CN100562666C - The system and method for screw compressor capacity control - Google Patents
The system and method for screw compressor capacity control Download PDFInfo
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- CN100562666C CN100562666C CNB2006800105948A CN200680010594A CN100562666C CN 100562666 C CN100562666 C CN 100562666C CN B2006800105948 A CNB2006800105948 A CN B2006800105948A CN 200680010594 A CN200680010594 A CN 200680010594A CN 100562666 C CN100562666 C CN 100562666C
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- 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
- F04C28/24—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
- F04C28/26—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves using bypass channels
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- 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
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- 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
Abstract
Carry out the system and method for screw compressor capacity control, described system comprises: helical-lobe compressor, described compressor by how fast function motoring with pressurized air or gaseous mediums, bypass inlet member with bypass valve, its zone of high pressure from helical-lobe compressor extends to low pressure area with the recycle gas media, the functional bypass valve controller that is connected in described bypass valve, functionally be connected in motor to realize the electric motor controller of how fast function operation, the main processing control unit of may command bypass valve and the operation of how fast function, be positioned on the compression media passage and change with the signal form measuring pressure and/or the measuring device of temperature variation, the functional signal adapter that is connected in Main Processor Unit and measuring device with received signal, and described electric motor controller and bypass valve controller function are connected in Main Processor Unit to carry out the volume controlled of helical-lobe compressor.
Description
Technical field
The present invention relates to rotary screw machine, more specifically, relate to the system and method for controlling the swept volume of helical-lobe compressor by the combination that utilizes bypass compression media and change air compressor motor speed.
Background technique
Easy and simple to handle and length of life reliable performance is stable because of it is widely used in the various commercial Application for helical-lobe compressor.Helical-lobe compressor generally comprises intermeshing public helical rotor and female helical rotor.Rotor is by rotations such as prime mover such as motor, motors, with the inlet air/gas compression access arrangement that will provide, the process of installing or need pressurized air or operation of other gas or work.
Helical-lobe compressor is typically designed to specific speed ride quality the best, but most time for want of relevant device or device or need pressurized air or the process of operation of other gas or work can not be moved with design speed the demand of pressurized air or other gas.The helical-lobe compressor partial load run causes its performance and energy efficiency to reduce.Under the perfect condition, compression system should meet demand all the time and not cause under the mode of any additional-energy and loss in efficiency and move in compressor airflow output.
Air-flow output in order to ensure the compressed air/gas of helical-lobe compressor meets demand all the time, and several capacity control methods just in use and be reported in the various research documents.
In one known method, the volume controlled of helical-lobe compressor is carried out by slide-valve gear, wherein uses the opening area of controlling air vent by the guiding valve of suitable control mechanism operation.This method provides unconfined volume controlled in the entire capacity control range.But because of safeguarding that relevant issues are not suitable for comprising various sliding parts.
In another known method, the volume controlled operation is carried out by suction throttle, wherein controls the valve of compressor air suction mouth and controls the air mass that enters compressor.Air through this valve is carried out the corresponding increase that throttling causes the pressure loss and overall pressure ratio, thereby increase power input, the gain of having offset volume controlled.
In the another known method, exit to carry out volume controlled by a small amount of oil of emitting pressurized gas and mix with pressurized gas.This method does not provide any advantage aspect power consumpiton, can not be used for the oil injection type compressor simultaneously.
The volume controlled of rotary compressor motor is also carried out by multi-function (speed and power) (multi-capacity (rate and power)) motor (two utmost points, four utmost points, situation pole motor) that uses non-dynamic type.
In another known method, the volume controlled of compressor is carried out by the speed that is changed motor by the variable velocity frequency drives.Because this method may command entire capacity control procedure, so this method is efficiently.The capacity minimizing that the major defect of this method is expensive and power reduces with rotating speed with equipment reduces is not directly proportional.
As mentioned above, many capacity control methods can with and be used for the dynamic capacity control of helical-lobe compressor.It is the highest as reduce the 20-30% operational efficiency at most from 100% capacity that the major defect of these methods is that these systems only reduce scope for small capacity.These systems also can further reduce capacity, but the minimizing of helical-lobe compressor input power is identical with the minimizing of capacity at this moment.
Because of less this problem existence of the capacity minimizing limit of power of each dynamic capacity controlling method, market trend is just turning to uses the screw compression systems of being furnished with variable frequency drives (VFD).The screw compressor system of being furnished with the VFD system can provide point-device control to the screw compressor capacity of 30-100% scope.Simultaneously these are furnished with the pressurized air of systems' output of VFD or the requirement that other gas meets relevant device, device or process very much.VFD is as the optional feature of screw compressor system, and himself is the form produce power loss to generate heat in the frequency of supply adjustment process.Except that the energy loss, also cause importing the power supply network distortion and increase sound level.By regulating frequency of supply, VFD is with lower or higher revolutions operation associated screws compressor.Related system such as helical-lobe compressor are the highest in the optimum speed operational efficiency, and the various losses of volumetric efficiency reduction etc. make its performance reduction when producing as low speed with the speed operation helical-lobe compressor that is lower than the best or design speed because of low cruise.Therefore, clearly, even the supply and demand of system conform to, the energy efficiency of whole system is also very low.
Goal of the invention
Primary and foremost purpose of the present invention provides has built-in bypass flow structure and by producing, regulate pressurized air or the gas stream of gas or many speed or multi-function (speed and power) electric motor driven screw compressor system and method for conveying.
One of purpose of the present invention provides the system and method that does not use variable frequency drives (VFD).
Summary of the invention
The invention provides the system and method for carrying out screw compressor capacity control, described system comprises: by the helical-lobe compressor of multi-function (speed and power) motoring with pressurized air or gaseous mediums, extend to the bypass inlet member with bypass valve of low pressure area from the zone of high pressure of helical-lobe compressor with the circulation gaseous medium, the functional bypass valve controller that is connected in described bypass valve, the functional electric motor controller that is connected in motor multi-function to realize (speed and power) (multi-capacity (rate andpower)) operation, the main processing control unit of may command bypass valve and multi-function (speed and power) operation, be positioned on the compression media passage and change with the signal form measuring pressure and/or the measuring device of temperature variation, the functional signal adapter that is connected in Main Processor Unit and measuring device with received signal, and described electric motor controller and bypass valve controller function are connected in Main Processor Unit to carry out the volume controlled of helical-lobe compressor.
Brief Description Of Drawings
Fig. 1 is the schematic representation of system of the present invention.
Fig. 2 is the partial cross section figure that is furnished with the helical-lobe compressor of the present invention of the bypass tube that is connected in master controller.
Fig. 3 is the side view that driving element and the functional motor driver that is connected of master controller are shown.
Fig. 4 is the flow chart that rotary screw machine capacity control method of the present invention is shown.
Fig. 5 is the schematic representation that loss in efficiency compares explanation between the helical-lobe compressor that drives to helical-lobe compressor of the present invention and by variable frequency drives.
Fig. 6 is to be the diagrammatic representation of the volume controlled operation/method series of rotary screw machine of the present invention under the power supply condition of 50Hz for frequency.
Embodiment
Therefore, the invention provides utilization pressurized air or gas are carried out the rotary screw machine system and method that the helical-lobe compressor air displacement is controlled in bypass and the combination that air compressor motor speed is changed.The construction features of system of the present invention are with reference to Fig. 1-3 explanation.
At first, with reference to Fig. 1, i.e. the schematic representation of compression system of the present invention, wherein rotary screw machine 1 drives with pressurized gas or air medium by multi-function (speed and power) motor 2 and discharges the compression media.
Helical-lobe compressor 1 comprises rotor shell, and male rotor 11 and mother rotor 12 continue the engagement rotation in this rotor shell.Gaseous medium air or gas enter rotor shell through upstream line or suction tude 13, are compressed into required pressure level afterwards during the suction end from rotor shell is delivered to exhaust end.Then pressurized air or gas are transported to end use application 6 through each subassembly net of described compression system hereinafter.
The construction features of by-pass structure of the present invention
The bypass tube 14 that extends from by-pass port 18 has bypass valve 10, and described bypass tube 14 extends to low pressure area with recycle gas or air medium from the zone of high pressure of helical-lobe compressor.Bypass valve of the present invention can be the valve of vertical operation known in the art or rotation, so that the media flow through control to be provided.Bypass valve controller 7 is devices of may command bypass valve 10.Valve control 7 is that stepping motor maybe can drive or transmit any suitable mechanical device of driving function to bypass valve 10.Bypass valve arrangement of the present invention also can realize by adjusting slide-valve gear.
The construction features of motor drive arrangement of the present invention
Multi-function (speed and power) motor 2 with axle is through suitable transmission assembly 19 prime mover as helical-lobe compressor 1.Suitably power transmission mechanism 19 comprises the axle of motor 2 and direct coupling or the gear transmission or the belt sheave structure of male rotor 11.Multi-function (speed and power) motor 2 generally is furnished with in-built electrical winding net, is suitable for as different poles structures such as 2 utmost points, 4 utmost points, 6 utmost points operation multi-function (speed and power) motor 2.Consider the job requirement of compressor 1, the electrode structure of motor 2 can start the specific speed operation of particular pole structure.
One-way valve 4 promotes the one-way flow of pressurized air or gas between oil separating case 3 and storage vessel 5.
A plurality of sensing devices (not shown in the accompanying drawing) are positioned on the storage vessel 5.Sensing device also can be in the exhaust passage between compressor outlet 13a and the end use application 6 any position.Sensing device is a pressure transducer, but the variation of pressure sensor level and be emitted as analogue signal 15.In the present invention, as exemplary embodiment, sensing is to use pressure transducer to carry out.But but the also combination of serviceability temperature sensor and pressure and temperature transducer.Use the pressurized gas of pneumatic sensor measurement discharge or the flow velocity of air also to belong to scope of the present invention to generate corresponding signal 15.
Signal conversion interface unit 20 can be converted to digital signal with the analogue signal 15 that sensing device generates.The digital signal of conversion will further be transferred to hereinafter described Main Processor Unit 8.
Main processing control unit
Main processing control unit 8 of the present invention is based on the device of microcontroller, has the instruction group that each connection set of control comprises motor control unit 9, by-pass governing unit 7.The microcontroller that the present invention uses is the device that generally is used to carry out this type of control operation.
The integration of main control processing unit and bypass, electric motor controller
Main processing control unit 8 is connected in by-pass governing unit 7 and motor control unit 9 through conductive material.
Use system of the present invention to carry out the method for screw compressor capacity control
The method of the screw compressor capacity control of the present invention of explanation now.
Bypass flow referring now to compressor control pressurized air of the present invention or gas illustrates treatment step of the present invention with multi-function (speed and the power) of motor 2 with the different operation phase that generate and regulate pressurized air or gas stream or output.
Initialization process
The method of the air displacement of system of the present invention control helical-lobe compressor 1 is used in explanation now.Above-mentioned helical-lobe compressor 1 and control unit and other device energising are handled with the compression of carrying out air or gas.During beginning, be mounted with the instruction group of control system operation aspect based on the main processing control unit 8 of microcontroller.
Working principle for stepless capacity control system that proposition is described, as exemplary embodiment, use the utmost point with requirement and the three-speed motor 2 of realizing the electric winding/structure of three speed (N1, N2 and N3) to carry out the volume controlled of helical-lobe compressor 1 of the present invention.
The speed step value assignment of main processing controller
After considering the velocity structure of motor 2, be dispensed to the corresponding speed stepping that respectively is called N1, N2 and N3 and be respectively per minute 1500 commentaries on classics, 1000 commentaries on classics and 750 commentaries on classics.The value that should note N1 is maximum all the time, and the speed maximum value that provides during the processing to motor is provided.In case determine the maximum speed value N1 of motor 2, the corresponding velocity amplitude that reduces is N2 and N3.Value N1, N2 and the N3 input data of the processing control unit 8 of deciding, the required rpm that makes control unit 8 regulate motor 2 in each stage of operation of helical-lobe compressor 1.Be appreciated that the value of N herein meets the electromotor velocity structure of any selected motor.Therefore, the value of N can change in N1 to Nn scope.
The force value assignment of main processing control unit
In any given system based on compressor, the variation of exhaust pressure is the function of 6 pairs of pressurized air of related application or gas demand.Therefore, must the required pressure of control compressor operating in each stage.In the present invention, consider velocity amplitude N1, N2 and N3, the relevant pressure value is given main processing control unit 8 with SP1, SP2 and SP3 form as the input data.
Owing to the exhaust pressure of monitoring compressor of the present invention at run duration all the time, must measure these values and continue input for main control unit 8 provides.As mentioned above, these values are measured by sensing device.Preset time, the exhaust pressure value of point was called MP.
After helical-lobe compressor 1 brings into operation, MP force value and force value SP1, SP2 and the SP3 that monitors all the time compared, find out the value that conforms to.The MP value is when arbitrary force value among SP1, SP2 or the SP3 conforms to, and motor control unit 9 changes electromotor velocity by selection and SP1, SP2 from arbitrary N1, N2 or N3 value or the corresponding rpm of SP3.
Based on above-mentioned initial phase, the working principle of helical-lobe compressor of the present invention 1 system is described now.Run duration, screw compressor system of the present invention were executed in the following operation phase, i.e. the start up period, working pressure increases stage and volume controlled stage.
The start up period:
Helical-lobe compressor 1 the start up period in, effective electrode structure of motor 2 can maximum available velocity service meter 2, promptly motor 2 moves with velocity amplitude N1.In this stage, bypass valve 10 cuts out fully, because the operation starting stage is the normal pressure state.
Working pressure increases the stage:
Be appreciated that force value SP1 is called the normal operating pressure of helical-lobe compressor 1.Increase the stage in working pressure, main processing control unit 8 is with speed N1 service meter 2, and bypass control valve (BCV) 10 is in buttoned-up status, equals SP1 until the exhaust pressure value MP that continues monitoring.
The volume controlled stage:
The working pressure increase stage begins the volume controlled stage after finishing.As long as the demand of 6 pairs of pressurized air of end use application or gas reduces, just require helical-lobe compressor 1 to move under the stage in volume controlled.In the volume controlled stage, the pressure of pressure sensor sensing pressurized air or gas, and generate signal 15 with analog signal form input analog-to-digital converter (ADC) 20, provides to main processing control unit 8 to be used for further processing afterwards.
Referring now to Fig. 4, the logical operation or the instruction group of main processing control unit 8 is described.
When the force value MP that continues to monitor was less than or equal to SP1, main processing control unit 8 did not generate any signal of motor control unit 9 and by-pass governing unit 7, made motor continue the operation with speed N1, and bypass valve 10 is in buttoned-up status.
The force value MP that continues monitoring is during less than force value SP2 and greater than force value SP1, and main processing control unit 8 generates the signal 17 of by-pass governing unit 7, does not generate any signal of motor control unit 9, makes motor move with top speed N1.When receiving signal 17, by-pass governing unit 7 is opened bypass valve 10 and is equaled the SP1 value until the MP value.
When the force value MP that continues to monitor equaled force value SP2, main processing control unit 8 generated signals 16 and 17.By-pass governing unit 7 response signals 17 are closed bypass valve 10 fully.After valve 10 response signals 17 were closed, motor control unit 9 was changed into N2 with the velocity amplitude of motor 2, i.e. motor 2 beginnings move with speed N2.
The force value MP that continues monitoring is during less than SP3 and greater than SP2, and main processing control unit 8 does not generate signal 16, only generates signal 17.By-pass governing unit 7 response signals 17 are opened bypass valve 10 and are equaled the SP1 value until the MP value.
When the force value MP that continues to monitor equaled SP3, main processing control unit 8 generated signals 16 and 17.By-pass governing unit 7 response signals 17 are closed bypass valve 10 fully, and motor control unit 9 response signals 17 are changed into velocity amplitude N3 with electromotor velocity afterwards, i.e. motor 2 beginnings move with speed N3.
The force value MP that continues monitoring is during greater than SP3, and main processing control unit 8 only generates signal 17, does not generate signal 16.By-pass governing unit 7 response signals 17 are opened bypass valve 10 and are equaled SP1 until MP.By carrying out above-mentioned group of operation, guaranteed the continuous rating control of helical-lobe compressor of the present invention.
Be noted herein that above-mentioned group of operation is in view of the three-speed motor explanation.It will be appreciated by those skilled in the art that aforesaid operations can be inferior according to pressure and electromotor velocity factor circulation ' n '.
System of the present invention also can save the bypass inlet member that is used for bypass intermediate compression air or gas and carry out.In the case, multi-function (speed and the power) of motor is realized by the stepping control structure.Volume controlled will be carried out stage by stage in this structure.
The performance of not using the helical-lobe compressor of the present invention of VFD has been described.The factor that influences the compressor assembly total efficiency is compressor speed and motor efficiency.Therefore, carry out system of the present invention, make that the volume controlled of compressor and efficient are improved to optimize this two factors.For the efficient of determining that compressor of the present invention improves, done comparative descriptions with compressor with VFD, its result makes table 1.But, should notice that here in fact comparison value is indicative, because these values change with the capacity of compressor is different.
Table 1
From above table 1 as can be seen, do not use the compressor of the present invention of VFD higher than the compressor efficiency that uses the VFD operation.For example,, use under the compressor situation of VFD if capacity required is reduced to 80%, need be with 20% operation of ideal velocity.But in compressor of the present invention, same capacity reduces 80%, and compressor is with 50% operation of design speed.
The result of table 1 is plotted among Fig. 5 in view of compressor capacity (%) and overall efficiency loss (%), clearly shows compressor augmented performance of the present invention.
Prepare the hypothesis that performance comparison sheet 1 is done:
1.100% refers to the performance of helical-lobe compressor 1 under the best rotational speed of given compressor.
2. to the minimizing of any frequency of supply, the loss in efficiency of VFD is counted as 4%.
3. when helical-lobe compressor 1 was driven by multi-function (speed and power) motor 2, thinking did not have the motor efficiency loss, because these motor are specifically designed different effectively electrode structures or the friction speed stepping moves with same efficiency.
4. helical-lobe compressor 1 does not have the bypass flow structure and when being driven by the standard single speed motor 1 of being furnished with VFD, during with low cruise, the efficient of motor 2 has decline slightly because this motor 1 is a standard motor, only be designed to specific effectively or most effective in the design electrode structure.
5. the speed of helical-lobe compressor 1 reduces at 40% o'clock from the best or design speed value, and the minimizing of helical-lobe compressor 1 total efficiency is assumed to 10%
In the performance comparison sheet 1 to given range 20 to the proportional calculating of 100% each numerical value that provides.
Each numerical value that provides in the performance comparison sheet 1 only is indicative, and numerical value can be different between different system.
Therefore, the invention provides the system that carries out screw compressor capacity control, described system comprises: helical-lobe compressor, described compressor by multi-function (speed and power) motoring with the compression media, bypass inlet member with bypass valve, extend to low pressure area with the recycle gas media from the zone of high pressure of helical-lobe compressor, the functional bypass valve controller that is connected in described bypass valve, the functional electric motor controller that is connected in motor multi-function to realize (speed and power) operation, the main processing control unit of may command bypass valve and multi-function (speed and power) operation, be positioned on the compression media passage and change with the signal form measuring pressure and/or the measuring device of temperature variation, the functional signal adapter that is connected in main processing control unit and measuring device with received signal, and described electric motor controller and bypass valve controller function are connected in main processing control unit to carry out the volume controlled of helical-lobe compressor.
In the system of the embodiment of the invention, wherein measuring device is pressure or temperature transducer.
In the system of another embodiment of the present invention, wherein the pressure of air or gas has malleation by the bypass inlet member on the helical-lobe compressor place of the moving compressor.
In the system of further embodiment of this invention, wherein helical-lobe compressor does not have bypass inlet member and by-pass governing device.
The present invention also provides the capacity control method of the helical-lobe compressor of claim 1 requirement, said method comprising the steps of: for compressor is provided with a plurality of force value and respective electrical motivation function (speed and power) value, measure the exhaust pressure of compressor, compare exhaust pressure value and preset pressure value, close with output compression media with top speed initial launch multi-function (speed and power) motor while bypass valve when exhaust pressure value equals preset pressure value, and control the desired volume of the capacity of compressor by the speed of main processing control unit relative adjustment bypass valve and multi-function (speed and power) motor with the acquisition compressor.
In the method for another embodiment of the present invention, wherein by measure exhaust pressure, comparison exhaust pressure and preset pressure value, with the electromotor velocity value service meter of corresponding preset pressure value and control bypass valve is carried out compressor capacity with the desired volume of acquisition compressor control.
In the method for another embodiment of the present invention, wherein as long as exhaust pressure value is when equaling preset pressure value, the initial motor speed value is changed to corresponding preset pressure value.
In the method for another embodiment of the present invention, regulate opening of bypass valve when wherein exhaust pressure value is not equal to preset pressure value.
Although illustrated and be considered to the preferred embodiment of the invention at present, clearly can make various changes and correction for a person skilled in the art to it, and do not deviate from the present invention, therefore the present invention includes institute in true spirit of the present invention and the scope and change and revise.
Advantage of the present invention
1. the noise of comparing generation with the system with VFD is littler.
2. owing to do not use any frequency adjustment to netting in the VFD situation, power supply network does not have distortion.
3. system cost is lower than the system cost with VFD about 25 to 30%.
4. because all control systems can be installed in compressor and motor body self, size Very compact.
5. total operational efficiency of compression system more is better than having the compression system about 30 to 40% of VFD.
6. the air vent flow area is opened the easy and independent operating of control system of control and the effective utmost point control of motor.
7. relevant technologies does not have the VFD technical sophistication.
Claims (7)
1. carry out the system of volume controlled in the helical-lobe compressor, described system comprises:
(a) helical-lobe compressor, by the multi-function motoring that has corresponding to the firm power output of each selected speed, with the pressurized gas media, described compressor has the compressing area between suction tude and exhaust passage
(b) bypass section between the zone in described suction tude and described compressing area, the pressure at a little higher than suction tude of pressure place wherein,
(c) have the bypass tube of closed bypass valve, it extends to described suction tude with the recycle gas media from described bypass section,
(d) main processing control unit,
(e) be arranged in the measuring device of the compression media passage of described compressor with variation of signal form measuring pressure and/or temperature variation,
(f) functionally be connected in described main processing control unit and described measuring device receiving the signal adapter of described signal,
(g) the functional bypass valve controller that is connected in described bypass valve,
(h) functionally be connected in described motor realizing the electric motor controller of multi-function operation, described bypass valve controller and electric motor controller be functional to be connected in described main processing control unit,
(i) when receiving described signal, described main processing control unit can be opened described closed bypass valve gradually by described bypass valve controller, controlling the capacity of described compressor, and
(j) when receiving described signal, described main processing control unit also can be by described electric motor controller with the rate conversion of described motor to next setting speed, with the described compressor capacity of box lunch equal described next when setting capacity under electromotor velocity, control described compressor capacity by closing described bypass valve.
2. the system as claimed in claim 1, wherein said measuring device is pressure or temperature transducer.
3. the system as claimed in claim 1, wherein said helical-lobe compressor does not have bypass suction tude and by-pass governing device.
4. the capacity control method in the helical-lobe compressor said method comprising the steps of:
(a) for described compressor is provided with a plurality of force value and corresponding electromotor velocity value,
(b) exhaust pressure of the described compressor of measurement,
(c) more described exhaust pressure value and preset pressure value,
(d) when described exhaust pressure value equals preset pressure value, with the described multi-function motor of top speed initial operation, simultaneously bypass valve cuts out, with export compressed media and
(e) control the capacity of described compressor by the speed of described described bypass valve of main processing control unit relative adjustment and multispeed motor, to obtain the desired volume of described compressor.
5. method as claimed in claim 4, wherein the control of described compressor capacity is carried out by following steps:
(a) measure described exhaust pressure,
(b) more described exhaust pressure and preset pressure value,
(c) with the corresponding electromotor velocity value of described preset pressure value turn round described motor and
(d) the described bypass valve of control is to obtain the desired volume of described compressor.
6. method as claimed in claim 5 is wherein as long as described exhaust pressure value when equaling preset pressure value, is changed to corresponding preset pressure value with the initial motor speed value.
7. method as claimed in claim 5 wherein when described exhaust pressure value is not equal to preset pressure value, is regulated opening of described bypass valve.
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| IN85CH2005 | 2005-02-02 | ||
| IN85/CHE/2005 | 2005-02-02 |
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| US (1) | US20080286087A1 (en) |
| EP (1) | EP1844236B1 (en) |
| CN (1) | CN100562666C (en) |
| AT (1) | ATE504743T1 (en) |
| DE (1) | DE602006021137D1 (en) |
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| EA201170677A1 (en) * | 2008-11-12 | 2011-10-31 | Эксонмобил Апстрим Рисерч Компани | BALLOON-COMPRESSOR METHODS AND SYSTEMS |
| JP5318062B2 (en) * | 2010-10-04 | 2013-10-16 | 株式会社神戸製鋼所 | Screw expander |
| TWI400415B (en) * | 2010-12-17 | 2013-07-01 | Ind Tech Res Inst | Controlling method of changeable capacity and changeable discharge pressure of a variable speed screw compressor |
| US10851785B2 (en) * | 2014-12-31 | 2020-12-01 | Ingersoll-Rand Industrial U.S., Inc. | Compressor system with variable blowdown control |
| WO2016112439A1 (en) * | 2015-01-15 | 2016-07-21 | Atlas Copco Airpower, Naamloze Vennootschap | Oil-injected vacuum pump element |
| CA2972636C (en) | 2015-01-15 | 2020-07-14 | Atlas Copco Airpower, Naamloze Vennootschap | Oil-injected vacuum pump element |
| BE1022764B1 (en) * | 2015-01-15 | 2016-08-30 | Atlas Copco Airpower Naamloze Vennootschap | Oil-injected vacuum pump element |
| US10808699B2 (en) | 2017-09-28 | 2020-10-20 | Ingersoll-Rand Industrial U.S., Inc. | Suction side slide valve for a screw compressor |
| CN108468643A (en) * | 2018-05-18 | 2018-08-31 | 麦克维尔空调制冷(武汉)有限公司 | It can determine the screw compressor capacity control system and method for the operation of frequency speed-changing |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE2641482A1 (en) * | 1976-09-15 | 1978-03-16 | Aerzener Maschf Gmbh | SCREW COMPRESSOR |
| JPS5718483A (en) * | 1980-07-08 | 1982-01-30 | Mayekawa Mfg Co Ltd | Speed control unit of screw type compressor |
| SE457822B (en) * | 1986-11-28 | 1989-01-30 | Svenska Rotor Maskiner Ab | PROCEDURES FOR AUTHORIZATION OF SELECTIVELY CONTROLLED PRESSURE PULSES IN A GAS MASS AND DEVICE FOR IMPLEMENTATION OF THE PROCEDURE |
| SE461346B (en) * | 1988-06-17 | 1990-02-05 | Svenska Rotor Maskiner Ab | ROTATE COMPRESSOR COMPRESSOR AND A REFRIGERATOR, A COMPRESSOR OF THE ABOVE TYPE NOT INCLUDED |
| US5183395A (en) * | 1992-03-13 | 1993-02-02 | Vilter Manufacturing Corporation | Compressor slide valve control |
| DE4221494C2 (en) * | 1992-06-29 | 2003-03-13 | Grasso Gmbh Refrigeration Tech | Flow change on a screw compressor |
| JP3325196B2 (en) * | 1997-03-31 | 2002-09-17 | 日本コムテック株式会社 | Screw compressor |
| JP3837278B2 (en) * | 2000-08-10 | 2006-10-25 | 株式会社神戸製鋼所 | Compressor operation method |
| US6659729B2 (en) * | 2001-02-15 | 2003-12-09 | Mayekawa Mfg. Co., Ltd. | Screw compressor equipment for accommodating low compression ratio and pressure variation and the operation method thereof |
| US6527522B2 (en) | 2001-07-03 | 2003-03-04 | Yen Sun Technology Corp. | Heat dissipation fan structure |
-
2006
- 2006-02-01 EP EP06711366A patent/EP1844236B1/en not_active Not-in-force
- 2006-02-01 WO PCT/IN2006/000038 patent/WO2006095364A1/en active Application Filing
- 2006-02-01 DE DE602006021137T patent/DE602006021137D1/en active Active
- 2006-02-01 US US11/883,373 patent/US20080286087A1/en not_active Abandoned
- 2006-02-01 AT AT06711366T patent/ATE504743T1/en not_active IP Right Cessation
- 2006-02-01 CN CNB2006800105948A patent/CN100562666C/en not_active Expired - Fee Related
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2008
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Also Published As
| Publication number | Publication date |
|---|---|
| EP1844236A1 (en) | 2007-10-17 |
| CN101163885A (en) | 2008-04-16 |
| ATE504743T1 (en) | 2011-04-15 |
| US20080286087A1 (en) | 2008-11-20 |
| DE602006021137D1 (en) | 2011-05-19 |
| EP1844236B1 (en) | 2011-04-06 |
| HK1116852A1 (en) | 2009-01-02 |
| WO2006095364A1 (en) | 2006-09-14 |
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