[go: up one dir, main page]

EP3918199B1 - Cooling arrangement and method for cooling a compressed-air generator with at least two stages - Google Patents

Cooling arrangement and method for cooling a compressed-air generator with at least two stages Download PDF

Info

Publication number
EP3918199B1
EP3918199B1 EP20704784.6A EP20704784A EP3918199B1 EP 3918199 B1 EP3918199 B1 EP 3918199B1 EP 20704784 A EP20704784 A EP 20704784A EP 3918199 B1 EP3918199 B1 EP 3918199B1
Authority
EP
European Patent Office
Prior art keywords
cooler
coolant
intercooler
aftercooler
subassembly
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.)
Active
Application number
EP20704784.6A
Other languages
German (de)
French (fr)
Other versions
EP3918199A1 (en
Inventor
Frank Georg Klaus
Ulrich Thomes
Marc Schiel
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
Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=69570619&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP3918199(B1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by Gardner Denver Deutschland GmbH filed Critical Gardner Denver Deutschland GmbH
Publication of EP3918199A1 publication Critical patent/EP3918199A1/en
Application granted granted Critical
Publication of EP3918199B1 publication Critical patent/EP3918199B1/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/06—Cooling; Heating; Prevention of freezing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/06—Cooling; Heating; Prevention of freezing
    • F04B39/066—Cooling by ventilation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B41/00—Pumping installations or systems specially adapted for elastic fluids
    • F04B41/06—Combinations of two or more pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/08—Cooling; Heating; Preventing freezing
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/04—Heating; Cooling; Heat insulation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J3/00—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification
    • F25J3/02—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification by rectification, i.e. by continuous interchange of heat and material between a vapour stream and a liquid stream
    • F25J3/04—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification by rectification, i.e. by continuous interchange of heat and material between a vapour stream and a liquid stream for air
    • F25J3/04006—Providing pressurised feed air or process streams within or from the air fractionation unit
    • F25J3/04012—Providing pressurised feed air or process streams within or from the air fractionation unit by compression of warm gaseous streams; details of intake or interstage cooling
    • F25J3/04018—Providing pressurised feed air or process streams within or from the air fractionation unit by compression of warm gaseous streams; details of intake or interstage cooling of main feed air
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J3/00—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification
    • F25J3/02—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification by rectification, i.e. by continuous interchange of heat and material between a vapour stream and a liquid stream
    • F25J3/04—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification by rectification, i.e. by continuous interchange of heat and material between a vapour stream and a liquid stream for air
    • F25J3/04521—Coupling of the air fractionation unit to an air gas-consuming unit, so-called integrated processes
    • F25J3/04612—Heat exchange integration with process streams, e.g. from the air gas consuming unit
    • F25J3/04618—Heat exchange integration with process streams, e.g. from the air gas consuming unit for cooling an air stream fed to the air fractionation unit
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J3/00—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification
    • F25J3/02—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification by rectification, i.e. by continuous interchange of heat and material between a vapour stream and a liquid stream
    • F25J3/04—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification by rectification, i.e. by continuous interchange of heat and material between a vapour stream and a liquid stream for air
    • F25J3/04763—Start-up or control of the process; Details of the apparatus used
    • F25J3/04769—Operation, control and regulation of the process; Instrumentation within the process
    • F25J3/04781—Pressure changing devices, e.g. for compression, expansion, liquid pumping
    • 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
    • F04C2210/00—Fluid
    • F04C2210/22—Fluid gaseous, i.e. compressible
    • F04C2210/221—Air
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J2230/00—Processes or apparatus involving steps for increasing the pressure of gaseous process streams
    • F25J2230/04—Compressor cooling arrangement, e.g. inter- or after-stage cooling or condensate removal

Definitions

  • the invention relates to a cooling arrangement for an at least two-stage compressed air generator.
  • a compressed air generator also called a compressor
  • a liquid-cooled intercooler which is arranged between a first and a second compressor stage, in order to cool the pre-compressed air discharged from the first compressor stage before it enters the second compressor stage
  • a liquid-cooled aftercooler which is arranged after the second compressor stage in order to cool the compressed air of this.
  • a liquid-cooled assembly cooler is provided, which absorbs heat from other assemblies of the compressed air generator, for example to cool power electronics or drives and gears of the compressor stages.
  • a coolant circuit runs through a main cooler, the cold side of which feeds a coolant to the respective coolant inlet of the intercooler, the aftercooler and the assembly cooler, and the hot side of which receives the heated coolant exiting at the coolant outlet of the intercooler and the aftercooler.
  • the invention also relates to a method for cooling an at least two-stage compressed air generator.
  • compressors for compressing gaseous media, in particular for generating compressed air.
  • the DE 601 17 821 T2 a multi-stage screw compressor having two or more compression stages, each compression stage including a pair of rotors for compressing a gas.
  • two or more variable speed drive means are provided, each drive means driving a respective compressor stage.
  • the EP 2 886 862 A1 describes a compressor with a motor, a drive shaft, a crank mechanism connected thereto, at least one compressed air generating device, a crankcase and a compressed air storage tank. All components are cooled with the aid of a flow of cooling air generated by a fan wheel.
  • a compressor system is known with a system housing in which several heat-generating system components are arranged.
  • This includes a double screw compressor with two compression stages, which serve to compress a gaseous medium, in particular to generate compressed air.
  • the system housing also contains an air-to-water cooler, a fan that generates a flow of cooling air, and air guiding elements that guide the air that has been heated by the system components to the air-to-water cooler.
  • the EP 2 529 116 B1 describes a method for recovering energy from the compression of a gas by a compressor with two or more pressure stages.
  • a heat exchanger with a primary part and a secondary part is provided downstream of the compressor.
  • the gas compressed from a pressure stage is routed through the primary part; a coolant is conducted through the secondary part.
  • the WO 2015/172206 A9 shows a compressor with at least two compression stages in series and at least two coolers, namely an intercooler between the compression stages and an aftercooler downstream after the last compression stage.
  • At least two of the coolers are designed as split coolers so that the secondary side through which the coolant flows is divided into two stages to cool the gas flowing through on the primary side in a hot stage and a cool stage.
  • the two stages of the secondary side are interconnected in different cooling circuits. For example, each of the first stages of the plurality of coolers and each of the second stages are connected in series.
  • the DE 31 34 844 A1 describes a method for energetic optimization of a compression process, in particular for multi-stage compression with centrifugal and piston compressors.
  • a heat pump is integrated into a compressor system for this purpose.
  • At least one evaporator of the heat pump is preferably integrated into the pipelines of the cooling stages carrying the heated cooling water.
  • a compressor module which includes a compressor with a housing with an integrated compressor cooler.
  • two such modules can be combined with one another, so that a low-pressure compressor module and a high-pressure compressor module are connected in series.
  • Each of the two compressor modules has a liquid-cooled cooler that cools the compressed air at the module outlet.
  • an engine cooler and a component cooler are provided, the coolant circuit of which is connected to that of the compressor cooler.
  • one object of the present invention is, on the one hand, to ensure efficient cooling of such compressed air generators (compressor systems) while reducing the outlay on equipment, but on the other hand to allow more efficient heat recovery in relation to the entire compressed air generator.
  • the cooling arrangement according to the invention is suitable for cooling a compressed air generator, preferably in the form of a compressor system, with at least two compressor stages.
  • the cooling arrangement includes at least one liquid-cooled intercooler arranged between a first and a second compressor stage for cooling the supercharged air discharged from the first compressor stage before it enters the second compressor stage.
  • a liquid-cooled aftercooler is located after the second or final compressor stage to cool the further compressed air.
  • the compressed air generated is made available to external units after it has flowed through the aftercooler.
  • the compressed air generator can also have more than two compressor stages and correspondingly additional intermediate coolers.
  • the cooling arrangement includes a liquid-cooled assembly cooler, which absorbs heat from other assemblies of the compressed air generator and transfers it to the coolant.
  • the module cooler is arranged in the housing of the compressed air generator and z. B. designed as a finned cooler, heat sink, heat pipe or the like.
  • the component cooler can be made up of several individual coolers and is used to dissipate heat, in particular from the drives of the compressor stages and the power electronics that are required to control the compressed air generator.
  • the cooling arrangement has a coolant circuit which includes a main cooler in order to dissipate the heat absorbed by the coolant in the other coolers from the compressed air generator.
  • the cold side of the main cooler delivers chilled coolant at a low temperature directly to the respective coolant inlets of the intercooler, the aftercooler and the assembly cooler.
  • the coolant inlets of the intercooler(s), aftercooler and assembly cooler(s) are connected in parallel so that the coolant is supplied to them at the same low temperature.
  • the hot end of the main cooler receives the heated coolant directly from the respective coolant outlet of the intercooler (or multiple intercoolers) and the aftercooler, or indirectly from them if a heat exchanger for heat recovery is interposed, as will be described further below.
  • the coolant outlets from the intercooler(s) and aftercooler are connected in parallel and supply the heated coolant at a high temperature to the main cooler, possibly via the heat exchanger.
  • the coolant outlet of the component cooler is not connected in parallel with the coolant outlet of the intercooler or aftercooler. This prevents the coolant from being cooled down from the high temperature at the outlet of the intercooler and aftercooler by the admixture from the subassembly cooler, because the subassembly cooler regularly delivers lower temperatures of the coolant due to the lower amount of heat to be dissipated.
  • the coolant of the assembly cooler is fed to a feed inlet of the intercooler and/or the aftercooler, with the feed inlet being arranged between the coolant inlet and coolant outlet, at a position at which the intermediate temperature of the coolant in the intercooler or aftercooler reaches the outlet temperature of the coolant at the assembly cooler corresponds to ⁇ 20%.
  • the temperature of the coolant mixed in by the assembly cooler preferably deviates by less than ⁇ 10%, in particular by less than ⁇ 3%, from the temperature at the point of admixture in the intercooler or aftercooler.
  • the same coolant (preferably water) is thus used for the intercooler, the aftercooler and the assembly cooler.
  • the main cooler can be made much smaller, which leads to a significant reduction in the size of the cooling circuit and thus the overall costs of the compressed air generator. Due to the described targeted feeding of the coolant supplied by the assembly cooler at the intermediate temperature into the intercooler and/or aftercooler, the high temperature present at the outlet of the intercooler and the aftercooler can be kept at a high level, preferably in the range of 90°C. This leads to a large temperature difference at the main cooler, so that its cooling surface can be kept smaller than when the inlet temperature at the main cooler is lower.
  • the required cooling area is proportional to the temperature difference between the inlet temperature (high temperature) and the desired outlet temperature (low temperature).
  • the coolant supplied by the component cooler is fed both to the intermediate cooler and to the aftercooler via the respective feed inlet.
  • a heat exchanger is connected in the coolant circuit between the respective coolant outlet of the intercooler and the aftercooler and the coolant inlet of the main cooler. The entire heat supplied to the coolant is thus available to the heat exchanger for transfer to a heat transfer medium.
  • the main cooler is preferably a water-air cooler or a water-water cooler or a combination cooler that uses water and air optionally as the cooling medium. This means that the user of the compressed air generator is free to implement the main cooling using fan-assisted exhaust air cooling or by connecting to an external liquid cooling medium.
  • the intercooler and/or the aftercooler have a plurality of feed inlets to which the coolant can be selectively fed from the coolant outlet of the subassembly cooler.
  • a distributor unit is arranged between the coolant outlet of the component cooler and the feed inputs, which temperature-controlled supplies that feed input at which the intermediate temperature of the coolant in the intercooler or aftercooler is closest to the outlet temperature of the coolant on the component cooler.
  • the cooling arrangement is thus an integral part of the compressed air generator, so that the installation effort for the user is kept to a minimum.
  • the compressed air generator comprises at least a first compressor stage 02 and a second compressor stage 03.
  • the air precompressed in the first compressor stage 01 is fed at a temperature of, for example, 200°C to an intermediate cooler 04 for cooling and leaves it at around 50°C, in order to then be second compressor stage 03 to be further compressed.
  • the finally compressed compressed air leaves the second compressor stage 03 at a temperature of around 200°C and is then fed to an aftercooler 05 for cooling again, so that the compressed air is finally delivered to external units at around 50°C.
  • a main cooler 07 supplies a cooling medium, preferably cooling water, on its cold side at a temperature of 45° C., for example.
  • the cooling water A is supplied in parallel to the inflow of the intercooler 04, the aftercooler 05 and an assembly cooler 08.
  • the cooling water flows through the intercooler 04 and the aftercooler 05 to absorb the heat the compressed air and is returned to the hot side of the main cooler 07 at a high temperature of, for example, 90°C.
  • the cooling water first flows through a heat exchanger 09, which is 1 but is deactivated, so that the cooling water temperature at the entrance and exit of the heat exchanger 09 is almost unchanged.
  • the heat is given off at the main cooler 07 in order to bring the cooling water down to a low temperature again.
  • the cooling is supported, for example, by a fan 11, which emits heated exhaust air at a temperature of 40° C., for example.
  • a special feature of the cooling arrangement is that the cooling water, after flowing through the component cooler 08, is not routed parallel to the cooling water of the intermediate cooler and the aftercooler directly to the main cooler 07 or to the upstream heat exchanger 09.
  • the cooling water outlet of the component cooler is connected to a feed inlet 12 on the intermediate cooler 04 and on the aftercooler 05.
  • the feed input 12 can also only be provided on one of the two coolers 04, 05 and its position is selected such that an intermediate temperature of 57° C., for example, prevails there in the cooler 04, 05.
  • the intermediate temperature should essentially correspond to the outlet temperature of the cooling water B, which is supplied by the assembly cooler 08.
  • the cooling water B is thus mixed back into the cooling water A in the intermediate cooler 04 and/or in the aftercooler 05 and is further heated there to the high temperature.
  • FIG. 2 shows the simplified block diagram of the compressed air generator 01 or the compressor system in a changed operating state, namely with activated heat recovery on the heat exchanger 09 Drop in temperature of the heated cooling water from, for example, 90°C to 50°C.
  • the extracted heat is available for other applications, for example for heating purposes.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Compressor (AREA)

Description

Die Erfindung betrifft eine Kühlungsanordnung für einen mindestens zweistufigen Drucklufterzeuger. Ein solcher Drucklufterzeuger, auch Kompressor genannt, umfasst einen flüssigkeitsgekühlten Zwischenkühler, der zwischen einer ersten und einer zweiten Verdichterstufe angeordnet ist, um die von der ersten Verdichterstufe abgegebene vorverdichtete Luft zu kühlen, bevor diese in die zweite Verdichterstufe eintritt, sowie einen flüssigkeitsgekühlten Nachkühler, der nach der zweiten Verdichterstufe angeordnet ist, um die von dieser verdichtete Luft zu kühlen. Weiterhin ist ein flüssigkeitsgekühlter Baugruppenkühler vorgesehen, der Wärme von weiteren Baugruppen des Drucklufterzeugers aufnimmt, um beispielsweise Leistungselektronik oder Antriebe und Getriebe der Verdichterstufen zu kühlen. Ein Kühlmittelkreislauf verläuft über einen Hauptkühler, dessen Kaltseite dem jeweiligen Kühlmitteleingang des Zwischenkühlers, des Nachkühlers und des Baugruppenkühlers ein Kühlmittel zuführt, und dessen Heißseite das am Kühlmittelausgang des Zwischenkühlers und des Nachkühlers austretende erwärmte Kühlmittel empfängt.The invention relates to a cooling arrangement for an at least two-stage compressed air generator. Such a compressed air generator, also called a compressor, comprises a liquid-cooled intercooler, which is arranged between a first and a second compressor stage, in order to cool the pre-compressed air discharged from the first compressor stage before it enters the second compressor stage, and a liquid-cooled aftercooler, which is arranged after the second compressor stage in order to cool the compressed air of this. Furthermore, a liquid-cooled assembly cooler is provided, which absorbs heat from other assemblies of the compressed air generator, for example to cool power electronics or drives and gears of the compressor stages. A coolant circuit runs through a main cooler, the cold side of which feeds a coolant to the respective coolant inlet of the intercooler, the aftercooler and the assembly cooler, and the hot side of which receives the heated coolant exiting at the coolant outlet of the intercooler and the aftercooler.

Die Erfindung betrifft weiterhin ein Verfahren zur Kühlung eines mindestens zweistufigen Drucklufterzeugers.The invention also relates to a method for cooling an at least two-stage compressed air generator.

Zur Kompression von gasförmigen Medien, insbesondere zur Erzeugung von Druckluft sind unterschiedlichste Bauformen von Kompressoren bekannt. Beispielsweise zeigt die DE 601 17 821 T2 einen Mehrstufen-Schraubenverdichter mit zwei oder mehr Verdichterstufen, wobei jede Verdichterstufe ein Paar von Rotoren zum Verdichten eines Gases umfasst. Weiterhin sind zwei oder mehr Antriebsmittel mit veränderbarer Geschwindigkeit vorgesehen, wobei jedes Antriebsmittel eine jeweilige Verdichterstufe antreibt.A wide variety of designs of compressors are known for compressing gaseous media, in particular for generating compressed air. For example, the DE 601 17 821 T2 a multi-stage screw compressor having two or more compression stages, each compression stage including a pair of rotors for compressing a gas. Furthermore two or more variable speed drive means are provided, each drive means driving a respective compressor stage.

Die EP 2 886 862 A1 beschreibt einen Kompressor mit einem Motor, einer Antriebswelle, einem mit dieser verbundenen Kurbeltrieb, mindestens einer Drucklufterzeugungseinrichtung, einem Kurbelgehäuse und einem Druckluftspeicherbehälter. Die Kühlung sämtlicher Komponenten erfolgt mit Hilfe eines von einem Lüfterrad erzeugten Kühlluftstroms.The EP 2 886 862 A1 describes a compressor with a motor, a drive shaft, a crank mechanism connected thereto, at least one compressed air generating device, a crankcase and a compressed air storage tank. All components are cooled with the aid of a flow of cooling air generated by a fan wheel.

Aus der DE 10 2017 107 602 B3 ist eine Kompressoranlage bekannt mit einem Anlagen-Gehäuse, in welchem mehrere Wärme erzeugende Anlagenkomponenten angeordnet sind. Dazu gehört ein Doppel-Schraubenverdichter mit zwei Verdichterstufen, die der Verdichtung eines gasförmigen Mediums dienen, insbesondere der Erzeugung von Druckluft. Das Anlagen-Gehäuse enthält weiterhin einen Luft-Wasser-Kühler, ein Gebläse, welches einen Kühlluftstrom erzeugt, sowie Luftleitelemente, welche die von den Anlagenkomponenten erwärmte Luft zu dem Luft-Wasser-Kühler führen.From the DE 10 2017 107 602 B3 a compressor system is known with a system housing in which several heat-generating system components are arranged. This includes a double screw compressor with two compression stages, which serve to compress a gaseous medium, in particular to generate compressed air. The system housing also contains an air-to-water cooler, a fan that generates a flow of cooling air, and air guiding elements that guide the air that has been heated by the system components to the air-to-water cooler.

Die EP 2 529 116 B1 beschreibt ein Verfahren zur Rückgewinnung von Energie bei der Verdichtung eines Gases durch einen Verdichter mit zwei oder mehr Druckstufen. Stromabwärts vom Verdichter ist ein Wärmetauscher mit einem Primär- und einem Sekundärteil vorgesehen. Durch den Primärteil wird das aus einer Druckstufe verdichtete Gas geleitet; durch den Sekundärteil wird ein Kühlmittel geleitet.The EP 2 529 116 B1 describes a method for recovering energy from the compression of a gas by a compressor with two or more pressure stages. A heat exchanger with a primary part and a secondary part is provided downstream of the compressor. The gas compressed from a pressure stage is routed through the primary part; a coolant is conducted through the secondary part.

Die WO 2015/172206 A9 zeigt einen Kompressor mit wenigstens zwei in Reihe liegenden Kompressionsstufen sowie wenigstens zwei Kühlern, nämlich einem Zwischenkühler zwischen den Kompressionsstufen und einem Nachkühler stromabwärts nach der letzten Kompressionsstufe. Wenigstens zwei der Kühler sind als aufgeteilte Kühler gestaltet, sodass die vom Kühlmittel durchströmte Sekundärseite in zwei Stufen unterteilt ist, um das auf der Primärseite durchströmende Gas in einer heißen und einer kühlen Stufe zu kühlen. Die beiden Stufen der Sekundärseite sind in unterschiedlichen Kühlkreisen zusammengeschaltet. Beispielsweise sind jeweils die ersten Stufen der mehreren Kühler sowie jeweils die zweiten Stufen in Reihe geschaltet.The WO 2015/172206 A9 shows a compressor with at least two compression stages in series and at least two coolers, namely an intercooler between the compression stages and an aftercooler downstream after the last compression stage. At least two of the coolers are designed as split coolers so that the secondary side through which the coolant flows is divided into two stages to cool the gas flowing through on the primary side in a hot stage and a cool stage. The two stages of the secondary side are interconnected in different cooling circuits. For example, each of the first stages of the plurality of coolers and each of the second stages are connected in series.

Die DE 31 34 844 A1 beschreibt ein Verfahren zur energetischen Optimierung eines Verdichtungsprozesses, insbesondere für die mehrstufige Verdichtung mit Kreisel- und Kolbenverdichtern. Dafür ist eine Wärmepumpe ist in eine Verdichteranlage integriert. Vorzugsweise werden in die das erwärmte Kühlwasser führenden Rohrleitungen der Kühlstufen mindestens ein Verdampfer der Wärmepumpe eingebunden.The DE 31 34 844 A1 describes a method for energetic optimization of a compression process, in particular for multi-stage compression with centrifugal and piston compressors. A heat pump is integrated into a compressor system for this purpose. At least one evaporator of the heat pump is preferably integrated into the pipelines of the cooling stages carrying the heated cooling water.

In der US 2018/0258952 A1 ist ein Kompressormodul beschrieben, welches einen Kompressor mit einem Gehäuse mit integriertem Kompressorkühler umfasst. Gemäße einer Ausführungsform können zwei solcher Module miteinander kombiniert werden, sodass ein Niederdruck-Kompressormodul und ein Hochdruck-Kompressormodul in Reihe geschaltet sind. Jedes der beiden Kompressormodule besitzt einen flüssigkeitsgekühlten Kühler, der die komprimierte Luft am Ausgang des Moduls kühlt. Weiterhin sind eine Motorkühler und ein Bauelementkühler vorgesehen, deren Kühlmittelkreislauf mit denjenigen der Kompressorkühler verbunden ist.In the US 2018/0258952 A1 describes a compressor module which includes a compressor with a housing with an integrated compressor cooler. According to one embodiment, two such modules can be combined with one another, so that a low-pressure compressor module and a high-pressure compressor module are connected in series. Each of the two compressor modules has a liquid-cooled cooler that cools the compressed air at the module outlet. Furthermore, an engine cooler and a component cooler are provided, the coolant circuit of which is connected to that of the compressor cooler.

In der US 2011 0 000 227 A1 wird ein Kompressor beschrieben, der zur Verbesserung der Effizienz der Abgaswärmerückgewinnung zum Umwälzen des Arbeitsfluids eines Rankine-Kreislauf einen Wärmetauscher zum Kühlen eines Gases, Kühlmittels, Wassers oder Öls, das durch den Kompressor während des Kompressorbetriebs durch Wärmeaustausch mit dem Arbeitsfluid erhitzt wird, aufweist. Der Rankine-Kreislauf wird durch den Wärmetauscher, einen Expander, einen Kondensator und einer Umwälzpumpe, die das Arbeitsfluid durch den Kreislauf zirkulieren lässt, realisiert.In the U.S. 2011 0 000 227 A1 describes a compressor for improving the efficiency of exhaust heat recovery for circulating the working fluid of a Rankine cycle, a heat exchanger for cooling a gas, refrigerant, water or oil heated by the compressor during compressor operation by heat exchange with the working fluid. The Rankine cycle is realized by the heat exchanger, an expander, a condenser and a circulating pump that circulates the working fluid through the cycle.

Generell ergibt sich bei derartigen Kompressoranlagen immer der Bedarf, mehr oder weniger große Wärmemengen abzuführen, um eine Überhitzung einzelner Komponenten bzw. der Gesamtanlage zu vermeiden. Die Gesamtanlage wird bislang regelmäßig durch Kühlluft gekühlt, wobei erwärmte Abluft zumeist ungenutzt in die Umwelt abgegeben wird. Die Wärme ist dann entweder verloren oder kann nur ineffizient aus der Abluft rückgewonnen werden. Einige Anlagen enthalten zusätzlich einen Wärmetauscher, dessen sekundäres Wärmetransportmedium Wärme aus einem primären Kühlkreislauf des Kompressors aufnimmt und abtransportiert. Die abgeführte Wärme kann dann von einem externen Verbraucher genutzt erden.In general, with such compressor systems, there is always a need to dissipate more or less large amounts of heat in order to avoid overheating of individual components or the entire system. Up until now, the entire system has been regularly cooled by cooling air, with the heated exhaust air usually being released into the environment unused. The heat is then either lost or can only be recovered inefficiently from the exhaust air. Some systems also contain a heat exchanger whose secondary heat transport medium absorbs heat from a primary cooling circuit of the compressor and transports it away. The dissipated heat can then be used by an external consumer.

Eine Aufgabe der vorliegenden Erfindung besteht ausgehend vom Stand der Technik darin, einerseits eine effiziente Kühlung solcher Drucklufterzeuger (Kompressoranlagen) sicherzustellen, unter Verringerung des gerätetechnischen Aufwands, andererseits aber auch eine effizientere Wärmerückgewinnung in Bezug auf den gesamten Drucklufterzeuger zu gestatten.Based on the prior art, one object of the present invention is, on the one hand, to ensure efficient cooling of such compressed air generators (compressor systems) while reducing the outlay on equipment, but on the other hand to allow more efficient heat recovery in relation to the entire compressed air generator.

Diese Aufgabe wird durch eine Kühlungsanordnung für einen mindestens zweistufigen Drucklufterzeuger gemäß dem beigefügten Anspruch 1 gelöst. Bevorzugte Ausführungsformen der Kühlungsanordnung sind in den Unteransprüchen 2 bis 7 genannt.This object is achieved by a cooling arrangement for an at least two-stage compressed air generator according to appended claim 1. Preferred embodiments of the cooling arrangement are specified in subclaims 2 to 7.

Weiterhin wird die Aufgabe durch ein Verfahren zur Kühlung eines mindestens zweistufigen Drucklufterzeugers gemäß dem beigefügten Anspruch 8 gelöst. Vorteilhafte Ausführungen des Verfahrens sind in den Unteransprüchen 9 und 10 genannt.Furthermore, the object is achieved by a method for cooling an at least two-stage compressed air generator according to appended claim 8. Advantageous embodiments of the method are specified in dependent claims 9 and 10.

Die erfindungsgemäße Kühlungsanordnung ist zur Kühlung eines Drucklufterzeugers, vorzugsweise in der Art einer Kompressoranlage, mit mindestens zwei Verdichterstufen geeignet. Die Kühlungsanordnung umfasst mindestens einen flüssigkeitsgekühlten Zwischenkühler, der zwischen einer ersten und einer zweiten Verdichterstufe angeordnet ist, um die von der ersten Verdichterstufe abgegebene vorverdichtete Luft zu kühlen, bevor diese in die zweite Verdichterstufe eintritt. Ein flüssigkeitsgekühlter Nachkühler ist nach der zweiten bzw. letzten Verdichterstufe angeordnet, um die weiter verdichtete Luft zu kühlen. Im einfachsten Fall wird die erzeugte Druckluft nach Durchströmen des Nachkühlers an externe Einheiten bereitgestellt. In Abwandlungen kann der Drucklufterzeuger auch mehr als zwei Verdichterstufen und entsprechend zusätzliche Zwischenkühler aufweisen.The cooling arrangement according to the invention is suitable for cooling a compressed air generator, preferably in the form of a compressor system, with at least two compressor stages. The cooling arrangement includes at least one liquid-cooled intercooler arranged between a first and a second compressor stage for cooling the supercharged air discharged from the first compressor stage before it enters the second compressor stage. A liquid-cooled aftercooler is located after the second or final compressor stage to cool the further compressed air. In the simplest case, the compressed air generated is made available to external units after it has flowed through the aftercooler. In modifications, the compressed air generator can also have more than two compressor stages and correspondingly additional intermediate coolers.

Weiterhin umfasst die Kühlungsanordnung einen flüssigkeitsgekühlten Baugruppenkühler, der Wärme von weiteren Baugruppen des Drucklufterzeugers aufnimmt und an das Kühlmittel abgibt. Der Baugruppenkühler ist, wie die anderen Kühler im Gehäuse des Drucklufterzeugers angeordnet und z. B. als Lamellenkühler, Kühlblech, Heatpipe oder dergleichen ausgebildet. Der Baugruppenkühler kann aus mehreren einzelnen Kühlern zusammengesetzt sein und dient der Wärmeabfuhr insbesondere von den Antrieben der Verdichterstufen sowie der Leistungselektronik, die für die Steuerung des Drucklufterzeugers benötigt wird.Furthermore, the cooling arrangement includes a liquid-cooled assembly cooler, which absorbs heat from other assemblies of the compressed air generator and transfers it to the coolant. Like the other coolers, the module cooler is arranged in the housing of the compressed air generator and z. B. designed as a finned cooler, heat sink, heat pipe or the like. The component cooler can be made up of several individual coolers and is used to dissipate heat, in particular from the drives of the compressor stages and the power electronics that are required to control the compressed air generator.

Die Kühlungsanordnung besitzt einen Kühlmittelkreislauf, der einen Hauptkühler umfasst, um die vom Kühlmittel in den anderen Kühlern aufgenommene Wärme aus dem Drucklufterzeuger abzuführen. Die Kaltseite des Hauptkühlers liefert gekühltes Kühlmittel mit einer Niedrigtemperatur direkt an den jeweiligen Kühlmitteleingang des Zwischenkühlers, des Nachkühlers und des Baugruppenkühlers. Die Kühlmitteleingänge von Zwischenkühler(n), Nachkühler und Baugruppenkühler(n) sind parallel geschaltet, sodass ihnen das Kühlmittel mit derselben Niedrigtemperatur zugeführt wird. Die Heißseite des Hauptkühlers empfängt das erhitzte Kühlmittel unmittelbar vom jeweiligen Kühlmittelausgang des Zwischenkühlers (bzw. der mehreren Zwischenkühler) und des Nachkühlers oder mittelbar von diesen, wenn ein Wärmetauscher zur Wärmerückgewinnung zwischengeschaltet ist, wie dies weiter unten beschrieben wird. Die Kühlmittelausgänge von Zwischenkühler(n) und Nachkühler sind parallel geschaltet und liefern das erhitzte Kühlmittel mit einer Hochtemperatur zum Hauptkühler, ggf. über den Wärmetauscher.The cooling arrangement has a coolant circuit which includes a main cooler in order to dissipate the heat absorbed by the coolant in the other coolers from the compressed air generator. The cold side of the main cooler delivers chilled coolant at a low temperature directly to the respective coolant inlets of the intercooler, the aftercooler and the assembly cooler. The coolant inlets of the intercooler(s), aftercooler and assembly cooler(s) are connected in parallel so that the coolant is supplied to them at the same low temperature. The hot end of the main cooler receives the heated coolant directly from the respective coolant outlet of the intercooler (or multiple intercoolers) and the aftercooler, or indirectly from them if a heat exchanger for heat recovery is interposed, as will be described further below. The coolant outlets from the intercooler(s) and aftercooler are connected in parallel and supply the heated coolant at a high temperature to the main cooler, possibly via the heat exchanger.

Für die Erfindung ist wesentlich, dass der Kühlmittelausgang des Baugruppenkühlers nicht parallel mit dem Kühlmittelausgang des Zwischenkühlers oder Nachkühlers geschaltet ist. Dadurch wird vermieden, dass das Kühlmittel von der Hochtemperatur, die am Ausgang von Zwischen- und Nachkühler anliegt, durch die Beimischung aus dem Baugruppenkühler abgekühlt wird, denn der Baugruppenkühler liefert regelmäßig niedrigere Temperaturen des Kühlmittels, aufgrund der geringeren abzuführenden Wärmemenge. Stattdessen wird das Kühlmittel des Baugruppenkühlers einem Zuspeiseeingang des Zwischenkühlers und/oder des Nachkühlers zugeführt, wobei der Zuspeiseeingang zwischen dem Kühlmitteleingang und Kühlmittelausgang angeordnet ist, an einer Position, an welcher die Zwischentemperatur des Kühlmittels im Zwischenkühler bzw. Nachkühler der Austrittstemperatur des Kühlmittels am Baugruppenkühler ±20% entspricht. Vorzugsweise weicht die Temperatur des vom Baugruppenkühler zugemischten Kühlmittels um weniger als ±10%, insbesondere um weniger als ±3% von der Temperatur am Punkt der Beimischung im Zwischen- oder Nachkühler ab.It is essential for the invention that the coolant outlet of the component cooler is not connected in parallel with the coolant outlet of the intercooler or aftercooler. This prevents the coolant from being cooled down from the high temperature at the outlet of the intercooler and aftercooler by the admixture from the subassembly cooler, because the subassembly cooler regularly delivers lower temperatures of the coolant due to the lower amount of heat to be dissipated. Instead, the coolant of the assembly cooler is fed to a feed inlet of the intercooler and/or the aftercooler, with the feed inlet being arranged between the coolant inlet and coolant outlet, at a position at which the intermediate temperature of the coolant in the intercooler or aftercooler reaches the outlet temperature of the coolant at the assembly cooler corresponds to ±20%. The temperature of the coolant mixed in by the assembly cooler preferably deviates by less than ±10%, in particular by less than ±3%, from the temperature at the point of admixture in the intercooler or aftercooler.

Dasselbe Kühlmittel (vorzugsweise Wasser) wird somit für den Zwischenkühler, den Nachkühler und den Baugruppenkühler eingesetzt. Damit kann nicht nur Wärme aus der verdichteten Druckluft sondern auch die Wärme von Baugruppen, z. B. Elektromotoren, Umrichtern, Verdichterstufen, Getriebeeinheiten usw. im Kühlmittel angereichert und von diesem abtransportiert werden. Der größte Teil der Abwärme des gesamten Drucklufterzeugers steht damit auch für eine Wärmerückgewinnung zur Verfügung.The same coolant (preferably water) is thus used for the intercooler, the aftercooler and the assembly cooler. This means that not only heat can be extracted from the compressed air, but also the heat from assemblies, e.g. B. electric motors, converters, compressor stages, gear units, etc. are enriched in the coolant and transported away by it. Most of the waste heat from the entire compressed air generator is therefore also available for heat recovery.

Ein weiterer Vorteil der Erfindung besteht darin, dass der Hauptkühler deutlich kleiner ausgeführt werden kann, was zu einer erheblichen Verringerung der Baugröße des Kühlkreislaufes und damit der Gesamtkosten des Drucklufterzeugers führt. Aufgrund der beschriebenen gezielten Zuspeisung des vom Baugruppenkühler mit der Zwischentemperatur gelieferten Kühlmittels in den Zwischenkühler und/oder Nachkühler, kann die Hochtemperatur, die am Ausgang des Zwischenkühlers und des Nachkühlers anliegt, auf einem hohen Niveau gehalten werden, vorzugsweise im Bereich von 90°C. Dies führt zu einer großen Temperaturdifferenz am Hauptkühler, sodass dessen Kühlfläche kleiner gehalten werden kann, als wenn die Eingangstemperatur am Hauptkühler geringer ausfällt. Die erforderliche Kühlfläche ist proportional zur Temperaturdifferenz zwischen Eingangstemperatur (Hochtemperatur) und gewünschter Ausgangstemperatur (Niedrigtemperatur).Another advantage of the invention is that the main cooler can be made much smaller, which leads to a significant reduction in the size of the cooling circuit and thus the overall costs of the compressed air generator. Due to the described targeted feeding of the coolant supplied by the assembly cooler at the intermediate temperature into the intercooler and/or aftercooler, the high temperature present at the outlet of the intercooler and the aftercooler can be kept at a high level, preferably in the range of 90°C. This leads to a large temperature difference at the main cooler, so that its cooling surface can be kept smaller than when the inlet temperature at the main cooler is lower. The required cooling area is proportional to the temperature difference between the inlet temperature (high temperature) and the desired outlet temperature (low temperature).

Gemäß einer vorteilhaften Ausführungsform wird das vom Baugruppenkühler gelieferte Kühlmittel sowohl dem Zwischenkühler als auch dem Nachkühler über den jeweiligen Zuspeiseeingang zugeführt.According to an advantageous embodiment, the coolant supplied by the component cooler is fed both to the intermediate cooler and to the aftercooler via the respective feed inlet.

Gemäß einer besonders bevorzugten Ausführungsform der Kühlungsanordnung ist ein Wärmetauscher im Kühlmittelkreislauf zwischen dem jeweiligen Kühlmittelausgang des Zwischenkühlers und des Nachkühlers sowie dem Kühlmitteleingang des Hauptkühlers eingeschaltet. Dem Wärmetauscher steht damit die gesamte dem Kühlmittel zugeführte Wärme für eine Übergabe an ein Wärmeträgermedium zur Verfügung.According to a particularly preferred embodiment of the cooling arrangement, a heat exchanger is connected in the coolant circuit between the respective coolant outlet of the intercooler and the aftercooler and the coolant inlet of the main cooler. The entire heat supplied to the coolant is thus available to the heat exchanger for transfer to a heat transfer medium.

Bevorzugt ist der Hauptkühler ein Wasser-Luft-Kühler oder ein Wasser-Wasser-Kühler oder ein Kombinationskühler, der Wasser und Luft wahlweise als kühlendes Medium nutzt. Damit steht es dem Nutzer des Drucklufterzeugers frei, ob er die Hauptkühlung mithilfe einer gebläseunterstützten Abluftkühlung oder durch Anschluss an ein externes Flüssigkühlmedium realisiert.The main cooler is preferably a water-air cooler or a water-water cooler or a combination cooler that uses water and air optionally as the cooling medium. This means that the user of the compressed air generator is free to implement the main cooling using fan-assisted exhaust air cooling or by connecting to an external liquid cooling medium.

Es ist vorteilhaft, wenn der Zwischenkühler und/oder der Nachkühler mehrere Zuspeiseeingänge besitzen, denen das Kühlmittel vom Kühlmittelausgang des Baugruppenkühlers wahlweise zuführbar ist. Insbesondere ist zwischen dem Kühlmittelausgang des Baugruppenkühlers und den Zuspeiseeingängen eine Verteilereinheit angeordnet, die temperaturgesteuert denjenigen Zuspeiseeingang versorgt, an welchem die Zwischentemperatur des Kühlmittels im Zwischenkühler bzw. Nachkühler der Austrittstemperatur des Kühlmittels am Baugruppenkühler am nächsten liegt.It is advantageous if the intercooler and/or the aftercooler have a plurality of feed inlets to which the coolant can be selectively fed from the coolant outlet of the subassembly cooler. In particular, a distributor unit is arranged between the coolant outlet of the component cooler and the feed inputs, which temperature-controlled supplies that feed input at which the intermediate temperature of the coolant in the intercooler or aftercooler is closest to the outlet temperature of the coolant on the component cooler.

Zweckmäßigerweise sind der Zwischenkühler, der Nachkühler, der Baugruppenkühler, der Wärmetauscher, die erste und zweite Verdichterstufe sowie eine elektronische Steuereinheit innerhalb eines gemeinsamen Gerätegehäuses angeordnet. Die Kühlungsanordnung ist damit integraler Bestandteil des Drucklufterzeugers, sodass sich der Installationsaufwand beim Nutzer auf ein Minimum beschränkt.Conveniently, the intercooler, the aftercooler, the assembly cooler, the heat exchanger, the first and second Airend and an electronic control unit arranged within a common device housing. The cooling arrangement is thus an integral part of the compressed air generator, so that the installation effort for the user is kept to a minimum.

Das erfindungsgemäße Verfahren zur Kühlung eines mindestens zweistufigen Drucklufterzeugers umfasst folgende Schritte:

  • Führen eines Kühlmediums in einem Kühlmittelkreislauf durch einen Hauptkühler und durch einen zum Hauptkühler in Reihe geschalteten ersten flüssigkeitsgekühlten Zwischenkühler, der damit von einer ersten Verdichterstufe vorverdichte Luft kühlt;
  • Führen des Kühlmediums in dem Kühlmittelkreislauf durch einen zum Hauptkühler ebenfalls in Reihe und zum Zwischenkühler parallel geschalteten Nachkühler, der damit von einer zweiten Verdichterstufe nachverdichtete Luft kühlt;
  • Zuführen des im Hauptkühler gekühlten Kühlmediums zu einem flüssigkeitsgekühlten Baugruppenkühler, der Wärme von weiteren Baugruppen des Drucklufterzeugers aufnimmt;
  • Zuspeisen des vom Baugruppenkühler abgegebenen, erhitzten Kühlmediums über einen Zuspeiseeingang in den Zwischenkühler und/oder in den Nachkühler, wobei die Zuspeisung an einer Position im Zwischenkühler bzw. im Nachkühler erfolgt, an welcher die Zwischentemperatur des Kühlmittels im Zwischenkühler bzw. Nachkühler der Austrittstemperatur des Kühlmittels am Baugruppenkühler ±20% entspricht, vorzugsweise diese beiden Temperaturen im Wesentlichen gleich sind.
The method according to the invention for cooling an at least two-stage compressed air generator comprises the following steps:
  • Conducting a cooling medium in a coolant circuit through a main cooler and through a first liquid-cooled intercooler which is connected in series with the main cooler and which uses it to cool pre-compressed air from a first compressor stage;
  • Conducting the cooling medium in the coolant circuit through an aftercooler, which is also connected in series with the main cooler and in parallel with the intermediate cooler, and which uses it to cool the air that has been post-compressed by a second compressor stage;
  • Supplying the cooling medium cooled in the main cooler to a liquid-cooled assembly cooler, which absorbs heat from other assemblies of the compressed air generator;
  • Feeding in the heated cooling medium discharged from the assembly cooler via a feed inlet into the intercooler and/or into the aftercooler, with the feed taking place at a position in the intercooler or in the aftercooler at which the intermediate temperature of the coolant in the intercooler or aftercooler is equal to the outlet temperature of the coolant corresponds to ±20% at the assembly cooler, these two temperatures are preferably essentially the same.

Weitere Vorteile und Einzelheiten der Erfindung ergeben sich aus der nachfolgenden Beschreibung einer bevorzugten Ausführungsform unter Bezugnahme auf die Zeichnung. Es zeigen:

Fig. 1
ein Blockschaltbild einer erfindungsgemäßen Kühlungsanordnung mit deaktivierter Wärmerückgewinnung;
Fig. 2
ein Blockschaltbild der Kühlungsanordnung mit aktivierter Wärmerückgewinnung.
Further advantages and details of the invention result from the following description of a preferred embodiment with reference to the drawing. Show it:
1
a block diagram of a cooling arrangement according to the invention with deactivated heat recovery;
2
a block diagram of the cooling arrangement with activated heat recovery.

Fig. 1 zeigt das vereinfachte Blockschaltbild eines Drucklufterzeugers 01 bzw. einer Kompressoranlage. Das Blockschaltbild umfasst vor allem die wesentlichen Elemente einer Kühlungsanordnung und vernachlässigt andere Einheiten des Drucklufterzeugers. Der Drucklufterzeuger umfasst mindestens eine erste Verdichterstufe 02 und eine zweite Verdichterstufe 03. Die in der ersten Verdichterstufe 01 vorverdichtete Luft wird mit einer Temperatur von beispielsweise 200°C einem Zwischenkühler 04 zur Kühlung zugeführt und verlässt diesen mit etwa 50°C, um dann von der zweiten Verdichterstufe 03 weiter verdichtet zu werden. Die endverdichtete Druckluft verlässt die zweite Verdichterstufe 03 mit einer Temperatur von etwa 200°C und wird dann einem Nachkühler 05 zu erneuten Kühlung zugeführt, sodass die Druckluft schließlich mit etwa 50°C an externe Einheiten geliefert wird. Zur Wärmeabfuhr liefert ein Hauptkühler 07 ein Kühlmedium, vorzugsweise Kühlwasser an seiner Kaltseite mit einer Temperatur von beispielsweise 45°C. Das Kühlwasser A wird mit dieser Niedrigtemperatur parallel an den Zufluss des Zwischenkühlers 04, des Nachkühlers 05 und eines Baugruppenkühlers 08 geliefert. Das Kühlwasser durchströmt den Zwischenkühler 04 und den Nachkühler 05 zur Aufnahme der Wärme der Druckluft und wird mit einer Hochtemperatur von beispielsweise 90°C an die Heißseite des Hauptkühlers 07 zurück geliefert. Zuvor durchströmt das Kühlwasser bei der dargestellten Bauform noch einen Wärmetauscher 09, der in Fig. 1 aber deaktiviert ist, sodass die Kühlwassertemperatur am Eingang und Ausgang des Wärmetauschers 09 nahezu unverändert ist. Am Hauptkühler 07 wird die Wärme abgegeben, um das Kühlwasser wieder auf Niedrigtemperatur zu bringen. Die Kühlung wird beispielsweise unterstützt durch ein Gebläse 11, welches eine erwärmte Abluft mit einer Temperatur von beispielsweise 40°C abgibt. 1 shows the simplified block diagram of a compressed air generator 01 or a compressor system. The block diagram primarily includes the essential elements of a cooling arrangement and neglects other units of the compressed air generator. The compressed air generator comprises at least a first compressor stage 02 and a second compressor stage 03. The air precompressed in the first compressor stage 01 is fed at a temperature of, for example, 200°C to an intermediate cooler 04 for cooling and leaves it at around 50°C, in order to then be second compressor stage 03 to be further compressed. The finally compressed compressed air leaves the second compressor stage 03 at a temperature of around 200°C and is then fed to an aftercooler 05 for cooling again, so that the compressed air is finally delivered to external units at around 50°C. To dissipate heat, a main cooler 07 supplies a cooling medium, preferably cooling water, on its cold side at a temperature of 45° C., for example. At this low temperature, the cooling water A is supplied in parallel to the inflow of the intercooler 04, the aftercooler 05 and an assembly cooler 08. The cooling water flows through the intercooler 04 and the aftercooler 05 to absorb the heat the compressed air and is returned to the hot side of the main cooler 07 at a high temperature of, for example, 90°C. In the design shown, the cooling water first flows through a heat exchanger 09, which is 1 but is deactivated, so that the cooling water temperature at the entrance and exit of the heat exchanger 09 is almost unchanged. The heat is given off at the main cooler 07 in order to bring the cooling water down to a low temperature again. The cooling is supported, for example, by a fan 11, which emits heated exhaust air at a temperature of 40° C., for example.

Eine Besonderheit der Kühlungsanordnung besteht darin, dass das Kühlwasser nach Durchströmen des Baugruppenkühlers 08 nicht parallel zum Kühlwasser des Zwischenkühlers und des Nachkühlers direkt zum Hauptkühler 07 bzw. zum vorgeschalteten Wärmetauscher 09 geführt wird. Stattdessen ist der Kühlwasserauslass des Baugruppenkühlers jeweils an einen Zuspeiseeingang 12 am Zwischenkühler 04 und am Nachkühler 05 angeschlossen. Der Zuspeiseeingang 12 kann alternativ auch nur an einem der beiden Kühler 04, 05 vorgesehen sein und ist in seiner Position so gewählt, dass dort im Kühler 04, 05 eine Zwischentemperatur von beispielsweise 57°C herrscht. Die Zwischentemperatur soll im Wesentlichen der Ausgangstemperatur des Kühlwassers B, welches vom Baugruppenkühler 08 geliefert wird, entsprechen. Das Kühlwasser B wird somit dem Kühlwasser A im Zwischenkühler 04 und/oder im Nachkühler 05 wieder beigemischt und dort weiter auf die Hochtemperatur erwärmt.A special feature of the cooling arrangement is that the cooling water, after flowing through the component cooler 08, is not routed parallel to the cooling water of the intermediate cooler and the aftercooler directly to the main cooler 07 or to the upstream heat exchanger 09. Instead, the cooling water outlet of the component cooler is connected to a feed inlet 12 on the intermediate cooler 04 and on the aftercooler 05. Alternatively, the feed input 12 can also only be provided on one of the two coolers 04, 05 and its position is selected such that an intermediate temperature of 57° C., for example, prevails there in the cooler 04, 05. The intermediate temperature should essentially correspond to the outlet temperature of the cooling water B, which is supplied by the assembly cooler 08. The cooling water B is thus mixed back into the cooling water A in the intermediate cooler 04 and/or in the aftercooler 05 and is further heated there to the high temperature.

Fig. 2 zeigt das vereinfachte Blockschaltbild des Drucklufterzeugers 01 bzw. der Kompressoranlage in einem veränderten Betriebszustand, nämlich mit aktivierter Wärmerückgewinnung am Wärmetauscher 09. Damit kommt es am Wärmetauscher 09 zu einem Temperaturabfall des erhitzten Kühlwassers von beispielsweise 90°C auf 50°C. Die entnommene Wärme steht für andere Anwendungen zur Verfügung, beispielsweise zu Heizzwecken. 2 shows the simplified block diagram of the compressed air generator 01 or the compressor system in a changed operating state, namely with activated heat recovery on the heat exchanger 09 Drop in temperature of the heated cooling water from, for example, 90°C to 50°C. The extracted heat is available for other applications, for example for heating purposes.

BezugszeichenlisteReference List

0101
Drucklufterzeuger / KompressoranlageCompressed air generator / compressor system
0202
erste Verdichterstufefirst compressor stage
0303
zweite Verdichterstufesecond compressor stage
0404
Zwischenkühlerintercooler
0505
Nachkühleraftercooler
0606
--
0707
Hauptkühlermain cooler
0808
Baugruppenkühlerassembly cooler
0909
Wärmetauscherheat exchanger
1010
--
1111
Gebläsefan
1212
Zuspeiseeingangfeed input

Claims (10)

  1. A cooling arrangement for an at least two-stage compressed air generator (01), comprising
    - a liquid-cooled intercooler (04), which is arranged between a first and a second compressor stage (02, 03), in order to cool the precompressed air discharged from the first compressor stage (02) before it enters the second compressor stage (03);
    - a liquid-cooled aftercooler (05), which is arranged after the second compressor stage (03), in order to cool the air compressed by said second compressor stage (03);
    - a liquid-cooled subassembly cooler (08), which absorbs heat from further subassemblies of the compressed air generator (01);
    characterised in that the cooling arrangement comprises a coolant circuit, which has a main cooler (07), the cold side of which feeds a cooled coolant having a low temperature to the respective coolant inlet of the intercooler (04), of the aftercooler (05) and of the subassembly cooler (08) in parallel, and the hot side of which receives the heated coolant having a high temperature which exits in parallel at the respective coolant outlet of the intercooler (04) and of the aftercooler (05);
    wherein the coolant outlet of the subassembly cooler (08) is connected to a feed inlet (12) of the intercooler (04) and/or the aftercooler (05), wherein the feed inlet (12) is arranged between the coolant inlet and the coolant outlet, at a point at which the intermediate temperature of the coolant in the intercooler (04) or in the aftercooler (05) corresponds to the exit temperature of the coolant at the subassembly cooler (08) ±20%.
  2. The cooling arrangement according to Claim 1, characterised in that a heat exchanger (09) is interposed in the coolant circuit between the respective coolant outlet of the intercooler (04) and of the aftercooler (05) and the hot side of the main cooler (07).
  3. The cooling arrangement according to Claim 1 or 2, characterised in that the main cooler (07) is a water-air cooler or a water-water cooler or a combination cooler, which uses water and air optionally as a cooling medium.
  4. The cooling arrangement according to Claim 3, characterised in that the main cooler (07) comprises a fan (11).
  5. The cooling arrangement according to any one of Claims 1 to 4, characterised in that the intercooler (04) and/or the aftercooler (05) have a plurality of feed inlets (12), to which the coolant can be optionally fed from the coolant outlet of the subassembly cooler (08).
  6. The cooling arrangement according to Claim 5, characterised in that a distributor unit is arranged between the coolant outlet of the subassembly cooler (08) and the feed inlets (12), which distributor unit supplies, in a temperature-controlled manner, that feed inlet (12) at which the intermediate temperature of the coolant in the intercooler (04) or aftercooler (05) is closest to the exit temperature of the coolant at the subassembly cooler (08).
  7. The cooling arrangement according to any one of Claims 1 to 6, characterised in that at least the intercooler (04), the aftercooler (05), the subassembly cooler (08), the heat exchanger (09), the first and second compressor stages (02, 03) and an electronic control unit are arranged within a common device housing.
  8. A method for cooling an at least two-stage compressed air generator (01), comprising the following steps:
    - guiding a cooling medium in a coolant circuit through a main cooler (07) and through a first liquid-cooled intercooler (04) connected in series with the main cooler (07), which intercooler (04) thus cools air precompressed by a first compressor stage (02);
    - guiding the cooling medium in the coolant circuit through an aftercooler (05) likewise connected in series with the main cooler (07) and connected parallel to the intercooler (04), which aftercooler (05) thus cools air post-compressed by a second compressor stage (03);
    - feeding the cooling medium cooled in the main cooler (07) to a liquid-cooled subassembly cooler (08), which absorbs heat from further subassemblies of the compressed air generator (01);
    wherein the heated cooling medium exiting the subassembly cooler (08) is fed via a feed inlet (12) into the intercooler (04) and/or into the aftercooler (05), wherein the feed takes place at a position (12) in the intercooler (04) or in the aftercooler (05) at which the intermediate temperature of the coolant in the intercooler (04) or aftercooler (05) corresponds to the exit temperature of the coolant at the subassembly cooler (08) ±20%.
  9. The method according to Claim 8, characterised in that the cooling medium heated in the intercooler (04) and in the aftercooler (05) is fed to a heat exchanger (09) for heat recovery before it is returned to the main cooler (07).
  10. The method according to Claim 8 or 9, characterised in that the heated cooling medium exiting the subassembly cooler (08) is fed via one of a plurality of feed inlets (12) into the intercooler (04) and/or into the aftercooler (05), wherein the feed inlet (12) is selected in such a way that the intermediate temperature of the coolant in the intercooler (04) or aftercooler (05) at said feed inlet (12) corresponds to the exit temperature of the coolant at the subassembly cooler (08).
EP20704784.6A 2019-01-30 2020-01-24 Cooling arrangement and method for cooling a compressed-air generator with at least two stages Active EP3918199B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102019102387.4A DE102019102387A1 (en) 2019-01-30 2019-01-30 Cooling arrangement and method for cooling an at least two-stage compressed air generator
PCT/EP2020/051751 WO2020156942A1 (en) 2019-01-30 2020-01-24 Cooling arrangement and method for cooling an at least two-stage compressed air generator

Publications (2)

Publication Number Publication Date
EP3918199A1 EP3918199A1 (en) 2021-12-08
EP3918199B1 true EP3918199B1 (en) 2023-03-08

Family

ID=69570619

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20704784.6A Active EP3918199B1 (en) 2019-01-30 2020-01-24 Cooling arrangement and method for cooling a compressed-air generator with at least two stages

Country Status (5)

Country Link
US (3) US11788524B2 (en)
EP (1) EP3918199B1 (en)
CN (1) CN113661325B (en)
DE (1) DE102019102387A1 (en)
WO (1) WO2020156942A1 (en)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN113597511B (en) * 2019-03-27 2023-05-02 株式会社日立产机系统 Compressor system and control method thereof
JP7367040B2 (en) * 2019-09-18 2023-10-23 株式会社日立産機システム heat recovery equipment
BE1030033B1 (en) * 2021-12-15 2023-07-10 Atlas Copco Airpower Nv AIR-COOLED PRESSUREFORMER WITH ENERGY RECOVERY FOR COMPRESSING OR PRESSURIZING A FLUID AND FEATURED WITH IMPROVED COOLING
DE102022112935A1 (en) * 2022-05-23 2023-11-23 Zf Cv Systems Global Gmbh Compressed air generating device and method for operating the same
DE102022112936A1 (en) * 2022-05-23 2023-11-23 Zf Cv Systems Global Gmbh Compressed air generating device and method for operating the same
DE102022112934A1 (en) * 2022-05-23 2023-11-23 Zf Cv Systems Global Gmbh Compressed air generating device and method for operating the same

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102777351A (en) 2012-08-08 2012-11-14 沈长青 Waste heat recycling device and recycling method of oil-free compressor
US20130067951A1 (en) 2011-09-16 2013-03-21 Anest Iwata Corporation Waste heat utilizing device for air compressor
US20180258952A1 (en) 2017-03-07 2018-09-13 Atlas Copco Airpower, Naamloze Vennootschap Compressor module for compressing gas and compressor equipped therewith

Family Cites Families (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DD155194A1 (en) * 1980-12-09 1982-05-19 Artur Wilda METHOD FOR THE ENERGETIC OPTIMIZATION OF A COMPACTION PROCESS
FR2710370B1 (en) 1993-09-21 1995-12-08 Air Liquide Method and assembly for compressing a gas.
JPH07217579A (en) 1994-02-01 1995-08-15 Hitachi Ltd Screw compressor cooling system
GB2367332B (en) 2000-09-25 2003-12-03 Compair Uk Ltd Improvements in multi-stage screw compressor drive arrangements
US7334428B2 (en) * 2005-09-30 2008-02-26 Sullair Corporation Cooling system for a rotary screw compressor
US20080127665A1 (en) * 2006-11-30 2008-06-05 Husky Injection Molding Systems Ltd. Compressor
JP5495293B2 (en) * 2009-07-06 2014-05-21 株式会社日立産機システム Compressor
BE1018598A3 (en) 2010-01-25 2011-04-05 Atlas Copco Airpower Nv METHOD FOR RECYCLING ENRGIE.
ES2834456T3 (en) 2013-12-17 2021-06-17 Kaeser Kompressoren Se Compressor
BE1022138B1 (en) * 2014-05-16 2016-02-19 Atlas Copco Airpower, Naamloze Vennootschap COMPRESSOR DEVICE AND A COOLER THAT IS APPLIED THEREOF
CN104100494B (en) * 2014-07-01 2016-08-17 中国科学院工程热物理研究所 A kind of compressed air method and system having from pre-cooling function
CN104179663B (en) 2014-08-13 2019-04-19 福建德兴节能科技有限公司 A kind of low energy consumption compressed air cooling means and its system
CN106089659A (en) 2016-08-09 2016-11-09 中山市艾能机械有限公司 Screw compression piston supercharged air-cooled integrated air compressor
DE102016011443A1 (en) 2016-09-21 2018-03-22 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Screw compressor for a commercial vehicle
DE102017107602B3 (en) 2017-04-10 2018-09-20 Gardner Denver Deutschland Gmbh Compressor system with internal air-water cooling

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20130067951A1 (en) 2011-09-16 2013-03-21 Anest Iwata Corporation Waste heat utilizing device for air compressor
CN102777351A (en) 2012-08-08 2012-11-14 沈长青 Waste heat recycling device and recycling method of oil-free compressor
US20180258952A1 (en) 2017-03-07 2018-09-13 Atlas Copco Airpower, Naamloze Vennootschap Compressor module for compressing gas and compressor equipped therewith

Also Published As

Publication number Publication date
DE102019102387A1 (en) 2020-07-30
CN113661325B (en) 2023-06-20
WO2020156942A1 (en) 2020-08-06
US11788524B2 (en) 2023-10-17
US20240068462A1 (en) 2024-02-29
EP3918199A1 (en) 2021-12-08
US12163511B2 (en) 2024-12-10
US20250101971A1 (en) 2025-03-27
CN113661325A (en) 2021-11-16
US20220106954A1 (en) 2022-04-07

Similar Documents

Publication Publication Date Title
EP3918199B1 (en) Cooling arrangement and method for cooling a compressed-air generator with at least two stages
EP3159506B1 (en) Functional synergies in the integration of orc systems in combustion engines
DE102008006259A1 (en) Integrated power station cooling system for e.g. generator, has conduction unit for conduction of cooling medium, which is delivered by refrigerator to heat dissipation devices for power station components of integrated cooling component
DE2852076A1 (en) PLANT FOR GENERATING MECHANICAL ENERGY FROM HEAT SOURCES OF DIFFERENT TEMPERATURE
DE102006010247A1 (en) Drive unit with heat recovery
EP3530890B1 (en) Drive with integrated orc
DE2900014A1 (en) GAS TURBINE DEVICE
EP2270322B1 (en) Cooling circuit for removing waste heat from an electromechanical convertor and power plant assembly with such a cooling circuit
EP3559564B1 (en) Method and apparatus for generating process cold and process steam
EP3447256B1 (en) System for cooling a process fluid from a heat producing installation
DE602005003489T2 (en) Multi-stage oil-free gas compressor
EP1167721B1 (en) Method and system for cooling a gas turbine plant
DE202013104306U1 (en) Dry running compressor for the production of compressed air
DE19923242A1 (en) Cooling method for a gas flow involves transferring heat from gas flow to absorption machine in first cooling stage(s) and using as energy for operating absorption machine
DE102011052776B4 (en) Supercritical heat pump
DE102012017314B4 (en) System for increasing the efficiency of two- or multi-stage compressor arrangements
DE10139315A1 (en) Cooling system for internal combustion engine, has single coolant pump and individual heat exchangers for engine and engine components
DE102009039326A1 (en) heat pump
DE102012014236B3 (en) Cooling device for temperature-control of e.g. roller of printing machine, has capacitor whose input is connected with outputs of both compressors, where output of capacitor is connected with inputs of both vaporizers
DE102011078455A1 (en) Refrigerant circuit for e.g. electric machine for e.g. intermittent application in motor car, has heat exchanger arranged between hot and cool components along flow direction of coolant in low temperature circuit
DE102021101268B4 (en) Fuel cell device and method for operating a fuel cell device
DE102006011380B4 (en) Heat engine
DE102019001161A1 (en) Refrigerant compressor and method for operating a refrigerant compressor
EP2989397A1 (en) Method and device for cooling an engine
EP3951140B1 (en) Energy recovery device with heat recovery circuit

Legal Events

Date Code Title Description
STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: UNKNOWN

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE INTERNATIONAL PUBLICATION HAS BEEN MADE

PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: REQUEST FOR EXAMINATION WAS MADE

17P Request for examination filed

Effective date: 20210806

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

DAV Request for validation of the european patent (deleted)
DAX Request for extension of the european patent (deleted)
REG Reference to a national code

Ref country code: DE

Ref legal event code: R079

Ref document number: 502020002702

Country of ref document: DE

Free format text: PREVIOUS MAIN CLASS: F04B0039060000

Ipc: F04B0001060000

RIC1 Information provided on ipc code assigned before grant

Ipc: F04B 41/06 20060101ALI20220818BHEP

Ipc: F04B 39/06 20060101ALI20220818BHEP

Ipc: F04B 53/08 20060101ALI20220818BHEP

Ipc: F04C 29/04 20060101ALI20220818BHEP

Ipc: F04C 23/00 20060101ALI20220818BHEP

Ipc: F04C 18/16 20060101ALI20220818BHEP

Ipc: F04B 1/06 20200101AFI20220818BHEP

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: GRANT OF PATENT IS INTENDED

INTG Intention to grant announced

Effective date: 20220926

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE PATENT HAS BEEN GRANTED

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

Ref country code: AT

Ref legal event code: REF

Ref document number: 1552726

Country of ref document: AT

Kind code of ref document: T

Effective date: 20230315

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 502020002702

Country of ref document: DE

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: LANGUAGE OF EP DOCUMENT: GERMAN

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG9D

P01 Opt-out of the competence of the unified patent court (upc) registered

Effective date: 20230523

REG Reference to a national code

Ref country code: NL

Ref legal event code: MP

Effective date: 20230308

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: RS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20230308

Ref country code: NO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20230608

Ref country code: LV

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20230308

Ref country code: LT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20230308

Ref country code: HR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20230308

Ref country code: ES

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20230308

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20230308

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20230308

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20230609

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20230308

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SM

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20230308

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20230308

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20230710

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20230308

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20230308

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20230308

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20230308

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20230708

REG Reference to a national code

Ref country code: DE

Ref legal event code: R026

Ref document number: 502020002702

Country of ref document: DE

PLBI Opposition filed

Free format text: ORIGINAL CODE: 0009260

PLAX Notice of opposition and request to file observation + time limit sent

Free format text: ORIGINAL CODE: EPIDOSNOBS2

26 Opposition filed

Opponent name: ATLAS COPCO AIRPOWER N.V.

Effective date: 20231207

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20230308

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20230308

PLBB Reply of patent proprietor to notice(s) of opposition received

Free format text: ORIGINAL CODE: EPIDOSNOBS3

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20230308

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MC

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20230308

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MC

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20230308

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20240124

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20240124

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20240131

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20240131

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20240131

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20240131

REG Reference to a national code

Ref country code: BE

Ref legal event code: MM

Effective date: 20240131

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20230308

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20230308

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20240124

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20240124

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20250127

Year of fee payment: 6

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: AT

Payment date: 20250417

Year of fee payment: 5

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20250131

Year of fee payment: 6

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20250130

Year of fee payment: 6

PLCK Communication despatched that opposition was rejected

Free format text: ORIGINAL CODE: EPIDOSNREJ1

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO

Effective date: 20200124

APAH Appeal reference modified

Free format text: ORIGINAL CODE: EPIDOSCREFNO

APAW Appeal reference deleted

Free format text: ORIGINAL CODE: EPIDOSDREFNO

APBP Date of receipt of notice of appeal recorded

Free format text: ORIGINAL CODE: EPIDOSNNOA2O

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: HU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO

Effective date: 20200124

REG Reference to a national code

Ref country code: DE

Ref legal event code: R100

Ref document number: 502020002702

Country of ref document: DE

APBU Appeal procedure closed

Free format text: ORIGINAL CODE: EPIDOSNNOA9O

PLBN Opposition rejected

Free format text: ORIGINAL CODE: 0009273

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: OPPOSITION REJECTED

27O Opposition rejected

Effective date: 20251022

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: TR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20230308