EP0618361A1 - Method and apparatus for compressing a gas - Google Patents
Method and apparatus for compressing a gas Download PDFInfo
- Publication number
- EP0618361A1 EP0618361A1 EP94250063A EP94250063A EP0618361A1 EP 0618361 A1 EP0618361 A1 EP 0618361A1 EP 94250063 A EP94250063 A EP 94250063A EP 94250063 A EP94250063 A EP 94250063A EP 0618361 A1 EP0618361 A1 EP 0618361A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- heat exchanger
- heat engine
- compressor
- gas
- pressure
- 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.)
- Granted
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
Definitions
- the invention relates to a method for compressing a gaseous medium, in particular air, according to the preamble of claim 1.
- the compressed gas If the compressed gas is directed to the consumption points without further treatment, it cools down in this way further down, condensate will precipitate again immediately.
- This accumulation of condensate can be disruptive in certain applications, for example when sandblasting for building renovation, because it causes the sand to stick together.
- the problem of the accumulation of condensate in the area of the point of consumption also arises if the compressed gas is not recooled before being released.
- the condensate that accumulates in most cases is not harmful as long as it does not freeze.
- icing leads to severe functional restrictions.
- the object of the invention is to provide a method for compressing a gaseous medium, in particular air, with which a relatively dry gas is generated and in which a complex monitoring system can be dispensed with.
- the proposed method is based on the idea of using the thermal energy of the cooling liquid used in a compression system for heating the cooled compressed gas.
- These cooling liquids can be, for example, the lubricating oil or the cooling liquid of the heat engine driving the compressor.
- the liquid used for cooling and lubricating an injection-cooled compressor, for example oil or water, can also be used for this.
- the advantage of the method can be seen in the fact that the heat transfer during the transition from a liquid to the compressed gas can be determined relatively easily and quite precisely.
- the heat exchanger required for heat transfer can be simple and compact. This is preferably designed as a tube bundle heat exchanger.
- the temperature conditions of the liquid used are at a favorable level, so that, as a rule, no additional control and monitoring systems are required.
- FIG. 2 shows another embodiment in the same functional diagram as FIG. 1, the same reference numerals being used for the same parts.
- the gas to be compressed is cleaned via an intake filter 10 and fed to a liquid-gel-cooled compressor unit 40 via an intake line 11.
- a heat engine 20 is also used here to drive the compressor 40.
- the compressed gas-liquid mixture passes from the compressor 40 via a line 12 to the separator 55.
- the separator 55 is monitored in terms of pressure by a safety valve 51.
- the still moist compressed gas passes through a line 71 and a pressure-holding check valve 52 arranged therein to an aftercooler 60 which is coupled to a condensate separator 61.
- the further path of the compressed gas corresponds to the embodiment shown in FIG. 1.
- the liquid separated in the separator 55 is returned to the compressor 40 from the liquid sump via the line 15, 16, 18. The return takes place via the system pressure prevailing in the separator 55.
- a filter 41 and an oil or liquid cooler 44 are arranged in the return line 15, 16, 18.
- FIG. 3 shows a further embodiment in a functional diagram comparable to FIG. 2.
- the thermal energy of the returned cooling and lubricating liquid is used in this example for heating the compressed gas.
- a heat exchanger 42 is arranged in the return line 15, 16, 17, 18 between the filter 41 and the oil or liquid cooler 44.
- this heat exchanger 42 is connected to the compressed gas system via lines 76, 77.
- the oil or liquid cooler 44 can be chosen to be the same size as in the embodiment shown in FIG. 2 or alternatively also smaller, since part of the required recooling takes place via the heat exchanger 42 arranged in the return line 16, 17.
- the type of drive unit for the compressor 40 is free, since this is not used for heating the compressed gas.
- it can be an electric motor, but also, alternatively, a diesel engine as shown in FIGS. 1 or 2 or another drive unit.
- FIG. 4 shows a further variant of the embodiment according to FIG. 2.
- no aftercooler 60 is provided in the pressure line 71 between the pressure vessel 55 and the heat exchanger 65, and the compressed gas is released by the lubricating and / or cooling liquid before being delivered to the consumption points 53 Heat engine 20 warmed.
Abstract
Description
Die Erfindung betrifft ein Verfahren zum Verdichten eines gasförmigen Mediums, insbesondere Luft, gemäß dem Gattungsbegriff des Anspruches 1.The invention relates to a method for compressing a gaseous medium, in particular air, according to the preamble of claim 1.
Für den Anwendungsbereich im Baugewerbe werden häufig mobile Kompressoranlagen eingesetzt, deren flüssigkeitsgekühltes oder trockenlaufendes Verdichteraggregat durch die Nutzseite eines Antriebsaggregates beispielsweise Diesel- oder Elektromotor angetrieben wird. Die Druckgasqualität muß hinsichtlich ihrer relativen Feuchte oft als zu nass bezeichnet werden, unabhängig davon, ob die Feuchtigkeit über das angesaugte Gas direkt oder indirekt über die für die Kühlung und Schmierung des Verdichters eingespritzte Flüssigkeit eingebracht wird. Bei Verdichteranlagen für spezielle Anwendungen wird das Gas nach der Verdichtung zurückgekühlt und das ausfallende Kondensat in geeigneten Abscheidesystemen, z.B. Zyklonabscheider getrennt und von dem Druckgas abgeschieden. Das Druckgas hat nach diesem Abscheidevorgang eine relative Feuchte von 100 %, d. h. das Druckgas ist mit Dampfanteilen gesättigt. Wird das Druckgas ohne weitere Behandlung zu den Verbrauchsstellen geleitet und kühlt es sich auf diesem Wege weiter ab, so fällt sofort wieder Kondensat aus. Dieser Kondensatanfall kann in bestimmten Anwendungsfällen störend sein, beispielsweise beim Sandstrahlen zur Bausanierung, weil es dadurch zum Verkleben des Sandes kommt. Das Problem des Anfalls von Kondensat im Bereich der Verbrauchsstelle tritt aber auch dann auf, wenn das verdichtete Gas vor Abgabe nicht rückgekühlt wird. Bei herkömmlichen Verdichteranlagen, wie sie üblicherweise im Baugewerbe genutzt werden, ist in den meisten Fällen das anfallende Kondensat nicht schädlich, solange es nicht zum Vereisen kommt. Insbesondere bei Preßluftwerkzeugen führt eine Vereisung zu einer starken Funktionseinschränkung.For the area of application in the construction industry, mobile compressor systems are often used, whose liquid-cooled or dry-running compressor unit is driven by the useful side of a drive unit, for example a diesel or electric motor. The compressed gas quality often has to be described as too wet with regard to its relative humidity, regardless of whether the moisture is introduced directly or indirectly via the gas injected for cooling and lubricating the compressor. In compressor systems for special applications, the gas is cooled back after compression and the condensate that precipitates is separated in suitable separation systems, eg cyclone separators, and separated from the compressed gas. After this separation process, the compressed gas has a relative humidity of 100%, ie the compressed gas is saturated with vapor components. If the compressed gas is directed to the consumption points without further treatment, it cools down in this way further down, condensate will precipitate again immediately. This accumulation of condensate can be disruptive in certain applications, for example when sandblasting for building renovation, because it causes the sand to stick together. The problem of the accumulation of condensate in the area of the point of consumption also arises if the compressed gas is not recooled before being released. In conventional compressor systems, such as those commonly used in the construction industry, the condensate that accumulates in most cases is not harmful as long as it does not freeze. In the case of compressed air tools in particular, icing leads to severe functional restrictions.
Es sind nun einige Verfahren bekannt, bei denen durch eine nachträgliche Erwärmung des Gases die relative Feuchte abgesenkt wird. Eine der Möglichkeiten besteht darin (DE-GM 75 22 395; DE-GM 86 01 519) das Druckgas mit der thermischen Energie des Abgases einer Wärmekraftmaschine zu beaufschlagen. Diese Lösung ist konstruktiv sehr aufwendig und es werden für die das heiße Abgas führende Bauteile hochwarmfeste Werkstoffe mit guter Korrosionsbeständigkeit benötigt. Diese Werkstoffe sind sehr teuer und schwer zu verarbeiten. Weiterhin ist bei diesem Verfahren ein aufwendiges Überwachungssystem notwendig, welches das Druckgas temperaturmäßig kontrolliert und bei Erreichen einer kritischen Betriebstemperatur regelungstechnisch in das Abgassystem und/oder das Druckgassystem eingreifen muß.Some methods are now known in which the relative humidity is reduced by subsequent heating of the gas. One of the possibilities is to apply (DE-GM 75 22 395; DE-GM 86 01 519) the compressed gas with the thermal energy of the exhaust gas from a heat engine. This solution is structurally very complex and high-temperature-resistant materials with good corrosion resistance are required for the components carrying the hot exhaust gas. These materials are very expensive and difficult to process. Furthermore, this method requires a complex monitoring system which controls the temperature of the compressed gas and, when a critical operating temperature is reached, has to intervene in the exhaust system and / or the compressed gas system in terms of control technology.
Aufgabe der Erfindung ist es, ein Verfahren zum Verdichten eines gasförmigen Mediums, insbesondere Luft, anzugeben, mit dem ein relativ trocknes Gas erzeugt wird und bei dem auf ein aufwendiges Überwachungssystem verzichtet werden kann.The object of the invention is to provide a method for compressing a gaseous medium, in particular air, with which a relatively dry gas is generated and in which a complex monitoring system can be dispensed with.
Diese Aufgabe wird mit den im kennzeichnenden Teil angegebenen Merkmalen des Anspruches 1 oder 3 gelöst.This object is achieved with the features of claim 1 or 3 specified in the characterizing part.
Vorteilhafte Weiterbildungen sowie Vorrichtungen zur Durchführung der Verfahren sind Bestandteil von Unteransprüchen.Advantageous further developments and devices for carrying out the method are part of subclaims.
Das vorgeschlagene Verfahren beruht auf der Idee, die thermische Energie der in einer Verdichteranlage verwendeten Kühlflüssigkeit für die Erwärmung des gekühlten Druckgases zu verwenden. Diese Kühlflüssigkeiten können beispielsweise das Schmieröl bzw. die Kühlflüssigkeit der den Verdichter antreibenden Wärmekraftmaschine sein. Auch die für die Kühlung und Schmierung eines einspritzgekühlten Verdichters verwendete Flüssigkeit, beispielsweise Öl oder Wasser kann dafür genutzt werden. Der Vorteil des Verfahrens ist darin zu sehen, daß die Wärmeübertragung beim Übergang von einer Flüssigkeit auf das Druckgas relativ einfach und recht genau bestimmbar ist. Außerdem kann der für die Wärmeübertragung erforderliche Wärmetauscher einfach und kompakt sein. Vorzugsweise ist dieser als Rohrbündelwärmetauscher ausgebildet. Die Temperaturverhältnisse der genutzten Flüssigkeit liegen in einem günstigen Niveau, so daß im Regelfall keine zusätzlichen Regelungs- und Überwachungssysteme erforderlich sind. Einzige Ausnahme kann im ungünstigsten Fall die Verwendung des Schmieröles der Wärmekraftmaschine sein, da diese bei bis zu etwa 130 Grad Celsius liegen kann. Da die maximal zulässige Verdichtungsendtemperatur für mit Öl gekühlte Verdichter in Deutschland bei 100 Grad Celsius liegt, ist ein einfacher Begrenzungsschalter ausreichend, um auch bei Anlagen mit strenger Auflage hinsichtlich der maximalen Verdichtungsendtemperatur ein Überschreiten dieser Maximaltemperatur zu vermeiden.The proposed method is based on the idea of using the thermal energy of the cooling liquid used in a compression system for heating the cooled compressed gas. These cooling liquids can be, for example, the lubricating oil or the cooling liquid of the heat engine driving the compressor. The liquid used for cooling and lubricating an injection-cooled compressor, for example oil or water, can also be used for this. The advantage of the method can be seen in the fact that the heat transfer during the transition from a liquid to the compressed gas can be determined relatively easily and quite precisely. In addition, the heat exchanger required for heat transfer can be simple and compact. This is preferably designed as a tube bundle heat exchanger. The temperature conditions of the liquid used are at a favorable level, so that, as a rule, no additional control and monitoring systems are required. The only exception can be in the worst case, the use of the lubricating oil of the heat engine, since this can be up to about 130 degrees Celsius. Since the maximum permissible compression end temperature for oil-cooled compressors in Germany is 100 degrees Celsius, a simple limit switch is sufficient to avoid exceeding this maximum temperature even in systems with strict requirements with regard to the maximum compression end temperature.
Bei der Verwendung der thermischen Energie der rückgeführten Kühl- bzw. Schmierflüssigkeiten bei flüssigkeitsgekühlten Verdichtern zur Erwärmung des Druckgases wird die Flüssigkeit bereits etwas abgekühlt, so daß in der Rückkühlleitung weniger Kühlleistung benötigt wird. Dies hat zur Folge, daß entweder die Kühleinrichtung klein gebaut werden kann oder bei gleichgroßer Kühlerleistung eine Freigabe des Verdichteraggregates für höher liegende Umgebungstemperaturen möglich ist.When using the thermal energy of the recirculated cooling or lubricating liquids in liquid-cooled compressors to heat the compressed gas, the liquid is already cooled somewhat, so that less cooling power is required in the recooling line. This has the consequence that either the cooling device can be built small or with the same cooling capacity, the compressor unit can be released for higher ambient temperatures.
Ein weiterer Vorteil des erfindungsgemäßen Verfahrens ist darin zu sehen, daß durch die Kompaktheit des eingesetzten Wärmetauschers eine große Freiheit hinsichtlich der Plazierung dieser Vorrichtung in der Anlage liegt. Nicht vergessen werden soll auch der daraus sich ergebende Kostenvorteil, da die flüssigkeitsbeaufschlagte Wärmetauscherlösung kostenmäßig weit unterhalb der bisher bekannten Abgaserwärmung liegt.Another advantage of the method according to the invention can be seen in the fact that the compactness of the heat exchanger used gives great freedom with regard to the placement of this device in the system. The resulting cost advantage should not be forgotten either, since the cost of the liquid heat exchanger solution is far below the previously known exhaust gas heating.
In der Zeichnung wird anhand einiger Ausführungsbeispiele das erfindungsgemäße Verfahren näher erläutert.In the drawing, the method according to the invention is explained in more detail using some exemplary embodiments.
Es zeigen:
- Figur 1
- in einem Funktionsschaubild eine erste Ausführungsform mit einem trockenlaufenden Verdichteraggregat und einer Wärmekraftmaschine als Antriebsaggregat
- Figur 2
- wie Figur 1 mit einem flüssigkeitsgekühlten Verdichteraggregat
- Figur 3
- ähnlich Figur 2, jedoch mit einem in der Rückführleitung angeordneten Wärmetauscher
- Figur 4
- wie Figur 2, jedoch ohne Nachkühler
- Figure 1
- in a functional diagram, a first embodiment with a dry-running compressor unit and a heat engine as the drive unit
- Figure 2
- like Figure 1 with a liquid-cooled compressor unit
- Figure 3
- Similar to Figure 2, but with a heat exchanger arranged in the return line
- Figure 4
- like Figure 2, but without aftercooler
Figur 2 zeigt in einem gleichen Funktionsschaubild wie Figur 1 eine andere Ausführungsform, wobei für gleiche Teile gleiche Bezugszeichen verwendet worden sind. Das zu verdichtende Gas wird über einen Ansaugfilter 10 gereinigt und über eine Ansaugleitung 11 einem flüssigkeitsgelkühlten Verdichteraggregat 40 zugeführt. Als Antrieb des Verdichters 40 wird hier ebenfalls eine Wärmekraftmaschine 20 verwendet. Das verdichtete Gas-Flüssigkeitsgemisch gelangt aus dem Verdichter 40 über eine Leitung 12 zum Abscheider 55. Der Abscheider 55 wird druckmäßig durch ein Sicherheitsventil 51 überwacht. Das noch feuchte Druckgas gelangt über eine Leitung 71 und einem darin angeordneten Druckhalte-Rückschlagventil 52 zu einem Nachkühler 60, der mit einem Kondensatabscheider 61 gekoppelt ist. Der weitere Weg des Druckgases entspricht der in der Figur 1 dargestellten Ausführungsform. Die im Abscheider 55 abgeschiedene Flüssigkeit wird aus dem Flüssigkeitssumpf über die Leitung 15,16,18 dem Verdichter 40 wieder rückgeführt. Die Rückführung erfolgt über den im Abscheider 55 herrschenden Systemdruck.FIG. 2 shows another embodiment in the same functional diagram as FIG. 1, the same reference numerals being used for the same parts. The gas to be compressed is cleaned via an
In der Rückführleitung 15,16,18 ist ein Filter 41 und ein Öl- oder Flüssigkeitskühler 44 angeordnet.A
In Figur 3 ist in einem vergleichbaren Funktionsschaubild wie Fig. 2 eine weitere Ausführungsform dargestellt. Im Unterschied zu den in den Figuren 1 und 2 dargestellten Ausführungsformen wird in diesem Beispiel die thermische Energie der rückgeführten Kühl- und Schmierflüssigkeit für die Erwärmung des Druckgases genutzt. Dazu ist in der Rückführleitung 15,16,17,18 ein Wärmetauscher 42 zwischen dem Filter 41 und dem Öl- oder Flüssigkeitskühler 44 angeordnet. Auf der Gasseite ist dieser Wärmetauscher 42 über Leitungen 76,77 mit dem Druckgassystem verbunden. Je nach Auslegung der Anlage kann der Öl- oder Flüssigkeitskühler 44 gleich groß gewählt werden wie bei der in Figur 2 dargestellten Ausführungsform oder alternativ auch kleiner, da ein Teil der erforderlichen Rückkühlung über den in der Rückführleitung 16,17 angeordneten Wärmetauscher 42 erfolgt. Bei der in Figur 3 dargestellten Ausführungsform ist die Art des Antriebsaggregates für den Verdichter 40 frei, da dieses für die Erwärmung des Druckgases nicht genutzt wird. Es kann wie hier dargestellt ein Elektromotor, aber ebenso alternativ ein Dieselmotor entsprechend der Darstellung in den Figuren 1 oder 2 sein bzw. ein anderes Antriebsaggregat.FIG. 3 shows a further embodiment in a functional diagram comparable to FIG. 2. In contrast to the embodiments shown in FIGS. 1 and 2, the thermal energy of the returned cooling and lubricating liquid is used in this example for heating the compressed gas. For this purpose, a
Figur 4 zeigt eine weitere Variante der Ausführungsform gemäß Figur 2. Im Unterschied dazu ist in der Druckleitung 71 zwischen Druckbehälter 55 und Wärmetauscher 65 kein Nachkühler 60 vorgesehen und das verdichtete Gas wird vor Abgabe an die Verbrauchsstellen 53 durch die Schmier- und/oder Kühlflüssigkeit der Wärmekraftmaschine 20 erwärmt.FIG. 4 shows a further variant of the embodiment according to FIG. 2. In contrast to this, no
Claims (4)
dadurch gekennzeichnet,
daß zur Erzeugung eines Gases mit geringer relativer Feuchte der Wärmetauscher mit der thermischen Energie des Schmier- und/oder Kühlkreislaufes der Wärmekraftmaschine beaufschlagt wird.Method for compressing a gaseous medium, in particular air, in which gas drawn in by means of a compressor driven by the useful side of a heat engine compresses from a low outlet pressure, in particular atmospheric pressure, to a final pressure predetermined in a pressure vessel and after removal from the pressure vessel and before delivery to it Consumption points are heated using the thermal energy of the heat engine by means of a heat exchanger,
characterized by
that to generate a gas with low relative humidity, the heat exchanger with the thermal energy of the lubrication and / or cooling circuit of the heat engine is applied.
dadurch gekennzeichnet,
daß die Verbindungsleitungen (73, 74) zwischen Wärmetauscher (65) und der Wärmekraftmaschine (20) Teil des Schmier- und/oder Kühlkreislaufes der Wärmekraftmaschine (20) ist.Apparatus for carrying out the method according to claim 1 with a compressor which is thermally connected to the heat engine via a line with a pressure vessel and a downstream heat exchanger to the consumption points and the heat exchanger via a line to the useful side of a heat engine and its pressure port,
characterized by
that the connecting lines (73, 74) between the heat exchanger (65) and the heat engine (20) is part of the lubrication and / or cooling circuit of the heat engine (20).
dadurch gekennzeichnet,
daß das gekühlte verdichtete Gas mit der thermischen Energie der vom Abscheider rückgeführten Flüssigkeit beaufschlagt wird.Method for compressing a gaseous medium, in particular air, in which gas drawn in by means of a liquid-cooled compressor driven by the useful side of a drive unit compresses gas from a lower outlet pressure, in particular atmospheric pressure, to a predetermined final pressure and heats it up before delivery to the consumption points, the heating being one After-cooling of the compressed gas is connected upstream and the liquid separated in the separator is returned to the compressor and cooled before injection into the compressor,
characterized by
that the cooled compressed gas is subjected to the thermal energy of the liquid returned from the separator.
dadurch gekennzeichnet,
daß der Wärmetauscher (42) in der Rückführleitung (16, 17) zwischen Filter (41) und Nachkühler (44) angeordnet ist.Apparatus for carrying out the method according to claim 3 with a liquid-cooled compressor connected to the useful side of a drive unit and its pressure port via a line with a separator and the liquid sump of the separator via a return line in which a filter and a cooler are arranged, with the compressor are connected and a cooler, a condensate separator and a heat exchanger are arranged between the separator and the consumption points,
characterized by
that the heat exchanger (42) in the return line (16, 17) between the filter (41) and aftercooler (44) is arranged.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE4310100 | 1993-03-23 | ||
DE4310100A DE4310100C2 (en) | 1993-03-23 | 1993-03-23 | Method and device for compressing a gaseous medium |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0618361A1 true EP0618361A1 (en) | 1994-10-05 |
EP0618361B1 EP0618361B1 (en) | 1997-01-22 |
Family
ID=6484093
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP94250063A Expired - Lifetime EP0618361B1 (en) | 1993-03-23 | 1994-03-11 | Method and apparatus for compressing a gas |
Country Status (2)
Country | Link |
---|---|
EP (1) | EP0618361B1 (en) |
DE (2) | DE4310100C2 (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1070610A3 (en) * | 1999-07-21 | 2003-01-02 | Werner Wille | Method and apparatus for compressing a gas |
Families Citing this family (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE19847885A1 (en) * | 1998-10-20 | 2000-05-04 | Werner Wille | Apparatus used in the building industry for compressing a gaseous medium has a post condenser arranged outside of the engine chamber |
DE19942265A1 (en) * | 1999-09-04 | 2001-03-08 | Alup Kompressoren Gmbh | Compressor system and method for compressing a gas |
DE102008046298A1 (en) * | 2008-09-09 | 2010-03-11 | Epc Engineering Consulting Gmbh | Apparatus for the production of bacterially synthesized cellulose or cellulose-containing sheet material |
DE102017131084A1 (en) * | 2017-12-22 | 2019-06-27 | Thomas Mayer | Device for heating and / or cooling a liquid medium and method for heating and / or cooling a liquid medium located in a container arrangement with at least one container |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3152753A (en) * | 1961-10-19 | 1964-10-13 | Renard P Adams | Heat exchanger method and apparatus |
DE7522395U (en) * | 1975-11-06 | Sullair Europe Corp | Screw compressor unit | |
DE8601519U1 (en) * | 1986-01-22 | 1987-10-01 | Pressluft-Frantz Gmbh, 6000 Frankfurt, De |
Family Cites Families (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE1075268B (en) * | 1960-02-11 | Worthmgton Corporation Harrison NJ (V St A) | Device for warming and cooling the lubricant of a rotary piston compressor driven by a flussigkeitsgekuhltui engine, in particular an internal combustion engine | |
US2090214A (en) * | 1935-03-12 | 1937-08-17 | Maniscalco Pietro | Compressed air power unit |
DE862642C (en) * | 1942-10-30 | 1953-01-12 | Klein | Process for cooling compressed gas for the purpose of separating lubricating oil and water and for reheating this gas in order to increase its working capacity |
FR1516809A (en) * | 1966-11-10 | 1968-02-05 | Peugeot | Method for regulating a compressed gas production installation, and installation including application |
GB1557296A (en) * | 1976-04-26 | 1979-12-05 | Cooper Ind Inc | Liquid injected compressors |
JPS62284918A (en) * | 1986-06-02 | 1987-12-10 | Tonen Sekiyukagaku Kk | Manufacture of high temperature high pressure gas and device thereof |
-
1993
- 1993-03-23 DE DE4310100A patent/DE4310100C2/en not_active Expired - Fee Related
-
1994
- 1994-03-11 EP EP94250063A patent/EP0618361B1/en not_active Expired - Lifetime
- 1994-03-11 DE DE59401627T patent/DE59401627D1/en not_active Expired - Fee Related
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE7522395U (en) * | 1975-11-06 | Sullair Europe Corp | Screw compressor unit | |
US3152753A (en) * | 1961-10-19 | 1964-10-13 | Renard P Adams | Heat exchanger method and apparatus |
DE8601519U1 (en) * | 1986-01-22 | 1987-10-01 | Pressluft-Frantz Gmbh, 6000 Frankfurt, De |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1070610A3 (en) * | 1999-07-21 | 2003-01-02 | Werner Wille | Method and apparatus for compressing a gas |
Also Published As
Publication number | Publication date |
---|---|
EP0618361B1 (en) | 1997-01-22 |
DE4310100A1 (en) | 1994-09-29 |
DE4310100C2 (en) | 1997-08-14 |
DE59401627D1 (en) | 1997-03-06 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
DE4320302C2 (en) | Arrangement for energy generation on board an aircraft, in particular a passenger aircraft | |
DE2238551A1 (en) | METHOD AND DEVICE FOR DRYING A WORKING MEDIUM COMPRESSED IN A COMPRESSOR | |
DE3420303A1 (en) | COMBUSTION ENGINE UNIT WITH VENTILATION SYSTEM FOR THE INJECTION PUMPS | |
DE102017002601A1 (en) | Cooling device for electronic control unit | |
EP2435160A1 (en) | Process for purifying compressed air, compressed air purification apparatus and motor vehicle having such an apparatus | |
EP0618361B1 (en) | Method and apparatus for compressing a gas | |
EP1370760B1 (en) | Device for humidifying the intake air of an internal combustion engine, which is equipped with a turbocharger, involving pre-heating effected by a water circuit | |
DE102013102879B4 (en) | Compressor with adjustment of the gas inlet temperature and method for operating this compressor | |
DE4438093C1 (en) | Ventilation device for parts of motor vehicle engines | |
EP0783658B1 (en) | Method and device for cooling gases | |
DE112011100614T5 (en) | Arrangement for defrosting an intercooler | |
EP3653882B1 (en) | Virtual sensor for the water content in oil circuit | |
EP2245305B1 (en) | Utility vehicle with a cooled compressor and method for cooling a compressor | |
DE102016213153B4 (en) | Condensation system for a fuel cell | |
DE102004051435B3 (en) | System for producing of dry compressed air, especially for rail vehicles, has air drier connected after cooler, whereby moisture falls out as condensate which is used for cooling of cooler by evaporation | |
DE19600377B4 (en) | Compressed gas system with a gas dryer | |
DE69921368T2 (en) | METHOD AND DEVICE FOR REGULATING COLD-AIR GENERATION | |
DE19934315C2 (en) | Method and device for compressing a gaseous medium | |
DE102019216874A1 (en) | PROCEDURE AND PROCESSING ARRANGEMENT FOR A HYDRAULIC PRESSURE MEDIUM | |
DE102013211701A1 (en) | A vehicle heating system and method of heating the interior of a vehicle with a vehicle heating system | |
DE19954190B4 (en) | Method and apparatus for generating cold | |
DE102018000988A1 (en) | Compressor system for generating compressed air and vehicle with compressed air spring system with compressor system for generating compressed air | |
DE102004011266A1 (en) | Internal combustion engine with humidifier and heat exchanger | |
DE102016009562A1 (en) | Device for providing gas | |
DE951817C (en) | Device for thawing an ice separator in a system with a cold gas cooling machine |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
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 |
|
AK | Designated contracting states |
Kind code of ref document: A1 Designated state(s): BE DE FR GB IT |
|
17P | Request for examination filed |
Effective date: 19940916 |
|
17Q | First examination report despatched |
Effective date: 19951127 |
|
GRAG | Despatch of communication of intention to grant |
Free format text: ORIGINAL CODE: EPIDOS AGRA |
|
GRAH | Despatch of communication of intention to grant a patent |
Free format text: ORIGINAL CODE: EPIDOS IGRA |
|
GRAH | Despatch of communication of intention to grant a patent |
Free format text: ORIGINAL CODE: EPIDOS IGRA |
|
GRAA | (expected) grant |
Free format text: ORIGINAL CODE: 0009210 |
|
AK | Designated contracting states |
Kind code of ref document: B1 Designated state(s): BE DE FR GB IT |
|
ITF | It: translation for a ep patent filed |
Owner name: GUZZI E RAVIZZA S.R.L. |
|
ET | Fr: translation filed | ||
REF | Corresponds to: |
Ref document number: 59401627 Country of ref document: DE Date of ref document: 19970306 |
|
GBT | Gb: translation of ep patent filed (gb section 77(6)(a)/1977) |
Effective date: 19970324 |
|
PLBE | No opposition filed within time limit |
Free format text: ORIGINAL CODE: 0009261 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT |
|
26N | No opposition filed | ||
REG | Reference to a national code |
Ref country code: GB Ref legal event code: IF02 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: GB Payment date: 20070322 Year of fee payment: 14 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: IT Payment date: 20070613 Year of fee payment: 14 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: FR Payment date: 20070319 Year of fee payment: 14 |
|
GBPC | Gb: european patent ceased through non-payment of renewal fee |
Effective date: 20080311 |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: ST Effective date: 20081125 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: FR Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20080331 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: GB Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20080311 |
|
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 NON-PAYMENT OF DUE FEES Effective date: 20080311 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: DE Payment date: 20090320 Year of fee payment: 16 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: BE Payment date: 20090430 Year of fee payment: 16 |
|
BERE | Be: lapsed |
Owner name: *MANNESMANN A.G. Effective date: 20100331 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: DE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20101001 Ref country code: BE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20100331 |