EP3388677A1 - Procédé de commande d'un compresseur à vis - Google Patents

Procédé de commande d'un compresseur à vis Download PDF

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Publication number
EP3388677A1
EP3388677A1 EP18164785.0A EP18164785A EP3388677A1 EP 3388677 A1 EP3388677 A1 EP 3388677A1 EP 18164785 A EP18164785 A EP 18164785A EP 3388677 A1 EP3388677 A1 EP 3388677A1
Authority
EP
European Patent Office
Prior art keywords
compressor
speed
compressor stage
stage
volume flow
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.)
Pending
Application number
EP18164785.0A
Other languages
German (de)
English (en)
Inventor
Ulrich Thomes
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 Deutschland GmbH
Original Assignee
Gardner Denver Deutschland GmbH
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 Gardner Denver Deutschland GmbH filed Critical Gardner Denver Deutschland GmbH
Publication of EP3388677A1 publication Critical patent/EP3388677A1/fr
Pending 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
    • 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
    • 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
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/001—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar working principle
    • F04C23/003—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar working principle having complementary function
    • 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
    • F04C28/02—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids specially adapted for several pumps connected in series or in parallel
    • 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
    • F04C28/06—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids specially adapted for stopping, starting, idling or no-load operation
    • 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
    • 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
    • F04C2240/40—Electric motor
    • F04C2240/402—Plurality of electronically synchronised motors
    • 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
    • F04C2270/00—Control; Monitoring or safety arrangements
    • F04C2270/02—Power
    • 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
    • F04C2270/00—Control; Monitoring or safety arrangements
    • F04C2270/05—Speed
    • F04C2270/052—Speed angular
    • 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
    • F04C2270/00—Control; Monitoring or safety arrangements
    • F04C2270/18—Pressure
    • 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
    • F04C2270/00—Control; Monitoring or safety arrangements
    • F04C2270/20—Flow
    • 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
    • F04C2270/00—Control; Monitoring or safety arrangements
    • F04C2270/44—Conditions at the outlet of a pump or machine

Definitions

  • the invention relates to a method for controlling a screw compressor, in particular a twin screw compressor in idle mode.
  • a screw compressor has at least a first and a second compressor stage, wherein the first compressor stage compresses a gaseous medium, usually air, and leads to the second compressor stage, which further compresses the medium and delivers it to a downstream system.
  • the inventive method is suitable for controlling directly driven screw compressors, in which both compressor stages are driven separately from one another and speed controlled.
  • the invention also relates to a compressor with a twin screw compressor controlled by this method in idle mode.
  • two or more variable speed drive means are provided, each drive means driving a respective one of the compressor stages.
  • a control unit controls the speeds of the drive means, monitoring the torque and speed of each drive means so that the screw compressor provides gas at a required flow delivery rate and pressure while minimizing power consumption of the screw compressor.
  • idling occurs as an operating condition.
  • no compressed air is removed from the downstream system, so that the delivery of additional medium must be set to avoid an increase in pressure.
  • the compressor should not be completely switched off in idle, if it must be reckoned with a short-term re-supply of compressed air.
  • a throttle valve is closed in the suction line and supplied via a bypass only a partial flow of the first compressor stage.
  • intake regulator which is arranged at the inlet of the first compressor stage.
  • the rotational speed of the upstream screw compressor unit is correlated with the rotational speed of the downstream screw compressor unit such that the final discharge pressure or the final delivery rate of the screw compressor system is kept constant, and / or the total power consumption the screw compressor system is minimized, or for a given total power consumption, a maximum end outlet pressure or a maximum end delivery volume is achieved.
  • this control method does not provide information for optimizing idle operation of the system and resulting energy savings.
  • the design complexity of the complete screw compressor should be reduced, resulting in a cost reduction in its manufacture should be derivable.
  • the invention provides a compressor in the nature of a twin screw compressor, which can be operated by this method.
  • the inventive method is used to control a screw compressor having at least a first and a second compressor stage, wherein the first compressor stage compresses a gaseous medium and leads to the second compressor stage, which further compresses the medium.
  • the first compressor stage is thus seen in the flow direction of the medium before the second compressor stage.
  • screw compressors have exactly two compressor stages, but also designs with more than two stages are possible.
  • both compressor stages are driven separately and speed controlled, d. H.
  • Each compressor stage is driven by a variable-speed drive, in particular by a direct drive, so that can be dispensed with a transfer case.
  • a volume flow of the compressed gaseous medium which is taken at the output of the second compressor stage or discharged to downstream units, detected with a suitable encoder.
  • a direct volume flow measurement can be used or the volume flow removed is indirectly z. B. determined from the prevailing at the output of the second compressor stage pressure conditions or from the occurring at the drive of the second compressor stage torque / drive current.
  • a volume flow is decreased, which can vary between a maximum value for which the screw compressor is designed, and a predetermined minimum value.
  • this load operation of the screw compressor is controlled in a conventional manner, which also includes that the speed of the drives of the two compressor stages can be varied within a predetermined range. If, during load operation, the volume flow decreases in a range between a maximum value and a predetermined minimum value, the controller reduces the speed of both compressor stages, and if the volume flow in this range increases again, the controller increases the speed of the compressor stages, so that in normal load operation predetermined output pressure is maintained.
  • a blow-off valve is opened in order to at least partially allow the volume flow initially supplied by the second compressor stage to be discharged via the blow-off valve. This prevents the pressure at the outlet of the screw compressor from exceeding a maximum permissible size.
  • the blow-off valve may be, for example, a controlled solenoid valve.
  • the speed of at least the first compressor stage is reduced to a predetermined idling speed V1 L in order to increase the volume flow delivered from the first to the second compressor stage to reduce.
  • a throttle valve or an intake regulator is currently not closed for this purpose. Rather, the inlet of the first compressor stage remains fully open. A throttle or an intake regulator and their control can be completely eliminated.
  • the reduction of the volumetric flow delivered by the first compressor stage preferably takes place exclusively via the reduction of the rotational speed of the first compressor stage to the idling rotational speed V1 L.
  • the speed of the second compressor stage is reduced to an idling speed V2 L in a next step.
  • the rotational speeds of both compressor stages are reduced substantially in parallel, each time down to the idling speed V1 L or V2 L.
  • the idling speed V1 L of the first compressor stage (Low Pressure - LP) is chosen in coordination with the idle speed V2 L of the second compressor stage (High Pressure - HP) so that the outlet temperature of the medium at the second stage is not less than the inlet temperature at this stage becomes.
  • Such an unwanted operating condition may occur when the pressure ratio at the second compressor stage becomes smaller than 0.6.
  • the idling speeds it must therefore be ensured that the second stage does not work as an "expander" and that the temperature of the medium drops as a result. Otherwise, undesirable condensation in the compressor may occur.
  • idle speeds to ensure that the second compressor stage is not driven by the transported medium from the first compressor stage, otherwise the drive of the second stage would switch to generator mode, which could lead to damage of this driving frequency converter.
  • the minimum idle speeds are also determined by which deceleration is acceptable on re-entry into the load condition. The shorter this return time, the higher the idle speed will have to be.
  • the idle speed ratio between the second and first stage is in the range of 2 to 3, more preferably about 2.5.
  • the pressure ratio of the first stage is about 1.5 and the pressure ratio of the second stage is approximately in the range of 0.6 to 0.75.
  • the idling speed V2 L of the second compressor stage is about 1/2 to 1/4 of the load speed of this stage.
  • the idle speed V1 L of the first compressor stage is about 1/5 to 1/8 of the load speed of this stage.
  • the compressor for compressing gaseous media comprises a screw compressor having at least a first and a second compressor stage, the first compressor stage compressing the gaseous medium and leading to the second compressor stage, which further compresses the medium, and both compressor stages are driven separately from each other and speed controlled.
  • the compressor further comprises a control unit configured to carry out the method described above.
  • the compressor is characterized in that the inlet of the fluidically front, first compressor stage is guided without a volume flow limiting, controllable throttle element or without an intake regulator to the ambient atmosphere.
  • the compressor has at the outlet of the fluidically rear, the second compressor stage a blow-off valve, which is caused by the control unit to open when the volume flow decreases below a predetermined minimum value.
  • Fig. 1 shows the basic structure of a compressor, which is designed as a twin screw compressor 200.
  • typical parameters are also given, such as those that occur during load operation when compressed air with a volume flow above a predetermined minimum value and not greater than a system-specific maximum value is requested.
  • a first compressor stage 201 has a first direct drive 202 which is speed-controlled.
  • the inlet of the first compressor stage 201 via which ambient air is sucked in, is coupled without the interposition of an intake regulator directly to an intake manifold 203, at which ambient atmosphere at a pressure of 1.0 bar at a temperature of e.g. B. 20 ° C is applied.
  • At the inlet of the first compressor stage 201 is thus at a pressure of 1.0 bar.
  • the first compressor stage 201 is z. B. operated at a speed of 15,500 min -1 to compress the air.
  • a pressure of 3.2 bar prevails, so that the first compressor stage has a compression ratio of 3.2 during load operation. Compression increases the temperature of the medium (compressed air) to 170 ° C.
  • the compressed air is conducted from the outlet of the first compressor stage 201 via an intercooler 204 to the inlet of a second compressor stage 206, which has a second, speed-controlled direct drive 207. After the intercooler 204, at the inlet of the second compressor stage 206, the compressed air has a temperature of for example 30 ° C and further a pressure of 3.2 bar.
  • the second compressor stage 206 In load operation, the second compressor stage 206 with a speed of z. B. 22,000 min -1 operated, so it comes to a further compression.
  • the compressed air therefore has a pressure of 10.2 bar and a temperature of 180 ° C at the outlet of the second compressor stage 206.
  • the second compressor stage thus also has a compression ratio of about 3.2.
  • the compressed air is passed from the outlet of the second compressor stage 206 through an aftercooler 208 and cooled there to about 35 ° C.
  • a blow-off valve 209 is arranged, which is controlled by a control unit (not shown).
  • the twin screw compressor 200 described by way of example exhibits a power consumption of 150 kW at maximum rotational speed of the direct drives 202, 207 and supplies compressed air with a maximum pressure of 12 bar and a minimum pressure of 6 bar.
  • the speed ratio between the compressor stages is approximately 1.4 during load operation.
  • Fig. 2 shows the twin screw compressor 200 in idle mode, that is, when substantially no compressed air is removed.
  • typical parameters are given, as they occur in idle mode.
  • the blow-off valve is opened and the speed of both compressor stages is reduced.
  • the inlet of the first compressor stage 201 via which further ambient air is sucked in, even if in a reduced amount, is further coupled without the interposition of a suction directly to the intake manifold 203, at which ambient atmosphere with a pressure of 1.0 bar at a temperature of 20 ° C is present.
  • At the inlet of the first compressor stage 201 is thus unchanged at a pressure of 1.0 bar.
  • the compressed air is supplied from the outlet of the first compressor stage 201 via the intercooler 204 led to the inlet of the second compressor stage 206. After the intercooler 204, at the inlet of the second compressor stage 206, the compressed air at idle has a temperature of for example 30 ° C and further a pressure of 1.5 bar (intermediate pressure).
  • the necessary cooling capacity for the intermediate cooling is thus reduced during idling operation.
  • the second compressor stage is operated 206 with an idle speed V2 L of 7.500 min -1.
  • the compressed air has at the outlet of the second compressor stage 206, a reduced pressure of about 1.2 bar and a temperature of 70 ° C compared to the intermediate pressure.
  • the second compressor stage thus has a compression ratio of about 0.8 (expansion).
  • the compressed air is passed from the outlet of the second compressor stage 206 through the aftercooler 208 and cooled there to about 30 ° C.
  • the twin screw compressor 200 described by way of example exhibits a power consumption of 7 kW during idling operation and delivers a maximum pressure of 1.2 bar.
  • the speed ratio between the compressor stages is about 3.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
EP18164785.0A 2017-04-10 2018-03-28 Procédé de commande d'un compresseur à vis Pending EP3388677A1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102017107601.8A DE102017107601B4 (de) 2017-04-10 2017-04-10 Verfahren zur Steuerung eines Schraubenverdichters

Publications (1)

Publication Number Publication Date
EP3388677A1 true EP3388677A1 (fr) 2018-10-17

Family

ID=61837603

Family Applications (1)

Application Number Title Priority Date Filing Date
EP18164785.0A Pending EP3388677A1 (fr) 2017-04-10 2018-03-28 Procédé de commande d'un compresseur à vis

Country Status (5)

Country Link
US (3) US11193489B2 (fr)
EP (1) EP3388677A1 (fr)
CN (1) CN108691768B (fr)
CA (1) CA3000496A1 (fr)
DE (1) DE102017107601B4 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102017107601B4 (de) 2017-04-10 2019-11-07 Gardner Denver Deutschland Gmbh Verfahren zur Steuerung eines Schraubenverdichters
JP7075305B2 (ja) * 2018-07-25 2022-05-25 北越工業株式会社 圧縮機の運転制御方法及び圧縮機
CN113294322B (zh) * 2020-02-24 2023-06-02 复盛实业(上海)有限公司 压缩机系统及其控制方法

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CN108691768B (zh) 2021-10-08
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DE102017107601A1 (de) 2018-10-11
US20230279857A1 (en) 2023-09-07
US11193489B2 (en) 2021-12-07
US20180291902A1 (en) 2018-10-11
CA3000496A1 (fr) 2018-10-10
US12092110B2 (en) 2024-09-17
US11686310B2 (en) 2023-06-27
US20220082100A1 (en) 2022-03-17

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