EP1907704B1 - Oil-injected compressor with means for oil temperature regulation - Google Patents
Oil-injected compressor with means for oil temperature regulation Download PDFInfo
- Publication number
- EP1907704B1 EP1907704B1 EP06754724A EP06754724A EP1907704B1 EP 1907704 B1 EP1907704 B1 EP 1907704B1 EP 06754724 A EP06754724 A EP 06754724A EP 06754724 A EP06754724 A EP 06754724A EP 1907704 B1 EP1907704 B1 EP 1907704B1
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- European Patent Office
- Prior art keywords
- oil
- compressor
- injected
- speed
- cooler
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- 238000001816 cooling Methods 0.000 claims abstract description 28
- 238000005461 lubrication Methods 0.000 claims abstract description 7
- 230000008878 coupling Effects 0.000 claims description 19
- 238000010168 coupling process Methods 0.000 claims description 19
- 238000005859 coupling reaction Methods 0.000 claims description 19
- 238000011144 upstream manufacturing Methods 0.000 claims description 2
- 230000001105 regulatory effect Effects 0.000 claims 3
- 239000003570 air Substances 0.000 description 32
- 238000010438 heat treatment Methods 0.000 description 3
- 238000007789 sealing Methods 0.000 description 3
- 239000012080 ambient air Substances 0.000 description 2
- 230000006835 compression Effects 0.000 description 2
- 238000007906 compression Methods 0.000 description 2
- 238000010276 construction Methods 0.000 description 2
- 230000005484 gravity Effects 0.000 description 2
- 230000004308 accommodation Effects 0.000 description 1
- 230000006978 adaptation Effects 0.000 description 1
- 230000032683 aging Effects 0.000 description 1
- 230000000254 damaging effect Effects 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 230000018109 developmental process Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 230000000630 rising effect Effects 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Chemical compound O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
Images
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/02—Lubrication; Lubricant separation
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
- F04C18/14—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
- F04C18/16—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
Definitions
- the present invention relates to an oil-injected compressor, in particular an oil-injected mobile screw compressor, with a motor-driven compressor unit for generating compressed air, which cooperates with an oil circuit for lubrication, the oil reservoir is housed in a downstream ⁇ labscheider adopted for separating the oil from the compressed air, wherein means for Oil temperature control are provided, which include a cooler with fan.
- a compressor is from the document WO 02/46 617 A1 and discloses the preamble of claim 1.
- the present invention is useful in other types of oil-injected compressors, such as scroll and vane compressors, in addition to oil-injected screw compressors.
- oil is injected by means of an oil circuit for lubrication in the field of moving compressor components and at their bearings in order to lubricate the one here existing, rotating at high speed bearings, and on the other also an inadmissible heating to prevent in the field of moving compressor components as a result of friction.
- the oil also serves to seal the air side against other areas of the compressor.
- the field of application of such oil-injected compressors extends thanks to the compactness mainly to mobile applications in rail vehicle construction or in the field of commercial vehicle construction.
- oil-injected compressors are also used in stationary compressed air supply systems.
- An oil-injected screw compressor essentially consists of a compressor unit with at least one pair of counter-rotating and interlocking cylindrical compressor screws.
- This compressor screw assembly serves to generate compressed air in which air drawn in from one side from the atmosphere is converted into compressed air by continuous compression, which leaves the compressor unit via a spring-returned outlet valve.
- the drive of the compressor screw assembly is carried out via a sealed out of the compressor unit to the outside drive shaft by means of a flanged here motor, usually an electric motor.
- the oil separator device is required to relieve the oil-laden compressed air of the oil, so that oil-free compressed air is available on the output side.
- the ⁇ labscheiderinnate usually consists essentially of an oil separator, which operates in a conventional manner by the principle of gravity. The oil, which separates from the oily compressed air rising in the oil separator, is collected in the oil reservoir. The ascended in the oil separator, already partially oil-free compressed air is subsequently usually fed to a cartridge-like fine separator and then leaves the ⁇ labscheider recognized via an output side arranged pressure-holding valve.
- the required high oil temperature is usually achieved quickly by a valve disposed in the oil control valve.
- the control valve regulates continuously and according to the operating conditions of the compressor divides the oil volume flow required for cooling in such a way between a radiator and bypass line, that always sets the same oil temperature.
- the compressor and the radiator of the oil circuit associated fan is operated according to the prior art with maximum power by a rigid connection to the drive motor of the compressor unit. Only with separately driven radiator fan systems, a simple start / stop operation is possible to prevent the cooling of the oil circuit at low oil temperature.
- the usually permanent and run at rated speed fan is used to maintain the operation of the compressor unit even in the worst case at high ambient temperatures, so that the maximum permissible oil temperature of 120 ° C is not exceeded.
- a disadvantage of this prior art is that as a result of the design of the fan to maximum requirement and maximum air flow, this is oversized in most of the time proportions of the operation of the compressor unit. This is usually a unnecessarily high Power requirement caused.
- the permanent fan drive causes a significant noise emission.
- the above-described control of the oil volume flow between radiator and bypass line causes regardless of the ambient temperature sets a predetermined control temperature in the oil reservoir. Since the maximum amount of water vapor in the ambient air significantly depends on its temperature, in this case, the level of the oil temperature is to be selected so high that even in the worst case, no condensate can fail in the compressor. As a result, the oil is exposed to increased aging. The same applies to all rubber and sealing parts of the compressor unit, which are exposed by the constant high oil temperature of a special load. Furthermore, the oil can not optimally fulfill its function as a gap seal in the actual compressor chamber when it is hot and thus less viscous, i. low viscosity, is. The volumetric efficiency drops with increasing oil temperature due to internal backflow.
- the means for controlling the oil temperature as adjusting device comprises a variable-speed drive for the fan, wherein a control device adjusts the speed of the fan as a function of the radiator from the ambient heat coming from the surrounding heat, wherein the variable-speed drive the fan wheel is provided with a constant speed connected to the drive shaft viscous coupling, which varies due to the prevailing during operation of the viscous coupling the slip and which is arranged in the flow of heated by the radiator cooling air between the latter and the fan.
- the solution according to the invention is based on the recognition that the heating of the cooling air originating from the environment is approximately constant when passing through the cooler, but the ambient temperature can fluctuate greatly, so that the final temperature of the cooling air used for cooling also depends to a considerable degree on the ambient temperature is.
- the solution according to the invention thus makes it possible to link two controlled variables for the oil temperature with each other. On the one hand indirectly the oil temperature, which heats the cooling air at the radiator accordingly, taken as a control variable; On the other hand, the ambient temperature, which defines the basic level of the cooling air temperature, also flows in as a controlled variable. By linking these two control variables, the oil temperature can also be adapted to the current ambient temperature level, whereas according to the prior art, the oil temperature always remains at a constantly high level.
- the solution according to the invention allows a fan wheel operation which is always adapted to the needs. Since so far the fan was operated at maximum power, although considered by time proportion, this would be required only occasionally, resulting in particular in the sound emission significant improvements.
- the power requirement of the fan wheel is also much lower than in a permanently operated at the maximum point fan.
- the mobile Use also has the duty cycle on the speed of the fan a significant impact. By dissipating in the stop phase of the compressor heat by cooling the compressor is used after a restart at the lowest possible speed of the fan wheel. As a result, even at low duty cycle, the necessary minimum temperature level is reached quickly and thereby emitted much less sound than in the known from the prior art solution.
- the solution according to the invention extends the maintenance intervals for oil and seals. In addition, the life of the compressor bearing is extended, resulting from the adjusted oil temperature.
- a viscous coupling connected to the drive shaft of constant speed is provided for the variable-speed drive of the fan wheel, which varies in accordance with the prevailing during operation of the viscous coupling temperatures of the slip accordingly.
- the drive shaft of the viscous coupling can be coupled in an advantageous manner with the shaft of the drive motor of the compressor unit.
- a viscous coupling in this case a conventional viscous coupling can be used, which noticeably reduces the slip with a simple bimetal from a certain temperature and also allows a soft adaptation of the slip to the temperature conditions due to the oil in the slippage space.
- control device adjusts the speed of the fan wheel in response to the determined by means of a temperature measuring device from the radiator to the heat coming from the environment cooling air heat.
- a temperature measuring device from the radiator to the heat coming from the environment cooling air heat.
- an electrical temperature sensor with appropriate electronics is required here.
- the measuring technology records the current ambient temperature at a suitable location.
- the control and regulation of the Lüfterradwindiere by means of inverter and drive the fan wheel which may for example be designed as a three-phase motor.
- the temperature measuring device or the viscous coupling is to be arranged according to the invention in the flow of heated by the radiator cooling air between this and the fan. At this point, a space-optimal accommodation can be realized. At the same time indirectly at this point the oil temperature, which heats the cooling air at the radiator, and on the other hand, the influence of the ambient temperature detectable and directly by a temperature sensor or indirectly by a corresponding temperature influence of the viscous coupling in a demand-driven speed control for the fan can be implemented.
- the cooler in addition to the above-described cooling of the oil circuit, can also be used for aftercooling of the compressed air leaving the oil separator device of the compressor. Thus eliminates a possibly separately provided for this cooler.
- the figure shows a schematic representation of an oil-injected compressor with means for controlling the oil temperature, here including a viscous coupling.
- an oil-injected compressor (screw compressor) essentially consists of a compressor unit 1, which is driven by an electric motor 2.
- an oil circuit 3 injected oil for lubrication.
- the oil required for lubrication, cooling and sealing purposes passes partially into the compressed air leaving the compressor unit 1 on the output side.
- the compressor unit 1 is followed by an oil separator 4.
- the oil reservoir 5 passes from the ⁇ labscheider issued 4 from the incoming oily compressed air by gravity separated oil, so that the output side of the oil separator 4 via the compressed air line 6 effluent compressed air is substantially free of oil.
- the compressed air line 6 is guided via a cooler 7 for further cooling of the compressed air.
- the cooler 7 also serves to cool the oil circulating in the oil circuit 3.
- the radiator 7 is supplied with the heated oil originating from the oil reservoir 5, which is again injected into the compressor unit 1 in a cooled manner by the radiator 7.
- Cooling air is drawn from the environment through the radiator 7 via a fan wheel 9 arranged adjacent to the radiator 7.
- the fan 9 is driven via the electric motor 2 with interposed viscous coupling 10.
- This arrangement forms in the oil temperature control a variable-speed drive for the fan 9, which represents the adjusting device insofar.
- the control device of the oil temperature control is embodied by the viscous coupling 10, which adjusts the rotational speed of the fan wheel 9 as a function of the heat transferred from the cooler 7 to the cooling air originating from the environment.
- the viscous coupling 10 is arranged in the region 11, which is suitable for detecting the ambient air heated by the oil temperature.
- the viscous coupling 10 varies due to the prevailing in this area 11 temperatures, the slip and thus the speed of the impeller 9, which thus ensures a demand-based oil temperature control.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
- Compressor (AREA)
Abstract
Description
Die vorliegende Erfindung betrifft einen öleingespritzten Verdichter, insbesondere einen öleingespritzten mobilen Schraubenverdichter, mit einer motorbetriebenen Verdichtereinheit zur Erzeugung von Druckluft, die mit einem Ölkreislauf zur Schmierung zusammenwirkt, dessen Ölvorrat in einer nachgeschalteten Ölabscheidereinrichtung zum Trennen des Öls von der Druckluft untergebracht ist, wobei Mittel zur Öltemperaturregelung vorgesehen sind, die einen Kühler mit Lüfterrad umfassen. Ein solchen Verdichter ist aus der Druckschrift
Die vorliegende Erfindung ist neben öleingespritzten Schrauben verdichtern auch bei anderen Arten von öleingespritzten Verdichtern, wie Spiral- und Flügelzellenverdichter, verwendbar. Bei den Verdichtern der hier interessierenden Art wird mittels eines Ölkreislaufs Öl zur Schmierung in den Bereich der bewegten Verdichterbauteile sowie an deren Lagerstellen eingespritzt, um zum Einen die hier vorhandenen, sich mit hoher Geschwindigkeit drehenden Wälzlager zu schmieren, und um zum Anderen auch ein unzulässiges Aufheizen im Bereich der bewegten Verdichterbauteile in Folge von Reibung zu verhindern. Des Weiteren dient das Öl auch zum Abdichten der Luftseite gegenüber anderen Bereichen des Verdichters. Das Einsatzgebiet derartiger öleingespritzter Verdichter erstreckt sich dank der Kompaktheit vornehmlich auf mobile Anwendungen im Schienenfahrzeugbau oder auch im Bereich des Nutzfahrzeugbaus. Daneben werden öleingespritzte Verdichter auch im Rahmen stationärer Druckluftversorgungsanlagen eingesetzt.The present invention is useful in other types of oil-injected compressors, such as scroll and vane compressors, in addition to oil-injected screw compressors. In the compressors of interest here type oil is injected by means of an oil circuit for lubrication in the field of moving compressor components and at their bearings in order to lubricate the one here existing, rotating at high speed bearings, and on the other also an inadmissible heating to prevent in the field of moving compressor components as a result of friction. Furthermore, the oil also serves to seal the air side against other areas of the compressor. The field of application of such oil-injected compressors extends thanks to the compactness mainly to mobile applications in rail vehicle construction or in the field of commercial vehicle construction. In addition, oil-injected compressors are also used in stationary compressed air supply systems.
Aus dem allgemeinen Stand der Technik gehen öleingespritzte Verdichter, wie öleingespritzte Schraubenverdichter, in verschiedenen Varianten hervor. Ein öleingespritzter Schraubenverdichter besteht im Wesentlichen aus einer Verdichtereinheit mit mindestens einem Paar von gegenläufig zueinander sich drehenden und ineinander verzahnten, walzenförmigen Verdichterschrauben. Diese Verdichterschraubenanordnung dient der Erzeugung von Druckluft, in dem von einer Seite her von der Atmosphäre angesaugte Luft durch kontinuierliche Verdichtung in Druckluft umgewandelt wird, welche die Verdichtereinheit über ein federrückgestelltes Auslassventil verlässt. Der Antrieb der Verdichterschraubenanordnung erfolgt dabei über eine abgedichtet aus der Verdichtereinheit nach außen geführte Antriebswelle mittels eines hier angeflanschten Motors, meist eines Elektromotors. Zum Schmieren, Abdichten und Kühlen der durch den Kompressionsprozess thermisch stark beanspruchten Verdichtereinheit ist diese mit einem Ölkreislauf verbunden, welcher ausgehend von einem Ölvorrat das Öl an die Verdichterschraubenanordnung sowie auch an die zugeordneten Wälzlager liefert. Das hier eingespritzte Öl verlässt diesen Wirkbereich in Richtung des Ölvorrats, der sich innerhalb der dem Ölkreislauf nachgeschalteten Ölabscheidereinrichtung befindet. Die Ölabscheidereinrichtung ist erforderlich, um die öldurchsetzte Druckluft wieder von dem Öl zu befreien, so dass ölfreie Druckluft ausgangsseitig zur Verfügung steht. Die Ölabscheidereinrichtung besteht gewöhnlich im Wesentlichen aus einem Ölabscheider, der in an sich bekannter Weise nach dem Schwerkraftprinzip arbeitet. Das Öl, welches sich von der im Ölabscheider aufsteigenden ölhaltigen Druckluft trennt, wird im Ölvorrat gesammelt. Die im Ölabscheider aufgestiegene, bereits teilweise ölfreie Druckluft wird nachfolgend meist einem patronenartigen Feinabscheider zugeführt und verlässt anschließend die Ölabscheidereinrichtung über ein ausgangsseitig angeordnetes Druckhalteventil.From the general state of the art, oil-injected compressors, such as oil-injected screw compressors, emerge in different variants. An oil-injected screw compressor essentially consists of a compressor unit with at least one pair of counter-rotating and interlocking cylindrical compressor screws. This compressor screw assembly serves to generate compressed air in which air drawn in from one side from the atmosphere is converted into compressed air by continuous compression, which leaves the compressor unit via a spring-returned outlet valve. The drive of the compressor screw assembly is carried out via a sealed out of the compressor unit to the outside drive shaft by means of a flanged here motor, usually an electric motor. For lubrication, sealing and cooling of the compression unit thermally highly stressed compressor unit this is connected to an oil circuit, which supplies starting from an oil reservoir, the oil to the compressor screw assembly and also to the associated bearings. The oil injected here leaves this effective range in the direction of the oil supply, which is located within the oil circuit downstream Ölabscheidereinrichtung. The oil separator device is required to relieve the oil-laden compressed air of the oil, so that oil-free compressed air is available on the output side. The Ölabscheidereinrichtung usually consists essentially of an oil separator, which operates in a conventional manner by the principle of gravity. The oil, which separates from the oily compressed air rising in the oil separator, is collected in the oil reservoir. The ascended in the oil separator, already partially oil-free compressed air is subsequently usually fed to a cartridge-like fine separator and then leaves the Ölabscheidereinrichtung via an output side arranged pressure-holding valve.
Für einen sicheren Betrieb von öleingespritzten Verdichtern ist insbesondere bei hoher und feuchter Umgebungstemperatur eine entsprechend hohe Öltemperatur erforderlich, um Kondensatausfall mit dessen schädigenden Auswirkungen im Inneren des Verdichters zu unterbinden. Die erforderlich hohe Öltemperatur wird üblicherweise durch ein im Ölkreislauf angeordnetes Regelventil rasch erreicht. Das Regelventil regelt stufenlos und teilt entsprechend den Betriebsbedingungen des Verdichters den zur Kühlung benötigten Ölvolumenstrom derart zwischen einer Kühler- und Bypassleitung auf, dass sich stets die gleiche Öltemperatur einstellt. Das dem Verdichter sowie dem Kühler des Ölkreislauf zugehörige Lüfterrad wird nach dem Stand der Technik mit maximaler Leistung betrieben, indem eine starre Verbindung zum Antriebsmotor der Verdichtereinheit besteht. Lediglich bei gesondert angetriebenen Kühler-Lüfter-Systemen ist ein einfacher Start-/Stop-Betrieb möglich, um bei niedriger Öltemperatur die Kühlung des Ölkreislaufs zu unterbinden. Der in der Regel permanente und mit Nenndrehzahl betriebene Lüfter dient dazu, den Betrieb der Verdichtereinheit auch im ungünstigsten Fall bei hohen Umgebungstemperaturen aufrecht zu erhalten, so dass die maximal zulässige Öltemperatur von 120 °C nicht überschritten wird.For a safe operation of oil-injected compressors especially at high and humid ambient temperature, a correspondingly high oil temperature is required to prevent condensate failure with its damaging effects inside the compressor. The required high oil temperature is usually achieved quickly by a valve disposed in the oil control valve. The control valve regulates continuously and according to the operating conditions of the compressor divides the oil volume flow required for cooling in such a way between a radiator and bypass line, that always sets the same oil temperature. The compressor and the radiator of the oil circuit associated fan is operated according to the prior art with maximum power by a rigid connection to the drive motor of the compressor unit. Only with separately driven radiator fan systems, a simple start / stop operation is possible to prevent the cooling of the oil circuit at low oil temperature. The usually permanent and run at rated speed fan is used to maintain the operation of the compressor unit even in the worst case at high ambient temperatures, so that the maximum permissible oil temperature of 120 ° C is not exceeded.
Nachteilig bei diesem Stand der Technik ist, dass das in Folge der Auslegung des Lüfters auf Maximalanforderung und maximalen Luftstrom, dieser in den meisten Zeitanteilen des Betriebs der Verdichtereinheit überdimensioniert ist. Hierdurch wird ein meist unnötig hoher Leistungsbedarf verursacht. Darüber hinaus verursacht der permanente Lüfterantrieb eine erhebliche Schallemission.A disadvantage of this prior art is that as a result of the design of the fan to maximum requirement and maximum air flow, this is oversized in most of the time proportions of the operation of the compressor unit. This is usually a unnecessarily high Power requirement caused. In addition, the permanent fan drive causes a significant noise emission.
Weiterhin führt die vorstehend beschriebene Regelung des Ölvolumenstroms zwischen Kühler und Bypass-Leitung dazu, dass sich unabhängig von der Umgebungstemperatur eine festgelegte Regeltemperatur im Ölvorrat einstellt. Da die maximale Menge von Wasserdampf in der Umgebungsluft maßgeblich von dessen Temperatur abhängt, ist in diesem Fall das Niveau der Öltemperatur so hoch zu wählen, dass auch im ungünstigen Fall kein Kondensat im Verdichter ausfallen kann. Dadurch ist das Öl einer erhöhten Alterung ausgesetzt. Gleiches gilt auch für sämtliche Gummi- und Dichtteile der Verdichtereinheit, welche durch die konstant hohe Öltemperatur einer besonderen Belastung ausgesetzt sind. Des Weiteren kann das Öl seine Funktion als Spaltabdichtung im eigentlichen Verdichterraum nicht optimal erfüllen, wenn dieses heiß und damit niederviskoser, d.h. dünnflüssiger, ist. Der volumetrische Wirkungsgrad fällt mit steigender Öltemperatur aufgrund von internen Rückströmungen ab.Furthermore, the above-described control of the oil volume flow between radiator and bypass line causes regardless of the ambient temperature sets a predetermined control temperature in the oil reservoir. Since the maximum amount of water vapor in the ambient air significantly depends on its temperature, in this case, the level of the oil temperature is to be selected so high that even in the worst case, no condensate can fail in the compressor. As a result, the oil is exposed to increased aging. The same applies to all rubber and sealing parts of the compressor unit, which are exposed by the constant high oil temperature of a special load. Furthermore, the oil can not optimally fulfill its function as a gap seal in the actual compressor chamber when it is hot and thus less viscous, i. low viscosity, is. The volumetric efficiency drops with increasing oil temperature due to internal backflow.
Durch den in mobilen Anwendungen des öleingespritzten Verdichters auftretenden Start-/Stop-Betrieb und der oftmals niederen Einschaltdauer wird der Nachteil einer Maximalauslegung der Kühlung des Ölkreislaufs mit den vorstehend genannten Nachteilen nochmals verstärkt, da durch zwischenzeitliche Abkühleffekte in den Stopphasen die Kühlluft im Betrieb dann oft gar nicht oder nur wenig benötigt wird und teilweise sogar kontraproduktiv ist. Bei extrem kalten Umgebungstemperaturen verhindert die komplette Lüfterleistung vom Start weg ein geeignetes Anwärmen des Ölkreislaufs. Das führt zu einem recht hohen hydraulischen Widerstand im Kühler, so dass beim Umschalten des herkömmlichen Regelventils von der Bypassleitung auf die Kühlerleitung der Ölvolumenstrom zusammenbrechen und der Verdichter Schaden nehmen kann.Due to the occurring in mobile applications of the oil-injected compressor start / stop operation and often low duty cycle of the disadvantage of a maximum design of the cooling of the oil circuit with the disadvantages mentioned above is further enhanced, since by interim cooling effects in the stop phases, the cooling air during operation then often not at all or only little needed and sometimes even counterproductive. At extremely cold ambient temperatures, the complete fan performance prevents proper heating of the oil circuit from the start. This leads to a rather high hydraulic resistance in the radiator, so that when switching the conventional control valve from the bypass line to the radiator line, the oil volume flow collapse and the compressor can be damaged.
Es ist daher die Aufgabe der vorliegenden Erfindung, einen öleingespritzten Verdichter der vorstehend beschriebenen Art dahingehend weiter zu verbessern, dass dessen Mittel zur Öltemperaturregelung eine bedarfsgerechte, effiziente Kühlung bei vertretbarem gerätetechnischen Aufwand sicherstellen.It is therefore the object of the present invention to further improve an oil-injected compressor of the type described above so that its means for controlling the oil temperature ensure efficient, efficient cooling with justifiable technical equipment.
Die Aufgabe wird ausgehend von einem öleingespritzten Verdichter gemäß dem Oberbegriff von Anspruch 1 in Verbindung mit dessen kennzeichnenden Merkmalen gelöst. Die nachfolgenden abhängigen Ansprüche geben vorteilhafte Weiterbildungen der Erfindung wieder.The object is achieved on the basis of an oil-injected compressor according to the preamble of claim 1 in conjunction with its characterizing features. The following dependent claims give advantageous developments of the invention.
Die Erfindung schließt die technische Lehre ein, dass die Mittel zur Öltemperaturregelung als Stelleinrichtung einen drehzahlvariablen Antrieb für das Lüfterrad umfassen, wobei eine Regeleinrichtung die Drehzahl des Lüfterrades in Abhängigkeit der vom Kühler an die aus der Umgebung stammenden Kühlluft übertragenden Wärme anpasst, wobei zum drehzahlvariablen Antrieb des Lüfterrades eine mit der Antriebswelle konstanter Drehzahl verbundene Viskokupplung vorgesehen, welche aufgrund der im Betrieb der Viskokupplung vorherrschenden Temperaturen den Schlupf entsprechend variiert und welche im Strom der durch den Kühler aufgeheizten Kühlluft zwischen diesem und dem Lüfterrad angeordnet ist.The invention includes the technical teaching that the means for controlling the oil temperature as adjusting device comprises a variable-speed drive for the fan, wherein a control device adjusts the speed of the fan as a function of the radiator from the ambient heat coming from the surrounding heat, wherein the variable-speed drive the fan wheel is provided with a constant speed connected to the drive shaft viscous coupling, which varies due to the prevailing during operation of the viscous coupling the slip and which is arranged in the flow of heated by the radiator cooling air between the latter and the fan.
Die erfindungsgemäße Lösung geht von der Erkenntnis aus, dass die Erwärmung der von der Umgebung stammenden Kühlluft beim Passieren des Kühlers zwar in etwa konstant ist, die Umgebungstemperatur jedoch stark schwanken kann, so dass die Endtemperatur der zur Kühlung verwendeten Kühlluft auch in erheblichem Maße abhängig von der Umgebungstemperatur ist. Die erfindungsgemäße Lösung gestattet es also, zwei Regelgrößen für die Öltemperatur miteinander zu verknüpfen. Zum Einen wird indirekt die Öltemperatur, welche die Kühlluft am Kühler entsprechend erwärmt, als Regelgröße hergenommen; zum Anderen fließt auch die Umgebungstemperatur, welche das Grundniveau der Kühllufttemperatur festlegt, als Regelgröße mit ein. Durch diese Verknüpfung beider Regelgrößen lässt sich die Öltemperatur auch an das aktuelle Umgebungstemperaturniveau anpassen, während nach dem Stand der Technik die Öltemperatur stets auf einem konstant hohen Niveau verbleibt. So ermöglicht die erfindungsgemäße Lösung einen stets bedarfsgerecht angepassten Lüfterradbetrieb. Da bisher das Lüfterrad mit maximaler Leistung betrieben wurde, obwohl nach Zeitanteil betrachtet diese nur gelegentlich erforderlich wäre, ergeben sich insbesondere bei der Schallemission erhebliche Verbesserungen. Auch der Leistungsbedarf des Lüfterrades ist insgesamt weit geringer als bei einem dauerhaft am Maximalpunkt betriebenen Lüfterrad. Insbesondere im mobilen Einsatz hat auch die Einschaltdauer auf die Drehzahl des Lüfterrades einen erheblichen Einfluss. Durch die in der Stopphase des Verdichters abgeführte Wärme durch Auskühlung wird der Verdichter nach einem Neustart bei möglichst geringer Drehzahl des Lüfterrades eingesetzt. Dadurch wird auch bei niedriger Einschaltdauer das notwendige Mindesttemperaturniveau zügig erreicht und dabei deutlich weniger Schall emittiert als bei der aus dem Stand der Technik bekannten Lösung. Des Weiteren verlängert die erfindungsgemäße Lösung die Wartungsintervalle für Öl und Dichtungen. Darüber hinaus verlängert sich auch die Lebensdauer der Verdichterlager, was aus der angepassten Öltemperatur resultiert.The solution according to the invention is based on the recognition that the heating of the cooling air originating from the environment is approximately constant when passing through the cooler, but the ambient temperature can fluctuate greatly, so that the final temperature of the cooling air used for cooling also depends to a considerable degree on the ambient temperature is. The solution according to the invention thus makes it possible to link two controlled variables for the oil temperature with each other. On the one hand indirectly the oil temperature, which heats the cooling air at the radiator accordingly, taken as a control variable; On the other hand, the ambient temperature, which defines the basic level of the cooling air temperature, also flows in as a controlled variable. By linking these two control variables, the oil temperature can also be adapted to the current ambient temperature level, whereas according to the prior art, the oil temperature always remains at a constantly high level. Thus, the solution according to the invention allows a fan wheel operation which is always adapted to the needs. Since so far the fan was operated at maximum power, although considered by time proportion, this would be required only occasionally, resulting in particular in the sound emission significant improvements. The power requirement of the fan wheel is also much lower than in a permanently operated at the maximum point fan. Especially in the mobile Use also has the duty cycle on the speed of the fan a significant impact. By dissipating in the stop phase of the compressor heat by cooling the compressor is used after a restart at the lowest possible speed of the fan wheel. As a result, even at low duty cycle, the necessary minimum temperature level is reached quickly and thereby emitted much less sound than in the known from the prior art solution. Furthermore, the solution according to the invention extends the maintenance intervals for oil and seals. In addition, the life of the compressor bearing is extended, resulting from the adjusted oil temperature.
Erfindungsgemäß ist zum drehzahlvariablen Antrieb des Lüfterrades eine mit der Antriebswelle konstanter Drehzahl verbundene Viskokupplung vorgesehen, welche aufgrund der im Betrieb der Viskokupplung vorherrschenden Temperaturen der Schlupf entsprechend variiert. Die Antriebswelle der Viskokupplung kann in vorteilhafter Weise mit der Welle des Antriebsmotors der Verdichtereinheit gekoppelt sein. Somit wird ein weiterer Antrieb hierfür eingespart. Als Viskokupplung kann hierbei eine herkömmliche Viskokupplung eingesetzt werden, welche mit einem einfachen Bimetall ab einer bestimmten Temperatur den Schlupf spürbar verringert und zudem durch das im Schlupfraum befindliche Öl eine weiche Anpassung des Schlupfes an die Temperaturgegebenheiten zulässt.According to the invention, a viscous coupling connected to the drive shaft of constant speed is provided for the variable-speed drive of the fan wheel, which varies in accordance with the prevailing during operation of the viscous coupling temperatures of the slip accordingly. The drive shaft of the viscous coupling can be coupled in an advantageous manner with the shaft of the drive motor of the compressor unit. Thus, a further drive is saved for this. As a viscous coupling in this case a conventional viscous coupling can be used, which noticeably reduces the slip with a simple bimetal from a certain temperature and also allows a soft adaptation of the slip to the temperature conditions due to the oil in the slippage space.
Alternativ hierzu ist es jedoch auch möglich, dass die Regeleinrichtung die Drehzahl des Lüfterrades in Abhängigkeit der mittels einer Temperaturmesseinrichtung ermittelten vom Kühler an die aus der Umgebung stammenden Kühlluft übertragenen Wärme anpasst. In Abweichung von der vorstehend beschriebenen Variante ist hier ein elektrischer Temperatursensor mit entsprechender Elektronik erforderlich. Durch die Messtechnik wird die aktuelle Umgebungstemperatur an geeigneter Stelle erfasst. Die Steuerung und Regelung der Lüfterraddrehzahl erfolgt mittels Umrichter und Antrieb des Lüfterrades, der beispielsweise als Drehstrommotor ausgeführt sein kann.Alternatively, however, it is also possible that the control device adjusts the speed of the fan wheel in response to the determined by means of a temperature measuring device from the radiator to the heat coming from the environment cooling air heat. In deviation from the variant described above, an electrical temperature sensor with appropriate electronics is required here. The measuring technology records the current ambient temperature at a suitable location. The control and regulation of the Lüfterraddrehzahl by means of inverter and drive the fan wheel, which may for example be designed as a three-phase motor.
Anstelle des Drehzahlmotors ist es jedoch auch denkbar, für den drehzahlvariablen Antrieb des Lüfterrades einen Hydromotor einzusetzen, welcher von einer vorgeschalteten Hydropumpe mit Druckmittel drehzahlvariabel beaufschlagbar ist. In beiden Fällen entfällt das beim Stand der Technik gebräuchliche Regelventil zur Regelung der Öltemperatur.Instead of the speed motor, however, it is also conceivable to use a hydraulic motor for the variable-speed drive of the fan wheel, which is acted upon by a hydraulic pump upstream of pressure medium variable speed. In both cases eliminates the usual in the prior art control valve for controlling the oil temperature.
Die Temperaturmesseinrichtung bzw. die Viskokupplung ist erfindungsgemäß im Strom der durch den Kühler aufgeheizten Kühlluft zwischen diesem und dem Lüfterrad anzuordnen. An dieser Stelle ist eine bauraumoptimale Unterbringung realisierbar. Gleichzeitig ist an dieser Stelle indirekt die Öltemperatur, welche die Kühlluft am Kühler entsprechend erwärmt, und zum Anderen die Beeinflussung durch die Umgebungstemperatur erfassbar und direkt durch einen Temperatursensor oder indirekt durch eine entsprechende Temperaturbeeinflussung der Viskokupplung in eine bedarfsgerechte Drehzahlregelung für das Lüfterrad umsetzbar.The temperature measuring device or the viscous coupling is to be arranged according to the invention in the flow of heated by the radiator cooling air between this and the fan. At this point, a space-optimal accommodation can be realized. At the same time indirectly at this point the oil temperature, which heats the cooling air at the radiator, and on the other hand, the influence of the ambient temperature detectable and directly by a temperature sensor or indirectly by a corresponding temperature influence of the viscous coupling in a demand-driven speed control for the fan can be implemented.
Gemäß einer weiteren, die Erfindung verbessernden Maßnahme ist vorgesehen, dass der Kühler neben der vorstehend beschriebenen Kühlung des Ölkreislaufs auch für eine Nachkühlung der die Ölabscheidereinrichtung des Verdichters verlassenden Druckluft nutzbar ist. Somit entfällt ein hierfür ggf. separat vorzusehender Kühler.According to a further measure improving the invention, it is provided that, in addition to the above-described cooling of the oil circuit, the cooler can also be used for aftercooling of the compressed air leaving the oil separator device of the compressor. Thus eliminates a possibly separately provided for this cooler.
Weitere die Erfindung verbessernde Maßnahmen werden nachstehend gemeinsam mit der Beschreibung eines bevorzugten Ausführungsbeispiels der Erfindung anhand der einzigen Figur näher dargestellt.Further measures improving the invention will be described in more detail below together with the description of a preferred embodiment of the invention with reference to the single figure.
Die Figur zeigt eine schematische Darstellung eines öleingespritzten Verdichters mit Mitteln zur Öltemperaturregelung, hier unter Einbeziehung einer Viskokupplung.The figure shows a schematic representation of an oil-injected compressor with means for controlling the oil temperature, here including a viscous coupling.
Gemäß Figur besteht ein öleingespritzter Verdichter (Schraubenverdichter) im Wesentlichen aus einer Verdichtereinheit 1, welche mit einem Elektromotor 2 angetrieben wird. Im Bereich der die Verdichtereinheit 1 bildenden Verdichterschraubenanordnung wird aus einem Ölkreislauf 3 Öl zur Schmierung eingespritzt. Das zu Schmierungs-, Kühlungs- und Dichtungszwecken erforderliche Öl gelangt dabei teilweise in die die Verdichtereinheit 1 ausgangsseitig verlassende Druckluft. Zum Trennen des Öls und der Druckluft ist der Verdichtereinheit 1 eine Ölabscheidereinrichtung 4 nachgeschaltet.According to FIG. 1, an oil-injected compressor (screw compressor) essentially consists of a compressor unit 1, which is driven by an
Die Ölabscheidereinrichtung 4 enthält einen Ölvorrat 5 für den Ölkreislauf 3. In den Ölvorrat 5 gelangt das von der Ölabscheidereinrichtung 4 aus der einströmenden ölhaltigen Druckluft per Schwerkraft abgesonderte Öl, so dass die ausgangsseitig der Ölabscheidereinrichtung 4 über die Druckluftleitung 6 abströmende Druckluft im Wesentlichen ölfrei ist. Die Druckluftleitung 6 ist über einen Kühler 7 zum weiteren Abkühlen der Druckluft geführt. Gleichzeitig dient der Kühler 7 auch der Kühlung des im Ölkreislauf 3 zirkulierenden Öls. Über eine Ölleitung 8 wird dem Kühler 7 das aus dem Ölvorrat 5 stammende aufgeheizte Öl zugeführt, welches durch den Kühler 7 entsprechend gekühlt wieder in die Verdichtereinheit 1 eingespritzt wird.In the oil reservoir 5 passes from the Ölabscheidereinrichtung 4 from the incoming oily compressed air by gravity separated oil, so that the output side of the oil separator 4 via the
Über ein benachbart zum Kühler 7 angeordnetes Lüfterrad 9 wird Kühlluft aus der Umgebung durch den Kühler 7 gesaugt. Das Lüfterrad 9 wird über den Elektromotor 2 mit zwischengeschalteter Viskokupplung 10 angetrieben.Cooling air is drawn from the environment through the radiator 7 via a fan wheel 9 arranged adjacent to the radiator 7. The fan 9 is driven via the
Diese Anordnung bildet bei der Öltemperaturregelung einen drehzahlvariablen Antrieb für das Lüfterrad 9, welche insoweit die Stelleinrichtung darstellt. Die Regeleinrichtung der Öltemperaturregelung wird durch die Viskokupplung 10 verkörpert, welche die Drehzahl des Lüfterrades 9 in Abhängigkeit der vom Kühler 7 an die aus der Umgebung stammenden Kühlluft übertragenen Wärme anpasst. Zu diesem Zwecke ist die Viskokupplung 10 im Bereich 11 angeordnet, der geeignet ist zur Erfassung der von der Öltemperatur erhitzten Umgebungsluft. Die Viskokupplung 10 variiert aufgrund der in diesem Bereich 11 vorherrschenden Temperaturen, den Schlupf und damit die Drehzahl des Lüfterrades 9, welche somit eine bedarfsgerechte Öltemperaturregelung gewährleistet.This arrangement forms in the oil temperature control a variable-speed drive for the fan 9, which represents the adjusting device insofar. The control device of the oil temperature control is embodied by the viscous coupling 10, which adjusts the rotational speed of the fan wheel 9 as a function of the heat transferred from the cooler 7 to the cooling air originating from the environment. For this purpose, the viscous coupling 10 is arranged in the region 11, which is suitable for detecting the ambient air heated by the oil temperature. The viscous coupling 10 varies due to the prevailing in this area 11 temperatures, the slip and thus the speed of the impeller 9, which thus ensures a demand-based oil temperature control.
Die Erfindung ist nicht beschränkt auf das vorstehend beschriebene bevorzugte Ausführungsbeispiel. So sind auch Abweichungen hiervon denkbar, die dem Schutzbereich der nachfolgenden Ansprüche unterfallen.The invention is not limited to the preferred embodiment described above. Thus, deviations from this are also conceivable, which fall under the scope of the following claims.
- 11
- Verdichtereinheitcompressor unit
- 22
- Elektromotorelectric motor
- 33
- ÖlkreislaufOil circuit
- 44
- Ölabscheidereinrichtungoil separator
- 55
- Ölvorratoil supply
- 66
- DruckluftleitungCompressed air line
- 77
- Kühlercooler
- 88th
- Ölleitungoil line
- 99
- Lüfterradfan
- 1010
- Viskokupplungviscous coupling
- 1111
- Bereich (an der Viskokupplung)Range (at the viscous coupling)
Claims (6)
- An oil-injected compressor, in particular an oil-injected mobile screw compressor, with a motor-driven compressor unit (1) for generating compressed air, which for lubrication interacts with an oil circuit (3), the oil reservoir (5) of which is accommodated in a downstream oil separator device (4) for separating the oil from the compressed air, means comprising a cooler (7) with fan impeller (9) and a variable-speed drive for the fan impeller (9) as adjusting device being provided for regulating the oil temperature, a regulating device adjusting the speed of the fan impeller (9) as a function of the heat transmitted to the ambient cooling air by the cooler (7), characterized in that a viscous drive coupling (10), which is connected to the constant-speed drive and which varies the slip according to the temperatures prevailing in the area (11) of the viscous drive coupling (10), and which is arranged in the flow of cooling air heated by the cooler (7) between this and the fan impeller (9), is provided for the variable-speed drive of the fan impeller (9).
- The oil-injected compressor as claimed in claim 1, characterized in that the regulating device adjusts the speed of the fan impeller (9) as a function of the heat transmitted to the ambient cooling air by the cooler (7), determined by means of a temperature measuring device, according to a predetermined reference temperature.
- The oil-injected compressor as claimed in claim 2, characterized in that the variable-speed drive for the fan impeller (9) is embodied as an electric motor (2).
- The oil-injected compressor as claimed in claim 2, characterized in that the variable-speed drive for the fan impeller (9) is embodied as a hydraulic motor, the speed of which can be varied by an upstream hydraulic pump.
- The oil-injected compressor as claimed in claim 3, characterized in that the viscous drive coupling (10) is driven via the shaft of the electric motor (2) of the compressor unit (1).
- The oil-injected compressor as claimed in any one of the preceding claims, characterized in that in addition to cooling the oil circuit (3) the cooler (7) also undertakes secondary cooling of the compressed air leaving the oil separator device (4).
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102005033084A DE102005033084B4 (en) | 2005-07-15 | 2005-07-15 | Oil-injected compressor with means for oil temperature control |
| PCT/EP2006/006903 WO2007009669A2 (en) | 2005-07-15 | 2006-07-14 | Oil-injected compressor with means for oil temperature regulation |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| EP1907704A2 EP1907704A2 (en) | 2008-04-09 |
| EP1907704B1 true EP1907704B1 (en) | 2009-06-17 |
Family
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| EP06754724A Not-in-force EP1907704B1 (en) | 2005-07-15 | 2006-07-14 | Oil-injected compressor with means for oil temperature regulation |
Country Status (6)
| Country | Link |
|---|---|
| US (1) | US20080206085A1 (en) |
| EP (1) | EP1907704B1 (en) |
| JP (1) | JP2009501290A (en) |
| AT (1) | ATE434133T1 (en) |
| DE (2) | DE102005033084B4 (en) |
| WO (1) | WO2007009669A2 (en) |
Families Citing this family (16)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP4885077B2 (en) * | 2007-07-03 | 2012-02-29 | 株式会社日立産機システム | Oil-free screw compressor |
| US8801395B2 (en) * | 2008-06-16 | 2014-08-12 | Gardner Denver, Inc. | Startup bypass system for a screw compressor |
| DE202008012380U1 (en) * | 2008-09-18 | 2010-02-11 | Oerlikon Leybold Vacuum Gmbh | vacuum pump |
| JP5410123B2 (en) | 2009-03-13 | 2014-02-05 | 株式会社日立産機システム | air compressor |
| DE102011014961A1 (en) * | 2011-03-24 | 2012-09-27 | Rotorcomp Verdichter Gmbh | Screw compressor system |
| DE102013113555A1 (en) * | 2013-12-05 | 2015-06-11 | Knorr-Bremse Systeme für Schienenfahrzeuge GmbH | Compressor system and method for operating the compressor system depending on the operating state of the rail vehicle |
| DE102013020533A1 (en) * | 2013-12-12 | 2015-07-02 | Gea Refrigeration Germany Gmbh | compressor |
| DE102014101113A1 (en) * | 2014-01-30 | 2015-07-30 | Pfeiffer Vacuum Gmbh | vacuum pump |
| JP6325336B2 (en) * | 2014-05-15 | 2018-05-16 | ナブテスコ株式会社 | Air compressor unit for vehicles |
| DE102016011431A1 (en) | 2016-09-21 | 2018-03-22 | Knorr-Bremse Systeme für Nutzfahrzeuge GmbH | Screw compressor for a commercial vehicle |
| DE102016011439A1 (en) * | 2016-09-21 | 2018-03-22 | Knorr-Bremse Systeme für Nutzfahrzeuge GmbH | Screw compressor system for a commercial vehicle |
| DE102017107933A1 (en) * | 2017-04-12 | 2018-10-18 | Knorr-Bremse Systeme für Nutzfahrzeuge GmbH | Compressor system with adjustable and / or controllable temperature monitoring device |
| CA3016521A1 (en) * | 2017-09-06 | 2019-03-06 | Joy Global Surface Mining Inc | Lubrication system for a compressor |
| CN107947469A (en) * | 2017-12-21 | 2018-04-20 | 盐城中德劲博机电有限责任公司 | Screw air compressor cooling structure |
| AU2021202410A1 (en) | 2020-04-21 | 2021-11-11 | Joy Global Surface Mining Inc | Lubrication system for a compressor |
| CN113833660B (en) * | 2021-10-18 | 2023-04-25 | 珠海凌达压缩机有限公司 | Oil supply assembly, compressor and control method |
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| GB867965A (en) * | 1959-07-31 | 1961-05-10 | Schwitzer Corp | A fluid coupling |
| GB2017216B (en) * | 1978-03-13 | 1982-10-27 | Imi Fluidair Ltd | Rotary positive-displacement fluid-machines |
| US4868437A (en) * | 1988-07-15 | 1989-09-19 | Siemens Energy & Automation, Inc. | Temperature activated cooling fan assembly |
| GB2266950B (en) * | 1992-04-24 | 1995-11-08 | Ingersoll Rand Co | Apparatus for and method of inhibiting formation of frozen condensate in a fluid system |
| JPH06213186A (en) * | 1993-01-14 | 1994-08-02 | Hitachi Ltd | Oil temperature adjusting device for oil-cooled rotary compressor |
| GB2367333B (en) * | 2000-09-25 | 2002-12-11 | Compair Uk Ltd | Improvements in variable speed oil-injected screw compressors |
| US6725812B1 (en) * | 2000-12-01 | 2004-04-27 | Borgwarner, Inc. | Water pump driven by viscous coupling |
| BE1013865A3 (en) * | 2000-12-06 | 2002-10-01 | Atlas Copco Airpower Nv | Method for controlling a compressor installation. |
| WO2002084124A1 (en) * | 2001-04-17 | 2002-10-24 | Tm.C. S.P.A. Termomeccanica Compressori | Screw compressor unit with incorporated oil cooling |
| DE10156180B4 (en) * | 2001-11-15 | 2015-10-15 | Oerlikon Leybold Vacuum Gmbh | Cooled screw vacuum pump |
| DE10156179A1 (en) * | 2001-11-15 | 2003-05-28 | Leybold Vakuum Gmbh | Cooling a screw vacuum pump |
| BE1014611A3 (en) * | 2002-02-08 | 2004-01-13 | Atlas Copco Airpower Nv | Method for oil return of driving in an oil injected screw compressor and thus controlled screw compressor. |
| US20040244393A1 (en) * | 2003-04-18 | 2004-12-09 | Ingersoll-Rand Company | Variable speed compressor cooling system |
-
2005
- 2005-07-15 DE DE102005033084A patent/DE102005033084B4/en not_active Expired - Fee Related
-
2006
- 2006-07-14 DE DE502006004009T patent/DE502006004009D1/en active Active
- 2006-07-14 EP EP06754724A patent/EP1907704B1/en not_active Not-in-force
- 2006-07-14 US US11/995,581 patent/US20080206085A1/en not_active Abandoned
- 2006-07-14 AT AT06754724T patent/ATE434133T1/en not_active IP Right Cessation
- 2006-07-14 WO PCT/EP2006/006903 patent/WO2007009669A2/en active Application Filing
- 2006-07-14 JP JP2008520807A patent/JP2009501290A/en active Pending
Also Published As
| Publication number | Publication date |
|---|---|
| DE102005033084A1 (en) | 2007-01-18 |
| EP1907704A2 (en) | 2008-04-09 |
| ATE434133T1 (en) | 2009-07-15 |
| WO2007009669A3 (en) | 2007-04-19 |
| DE502006004009D1 (en) | 2009-07-30 |
| JP2009501290A (en) | 2009-01-15 |
| US20080206085A1 (en) | 2008-08-28 |
| WO2007009669A2 (en) | 2007-01-25 |
| DE102005033084B4 (en) | 2007-10-11 |
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