintain the tank T pressurised.
  • a compressor that has a relatively low internal volume factor.
  • internal volume factor is meant the relationship between the minimum and maximum thread volume enclosed in the helical rotor compressor used.
  • the internal volume factor will preferably be such that the pressure of the compressor K will be less than P 2 +0.85*(P 1 ⁇ P 2 ) when the thread volume of the working chamber that commences communication with the tank T has its minimum volume. This means that the compressor outlet pressure in given working chamber will be at most equal to the lowest pressure of the tank plus 85 percent of the difference between the highest and the lowest pressure of the tank.
  • the compressor will preferably be optimised for an internal volume factor at which the compressor pressure at the opening instance will be equal to the lowest working pressure P 2 in the pressure container. It is particularly preferred that the compressor is optimised in respect of an internal volume factor at which the compressor pressure at the opening instance is lower than the lowest working pressure P 2 in the pressure container.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Control Of Direct Current Motors (AREA)
  • Control Of Electric Motors In General (AREA)
US10/575,542 2003-10-17 2004-09-30 Compressor Abandoned US20070207045A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
SE0302739A SE524343C2 (sv) 2003-10-17 2003-10-17 Varvtalsreglerad skruvrotorkompressor
SE0302739-8 2003-10-17
PCT/SE2004/001390 WO2005038257A1 (en) 2003-10-17 2004-09-30 Compressor

Publications (1)

Publication Number Publication Date
US20070207045A1 true US20070207045A1 (en) 2007-09-06

Family

ID=29398751

Family Applications (1)

Application Number Title Priority Date Filing Date
US10/575,542 Abandoned US20070207045A1 (en) 2003-10-17 2004-09-30 Compressor

Country Status (7)

Country Link
US (1) US20070207045A1 (sv)
EP (1) EP1687539A1 (sv)
JP (1) JP2007508494A (sv)
KR (1) KR20060097018A (sv)
CN (1) CN100458164C (sv)
SE (1) SE524343C2 (sv)
WO (1) WO2005038257A1 (sv)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR20140135960A (ko) * 2012-02-28 2014-11-27 아틀라스 캅코 에어파워, 남로체 벤누트삽 스크류 압축기
US20150030491A1 (en) * 2012-02-28 2015-01-29 Atlas Copco Airpower, Naamloze Vennootschap Compressor device as well as the use of such a compressor device
US11015602B2 (en) 2012-02-28 2021-05-25 Atlas Copco Airpower, Naamloze Vennootschap Screw compressor

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3118458B1 (en) * 2015-07-15 2017-08-30 ABB Technology Oy Method and apparatus in connection with a screw compressor

Citations (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3855515A (en) * 1972-03-06 1974-12-17 Waters Associates Inc Motor control circuit
US3860363A (en) * 1973-05-10 1975-01-14 Chicago Pneumatic Tool Co Rotary compressor having improved control system
US4052135A (en) * 1976-05-11 1977-10-04 Gardner-Denver Company Control system for helical screw compressor
US4068980A (en) * 1976-10-01 1978-01-17 Gardner-Denver Company Compressor startup control
US4492526A (en) * 1981-12-18 1985-01-08 Institut Cerac S.A. Compressor drive system
US4686439A (en) * 1985-09-10 1987-08-11 A. T. Hunn Company Multiple speed pump electronic control system
US4756669A (en) * 1986-07-31 1988-07-12 Nippon Air Brake Co., Ltd. Air compressor control apparatus
US5580221A (en) * 1994-10-05 1996-12-03 Franklin Electric Co., Inc. Motor drive circuit for pressure control of a pumping system
US5949173A (en) * 1993-06-07 1999-09-07 General Electric Company Permanent magnet direct current motor
US6146101A (en) * 1998-05-22 2000-11-14 Chang; Ming-Yi Automatic control device for an air compressor
US6599093B2 (en) * 2000-08-10 2003-07-29 Kabushiki Kaisha Kobe Seiko Sho Compressor having speed and intake regulation valve control
US20040146414A1 (en) * 2001-06-11 2004-07-29 Philip Nichol Screw compressor with switched reluctance motor
US20040265134A1 (en) * 2003-06-24 2004-12-30 Hitachi Koki Co., Ltd. Air compressor and control method therefor
US7081698B1 (en) * 2003-07-31 2006-07-25 Black & Decker Inc. Efficient motor

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN1011728B (zh) * 1986-12-15 1991-02-20 瑞典转子机械公司 螺杆压缩机
CN2155519Y (zh) * 1993-06-30 1994-02-09 李敬茂 节能空调器
FI104205B (sv) * 1994-11-24 1999-11-30 Sarlin Hydor Oy Förfarande och anordning för styrning av ett kompressionssystem för ett flytande medium
DE9419651U1 (de) * 1994-12-08 1995-02-02 Hatlapa Uetersener Maschinenfabrik GmbH & Co, 25436 Uetersen Kompressoranlage
US5979168A (en) * 1997-07-15 1999-11-09 American Standard Inc. Single-source gas actuation for screw compressor slide valve assembly

Patent Citations (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3855515A (en) * 1972-03-06 1974-12-17 Waters Associates Inc Motor control circuit
US3860363A (en) * 1973-05-10 1975-01-14 Chicago Pneumatic Tool Co Rotary compressor having improved control system
US4052135A (en) * 1976-05-11 1977-10-04 Gardner-Denver Company Control system for helical screw compressor
US4068980A (en) * 1976-10-01 1978-01-17 Gardner-Denver Company Compressor startup control
US4492526A (en) * 1981-12-18 1985-01-08 Institut Cerac S.A. Compressor drive system
US4686439A (en) * 1985-09-10 1987-08-11 A. T. Hunn Company Multiple speed pump electronic control system
US4756669A (en) * 1986-07-31 1988-07-12 Nippon Air Brake Co., Ltd. Air compressor control apparatus
US5949173A (en) * 1993-06-07 1999-09-07 General Electric Company Permanent magnet direct current motor
US5580221A (en) * 1994-10-05 1996-12-03 Franklin Electric Co., Inc. Motor drive circuit for pressure control of a pumping system
US6146101A (en) * 1998-05-22 2000-11-14 Chang; Ming-Yi Automatic control device for an air compressor
US6599093B2 (en) * 2000-08-10 2003-07-29 Kabushiki Kaisha Kobe Seiko Sho Compressor having speed and intake regulation valve control
US20040146414A1 (en) * 2001-06-11 2004-07-29 Philip Nichol Screw compressor with switched reluctance motor
US20040265134A1 (en) * 2003-06-24 2004-12-30 Hitachi Koki Co., Ltd. Air compressor and control method therefor
US7081698B1 (en) * 2003-07-31 2006-07-25 Black & Decker Inc. Efficient motor

Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR20140135960A (ko) * 2012-02-28 2014-11-27 아틀라스 캅코 에어파워, 남로체 벤누트삽 스크류 압축기
US20150023826A1 (en) * 2012-02-28 2015-01-22 Andries Jan F. Desiron Screw compressor
US20150030491A1 (en) * 2012-02-28 2015-01-29 Atlas Copco Airpower, Naamloze Vennootschap Compressor device as well as the use of such a compressor device
AU2012371539B2 (en) * 2012-02-28 2017-08-03 Atlas Copco Airpower, Naamloze Vennootschap Screw compressor
KR20170109687A (ko) * 2012-02-28 2017-09-29 아틀라스 캅코 에어파워, 남로체 벤누트삽 스크류 압축기
US9850896B2 (en) * 2012-02-28 2017-12-26 Atlas Copco Airpower, Naamloze Vennootschap Screw compressor
US10151313B2 (en) * 2012-02-28 2018-12-11 Atlas Copco Airpower, Naamloze Vennootschap Compressor device as well as the use of such a compressor device
US10197058B2 (en) 2012-02-28 2019-02-05 Atlas Copco Airpower, Naamloze Vennootschap Screw compressor
AU2017206172B2 (en) * 2012-02-28 2019-03-07 Atlas Copco Airpower, Naamloze Vennootschap Screw compressor
US20190186490A1 (en) * 2012-02-28 2019-06-20 Atlas Copco Airpower, Naamloze Vennootschap Screw compressor
KR102006045B1 (ko) 2012-02-28 2019-07-31 아틀라스 캅코 에어파워, 남로체 벤누트삽 스크류 압축기
KR102013510B1 (ko) 2012-02-28 2019-10-21 아틀라스 캅코 에어파워, 남로체 벤누트삽 스크류 압축기
US10480511B2 (en) * 2012-02-28 2019-11-19 Atlas Copco Airpower, Naamloze Vennootschap Screw compressor
US11015602B2 (en) 2012-02-28 2021-05-25 Atlas Copco Airpower, Naamloze Vennootschap Screw compressor

Also Published As

Publication number Publication date
SE0302739L (sv) 2004-07-27
JP2007508494A (ja) 2007-04-05
CN1867775A (zh) 2006-11-22
WO2005038257A1 (en) 2005-04-28
SE524343C2 (sv) 2004-07-27
SE0302739D0 (sv) 2003-10-17
EP1687539A1 (en) 2006-08-09
CN100458164C (zh) 2009-02-04
KR20060097018A (ko) 2006-09-13

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Legal Events

Date Code Title Description
AS Assignment

Owner name: SVENSKA ROTOR MASKINER AB, SWEDEN

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:SUNDSTROM, MATS;OHMAN, HENRIK;REEL/FRAME:018609/0896

Effective date: 20060502

STCB Information on status: application discontinuation

Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION