EP1907704B1 - Compresseur a injection d'huile dote de moyens de reglage de la temperature de l'huile - Google Patents

Compresseur a injection d'huile dote de moyens de reglage de la temperature de l'huile Download PDF

Info

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
Authority
EP
European Patent Office
Prior art keywords
oil
compressor
injected
speed
cooler
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.)
Not-in-force
Application number
EP06754724A
Other languages
German (de)
English (en)
Other versions
EP1907704A2 (fr
Inventor
Nils ZIEGLGÄNSBERGER
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.)
Knorr Bremse Systeme fuer Schienenfahrzeuge GmbH
Original Assignee
Knorr Bremse Systeme fuer Schienenfahrzeuge GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Knorr Bremse Systeme fuer Schienenfahrzeuge GmbH filed Critical Knorr Bremse Systeme fuer Schienenfahrzeuge GmbH
Publication of EP1907704A2 publication Critical patent/EP1907704A2/fr
Application granted granted Critical
Publication of EP1907704B1 publication Critical patent/EP1907704B1/fr
Anticipated expiration legal-status Critical
Not-in-force legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • 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
    • 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
    • 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.

Landscapes

  • 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)

Claims (6)

  1. Compresseur à injection d'huile, notamment compresseur hélicoïdal mobile à injection d'huile, comprenant un groupe ( 1 ) compresseur entraîné par un moteur pour la production d'air comprimé, qui coopère pour la lubrification avec un circuit ( 3 ) d'huile, dont la réserve ( 5 ) d'huile est logée dans un dispositif ( 4 ) séparateur d'huile en aval pour séparer l'huile de l'air comprimé, des moyens de régulation de la température de l'huile étant prévus, moyens qui comprennent un dispositif ( 7 ) de refroidissement à roue ( 9 ) de ventilateur et, comme dispositif de réglage, un entraînement à vitesse de rotation variable de la roue ( 9 ) du ventilateur, un dispositif de régulation adaptant la vitesse de rotation de la roue ( 9 ) du ventilateur en fonction de la chaleur transmise par le dispositif ( 7 ) de refroidissement à l'air de refroidissement provenant de l'atmosphère ambiante,
    caractérisé en ce qu'il est prévu, pour l'entraînement à vitesse de rotation variable de la roue ( 9 ) du ventilateur, un visco-accouplement ( 10 ) qui est relié à l'entraînement à vitesse de rotation constante, qui fait varier le glissement sur la base des températures régnant dans la partie ( 11 ) du visco-accouplement ( 10 ) et qui est disposé dans le courant de l'air de refroidissement chauffé par le dispositif ( 7 ) de refroidissement, entre celui-ci et la roue ( 9 ) du ventilateur.
  2. Compresseur à injection d'huile suivant la revendication 1 ,
    caractérisé en ce que le dispositif de régulation adapte en fonction d'une température de consigne prescrite, la vitesse de rotation de la roue ( 9 ) du ventilateur en fonction de la chaleur déterminée par un dispositif de mesure de la température et transmise par le dispositif ( 7 ) de refroidissement à l'air de refroidissement provenant de l'atmosphère ambiante.
  3. Compresseur à injection d'huile suivant la revendication 2,
    caractérisé en ce que l'entraînement à vitesse de rotation variable de la roue ( 9 ) du ventilateur est constitué à la manière d'un moteur ( 2 ) électrique.
  4. Compresseur à injection d'huile suivant la revendication 2,
    caractérisé en ce que l'entraînement à vitesse de rotation variable de la roue ( 9 ) du ventilateur est constitué à la manière d'un moteur hydraulique qui peut être alimenté à vitesse de rotation variable par une pompe hydraulique montée en amont.
  5. Compresseur à injection d'huile suivant la revendication 3,
    caractérisé en ce que l'entraînement du visco-accouplement ( 10 ) s'effectue par l'arbre du moteur ( 2 ) électrique du groupe ( 1 ) compresseur.
  6. Compresseur à injection d'huile suivant l'une des revendications précédentes,
    caractérisé en ce que le dispositif ( 7 ) de refroidissement effectue, outre le refroidissement dans le circuit ( 3 ) d'huile, également un post-refroidissement de l'air comprimé quittant le dispositif ( 4 ) à séparateur d' huile.
EP06754724A 2005-07-15 2006-07-14 Compresseur a injection d'huile dote de moyens de reglage de la temperature de l'huile Not-in-force EP1907704B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102005033084A DE102005033084B4 (de) 2005-07-15 2005-07-15 Öleingespritzter Verdichter mit Mitteln zur Öltemperaturregelung
PCT/EP2006/006903 WO2007009669A2 (fr) 2005-07-15 2006-07-14 Compresseur a injection d'huile dote de moyens de reglage de la temperature de l'huile

Publications (2)

Publication Number Publication Date
EP1907704A2 EP1907704A2 (fr) 2008-04-09
EP1907704B1 true EP1907704B1 (fr) 2009-06-17

Family

ID=37508278

Family Applications (1)

Application Number Title Priority Date Filing Date
EP06754724A Not-in-force EP1907704B1 (fr) 2005-07-15 2006-07-14 Compresseur a injection d'huile dote de moyens de reglage de la temperature de l'huile

Country Status (6)

Country Link
US (1) US20080206085A1 (fr)
EP (1) EP1907704B1 (fr)
JP (1) JP2009501290A (fr)
AT (1) ATE434133T1 (fr)
DE (2) DE102005033084B4 (fr)
WO (1) WO2007009669A2 (fr)

Families Citing this family (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4885077B2 (ja) * 2007-07-03 2012-02-29 株式会社日立産機システム 無給油式スクリュー圧縮機
US8801395B2 (en) * 2008-06-16 2014-08-12 Gardner Denver, Inc. Startup bypass system for a screw compressor
DE202008012380U1 (de) * 2008-09-18 2010-02-11 Oerlikon Leybold Vacuum Gmbh Vakuumpumpe
JP5410123B2 (ja) 2009-03-13 2014-02-05 株式会社日立産機システム 空気圧縮機
DE102011014961A1 (de) * 2011-03-24 2012-09-27 Rotorcomp Verdichter Gmbh Schraubenverdichteranlage
DE102013113555A1 (de) * 2013-12-05 2015-06-11 Knorr-Bremse Systeme für Schienenfahrzeuge GmbH Kompressorsystem und Verfahren zum Betrieb des Kompressorsystems in Abhängigkeit vom Betriebszustand des Schienenfahrzeugs
DE102013020533A1 (de) * 2013-12-12 2015-07-02 Gea Refrigeration Germany Gmbh Verdichter
DE102014101113A1 (de) * 2014-01-30 2015-07-30 Pfeiffer Vacuum Gmbh Vakuumpumpe
JP6325336B2 (ja) * 2014-05-15 2018-05-16 ナブテスコ株式会社 車両用空気圧縮機ユニット
DE102016011431A1 (de) * 2016-09-21 2018-03-22 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Schraubenkompressor für ein Nutzfahrzeug
DE102016011439A1 (de) * 2016-09-21 2018-03-22 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Schraubenkompressorsystem für ein Nutzfahrzeug
DE102017107933A1 (de) * 2017-04-12 2018-10-18 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Kompressorsystem mit regelbarer und/oder steuerbarer Temperaturüberwachungs-einrichtung
CA3016521A1 (fr) * 2017-09-06 2019-03-06 Joy Global Surface Mining Inc Systeme de lubrification destine a un compresseur
CN107947469A (zh) * 2017-12-21 2018-04-20 盐城中德劲博机电有限责任公司 螺杆空压机冷却结构
AU2021202410A1 (en) 2020-04-21 2021-11-11 Joy Global Surface Mining Inc Lubrication system for a compressor
CN111864996B (zh) * 2020-08-06 2025-05-23 智新科技股份有限公司 一种油冷电机
CN113833660B (zh) * 2021-10-18 2023-04-25 珠海凌达压缩机有限公司 供油组件、压缩机及控制方法
BE1030213B1 (nl) * 2022-01-25 2023-08-21 Atlas Copco Airpower Nv Werkwijze voor het regelen van een eerste referentietemperatuur in een inrichting voor samenpersen van gas
US12180964B1 (en) 2024-04-02 2024-12-31 Bendix Commercial Vehicle Systems Llc Apparatus and method for controlling a vehicle air compressor to track water content in compressor oil

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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 (ja) * 1993-01-14 1994-08-02 Hitachi Ltd 油冷式回転圧縮機の油温調整装置
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 (nl) * 2000-12-06 2002-10-01 Atlas Copco Airpower Nv Werkwijze voor het regelen van een compressorinstallatie.
EP1379786B1 (fr) * 2001-04-17 2005-03-16 TM.C. S.P.A. Termomeccanica Compressori Unite compresseur a vis avec systeme de refroidissement d'huile incorpore
DE10156179A1 (de) * 2001-11-15 2003-05-28 Leybold Vakuum Gmbh Kühlung einer Schraubenvakuumpumpe
DE10156180B4 (de) * 2001-11-15 2015-10-15 Oerlikon Leybold Vacuum Gmbh Gekühlte Schraubenvakuumpumpe
BE1014611A3 (nl) * 2002-02-08 2004-01-13 Atlas Copco Airpower Nv Werkwijze voor het besturen van de olieterugvoer in een met olie geinjecteerde schroefcompressor en aldus bestuurde schroefcompressor.
US20040244393A1 (en) * 2003-04-18 2004-12-09 Ingersoll-Rand Company Variable speed compressor cooling system

Also Published As

Publication number Publication date
WO2007009669A2 (fr) 2007-01-25
DE102005033084A1 (de) 2007-01-18
US20080206085A1 (en) 2008-08-28
WO2007009669A3 (fr) 2007-04-19
DE102005033084B4 (de) 2007-10-11
ATE434133T1 (de) 2009-07-15
DE502006004009D1 (de) 2009-07-30
JP2009501290A (ja) 2009-01-15
EP1907704A2 (fr) 2008-04-09

Similar Documents

Publication Publication Date Title
DE102005033084B4 (de) Öleingespritzter Verdichter mit Mitteln zur Öltemperaturregelung
DE102016218396B4 (de) Kältemittelverdichter
DE102004029505B4 (de) Fluidmaschine zum Umsetzen von Wärmeenergie in mechanische Drehkraft
WO2003042542A1 (fr) Procede de maintien a la temperature voulue d'une pompe a vide a vis
EP2732139A2 (fr) Dispositif de récupération de la chaleur résiduelle
EP3371423B1 (fr) Dispositif de refoulement pour le refoulement d'huile
EP3601797B1 (fr) Compresseur à piston avec une zone de reglage étendu
EP3362652B1 (fr) Dispositif de transport pour véhicule automobile
DE69723060T2 (de) Kühlmittelpumpe zur kraftfahrzeugverwendung
EP2071186A2 (fr) Pompe à vide et procédé de son fonctionnement
DE102005047760A1 (de) Komplexe Fluidmaschine
EP3388677A1 (fr) Procédé de commande d'un compresseur à vis
EP2570753B1 (fr) Pompe à chaleur avec éjecteur
DE102014008288B4 (de) Spindelverdichter für Kompressionskältemaschinen
EP0347706A1 (fr) Dispositif de pompe à vide multiétagé
DE102015213338B4 (de) Aktuatoreinheit
DE102004018860A1 (de) Fluidmaschine
DE19817351A1 (de) Schraubenspindel-Vakuumpumpe mit Gaskühlung
WO2010102604A1 (fr) Pompe de liquide de refroidissement à régulation
EP3596340B1 (fr) Système compresseur avec dispositif de surveillance de la température régulable et/ou commandable
DE10142263C1 (de) Regelbare Kühlmittelpumpe
DE102012207019B4 (de) Strömungsmaschine sowie Verfahren zur Kühlen einer solchen
EP4015823B1 (fr) Unité de moteur à piston rotatif pourvu de dispositif d'alimentation en lubrifiant
DE10207113A1 (de) Klimaanlagen, geeignet für die Verwendung in Fahrzeugen und Verfahren für den Betrieb solcher Klimaanlagen
EP2473739B1 (fr) Pompe à vis sèche à compression interne

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

17P Request for examination filed

Effective date: 20080215

AK Designated contracting states

Kind code of ref document: A2

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC NL PL PT RO SE SI SK TR

RIN1 Information on inventor provided before grant (corrected)

Inventor name: ZIEGLGAENSBERGER, NILS

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC NL PL PT RO SE SI SK TR

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: LANGUAGE OF EP DOCUMENT: GERMAN

REF Corresponds to:

Ref document number: 502006004009

Country of ref document: DE

Date of ref document: 20090730

Kind code of ref document: P

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

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: 20090617

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

Ref country code: FR

Payment date: 20090720

Year of fee payment: 4

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: 20090617

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: 20090617

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: 20090617

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: 20090917

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

Ref country code: FI

Payment date: 20090727

Year of fee payment: 4

NLV1 Nl: lapsed or annulled due to failure to fulfill the requirements of art. 29p and 29m of the patents act
REG Reference to a national code

Ref country code: IE

Ref legal event code: FD4D

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

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: 20091017

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: 20090617

Ref country code: IE

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: 20090617

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: 20090617

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: 20090617

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: 20090928

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: 20090617

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: 20090617

Ref country code: MC

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

Effective date: 20090731

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

Ref country code: BE

Payment date: 20090728

Year of fee payment: 4

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: 20090917

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: 20091017

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

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

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: 20090617

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

Ref country code: IT

Payment date: 20090731

Year of fee payment: 4

26N No opposition filed

Effective date: 20100318

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

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: 20090918

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

Ref country code: AT

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

Effective date: 20090714

BERE Be: lapsed

Owner name: KNORR-BREMSE SYSTEME FUR SCHIENENFAHRZEUGE G.M.B.

Effective date: 20100731

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20100714

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20110331

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: 20090714

Ref country code: LI

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

Effective date: 20100731

Ref country code: CH

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

Effective date: 20100731

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: 20100802

Ref country code: FI

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

Effective date: 20100714

Ref country code: IT

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

Effective date: 20100714

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: 20100731

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

Effective date: 20091218

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: 20100714

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: 20090617

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

Effective date: 20090617

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

Ref country code: DE

Payment date: 20150722

Year of fee payment: 10

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 502006004009

Country of ref document: DE

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: 20170201