EP2169233B1 - Système de refroidissement pour véhicules dotés d'un moteur à combustion interne refroidi par du liquide - Google Patents

Système de refroidissement pour véhicules dotés d'un moteur à combustion interne refroidi par du liquide Download PDF

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Publication number
EP2169233B1
EP2169233B1 EP09009316.2A EP09009316A EP2169233B1 EP 2169233 B1 EP2169233 B1 EP 2169233B1 EP 09009316 A EP09009316 A EP 09009316A EP 2169233 B1 EP2169233 B1 EP 2169233B1
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EP
European Patent Office
Prior art keywords
pump
cooling system
coolant
channels
terms
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP09009316.2A
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German (de)
English (en)
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EP2169233A3 (fr
EP2169233A2 (fr
Inventor
Norbert Schatz
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.)
MAN Truck and Bus SE
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MAN Truck and Bus SE
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Publication date
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Publication of EP2169233A2 publication Critical patent/EP2169233A2/fr
Publication of EP2169233A3 publication Critical patent/EP2169233A3/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D15/00—Control, e.g. regulation, of pumps, pumping installations or systems
    • F04D15/02—Stopping of pumps, or operating valves, on occurrence of unwanted conditions
    • F04D15/0209—Stopping of pumps, or operating valves, on occurrence of unwanted conditions responsive to a condition of the working fluid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P7/00—Controlling of coolant flow
    • F01P7/14—Controlling of coolant flow the coolant being liquid
    • F01P7/16—Controlling of coolant flow the coolant being liquid by thermostatic control
    • F01P7/161—Controlling of coolant flow the coolant being liquid by thermostatic control by bypassing pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D1/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D15/00—Control, e.g. regulation, of pumps, pumping installations or systems
    • F04D15/0027—Varying behaviour or the very pump
    • F04D15/0038—Varying behaviour or the very pump by varying the effective cross-sectional area of flow through the rotor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P7/00—Controlling of coolant flow
    • F01P7/14—Controlling of coolant flow the coolant being liquid
    • F01P2007/146—Controlling of coolant flow the coolant being liquid using valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2270/00—Control
    • F05D2270/60—Control system actuates means
    • F05D2270/64—Hydraulic actuators

Definitions

  • the present invention relates to a cooling system for vehicles, in particular commercial or motor vehicles with a liquid-cooled internal combustion engine, according to the preamble of claim 1.
  • Such a cooling system for internal combustion engines describes, for example, the DE 10 2005 062 200 B3 , in which the cooling circuit of the liquid cooling is supplied via a single-flow centrifugal pump, the delivery rate of which can be changed by means of an annular slide valve that more or less covers the impeller.
  • the ring slide is acted upon pneumatically via a separate pressure medium source and is used to control the flow rate or pump output within a coolant circuit as required.
  • a controllable coolant pump for a cooling circuit of an internal combustion engine in which a pump wheel is rotatably mounted in a housing, a coolant inlet and two separate coolant outlets being provided.
  • a valve slide is provided which can be moved between two slide positions, with both coolant outlets being open in a first slide position and one of the two coolant outlets being opened and the other closed in a second slide position.
  • the valve slide should also be movable into a third slide position in which both coolant outlets are closed.
  • the pump wheel has two pump wheel stages, each of which includes a plurality of pump wheel channels, wherein the two pump wheel stages can have the same or different flow cross-sections.
  • the coolant inlet is connected to a radiator or coolant thermostat of the motor vehicle, while the two coolant outlets are to be connected to separate branches of the coolant circuit, namely one with cooling channels in a cylinder head and the other with cooling channels in a cylinder crankcase of the internal combustion engine.
  • the object of the invention is to develop a cooling system with a controllable coolant pump for vehicles with a liquid-cooled internal combustion engine in such a way that this cooling system can be supplied as required while providing favorable efficiencies and versatile control options.
  • the z. B. specifically designed as a centrifugal pump coolant pump for supplying different, separate coolant circuits multi-flow, in particular double-flow with several, in particular two, pump flows, with at least one of the pump flows via the control element, which is preferably designed as a ring slide, can be changed with regard to the delivery rate.
  • the control element which is preferably designed as a ring slide
  • the regulating element for regulating the variable delivery rate of at least one of the pump flows can be acted upon by means of a predetermined amount of a coolant from another, separated, first pump flow.
  • impellers of the pump impeller can be provided, which are functionally separated from each other by a partition wall in the pump room, z.
  • the impeller immediately adjacent to the pump housing cooperates with a ring slide as a control element.
  • the impellers are preferably formed by a subdivided, one-piece impeller.
  • impeller is to be understood here in a broader sense and should in principle encompass any suitable impeller geometry.
  • the cooling system of the internal combustion engine is supplied with a first pump flow and a low-temperature circuit of the internal combustion engine is supplied with a second pump flow variable in the flow rate.
  • the first pump flow can be designed for a higher delivery rate than the second pump flow by appropriate division of the two at least functionally separate impellers.
  • the main cooling circuit of the internal combustion engine can be designed for up to 80% pump output and the secondary cooling circuit or low-temperature cooling circuit for around 20%, with the need-based control providing a further structural intervention.
  • the pump flow which is variable in terms of its delivery rate, can be designed in terms of its structurally determined delivery rate so that a defined system pressure in the associated coolant is not exceeded at full delivery rate.
  • This design and, if necessary, control of the throughput of the variable pump flow in terms of delivery rate enables a z. B. to omit the low-temperature circuit as a secondary cooling circuit otherwise used overpressure valve.
  • the regulating element is preferably designed as an annular slide.
  • This ring slide can be via z.
  • springs as an energy store in a position releasing the full flow rate of the variable flow rate of the pump flow and is particularly preferably actuated by applying pressure by means of a coolant flow of a first pump flow on the pressure side. This creates a particularly simple control of the second pump flow depending on the pressure profile on the pressure side of the first pump flow, it being possible to dispense with additional pressure medium sources.
  • the delivery rate of the first pump flow can also be designed to be adjustable via a second adjusting means.
  • This provides an even more extensive, needs-based control of the z.
  • centrifugal pump as a coolant pump which among other things, a particularly rapid heating of the internal combustion engine to operating temperature and an even more favorable pump efficiency can be controlled.
  • the second adjustment means can preferably also be formed by an annular slide which is temperature, speed and / or pressure dependent via a pressure medium source operated by the internal combustion engine is applied.
  • the pressure medium source can in particular be a servo device that is driven by the internal combustion engine anyway, for example a hydraulic power steering, etc.
  • a compressed air source can also be used.
  • this ring slide can also be arranged in a housing that communicates with the pump housing and at least partially surrounds the pump chamber.
  • the housing can either be a separate receiving housing (coolant distributor housing) adjoining the internal combustion engine, into which the pump housing is inserted, and / or the cylinder housing of the internal combustion engine to which the centrifugal pump is attached.
  • both cooling circuits or both pump flows can expediently be connected separately to one or two storage tanks of the cooling system in order to compensate for the usual expansion of the cooling medium when it is heated.
  • a cylinder housing 1 of a multi-cylinder, liquid-cooled internal combustion engine is partially visible here, in the end face 2 of which a pump chamber 3 is formed, in which a centrifugal pump 4 is used as a controllable coolant pump.
  • a separate receiving housing can also be provided as the coolant distributor housing 1a, into which the centrifugal pump 4 is partially or completely inserted.
  • This coolant distributor housing 1a is shown here only extremely schematically and with dashed lines.
  • the centrifugal pump 4 is driven by the internal combustion engine via a drive shaft 5 and a drive wheel 6 via a belt drive (not shown).
  • the centrifugal pump 4 has a double-flow design and supplies the internal combustion engine with cooling liquid on the pressure side in a first high-temperature cooling circuit via an only indicated pressure line 7, which communicates via a return line 8 with a first air-flow heat exchanger 9a as a high-temperature heat exchanger.
  • An intake line 10a conducts the recooled cooling liquid to an intake opening 11a of the centrifugal pump 4.
  • the first cooling circuit described supplies the entire internal combustion engine in a known manner, furthermore e.g. a heating system (not shown) of the interior of the motor vehicle, etc.
  • the second low-temperature circuit has a pressure line 12 which is connected to the second pump flow of the centrifugal pump 4 and which is connected to a charge air cooler 13.
  • the cooling liquid flows via a return line 14 to a second heat exchanger 9b through which air flows Low-temperature heat exchanger, from where the cooling liquid then flows back via a return line 10b to a suction opening 11b of the centrifugal pump 4.
  • the charge air cooler 13 is connected to charge air lines 15, 16, which are only indicated, and is used for recooling compressed combustion air supplied to the internal combustion engine.
  • Both cooling circuits are connected via lines 17a, 17b, which branch off from the return lines 8, 14, to an expansion tank 18 partially filled with cooling liquid.
  • the Fig. 2 shows the centrifugal pump 4 in detail, which is essentially composed of a pump housing 19, the drive shaft 5, the drive wheel 6, a double-flow pump impeller 20 and an axially adjustable ring slide 21.
  • the centrifugal pump 4 is of a known type, as far as it has not been described.
  • the drive shaft 5 is rotatably supported in the pump housing 19 by means of a roller bearing 22, not shown, and is sealed to the outside. B. protrudes into the cylinder housing 1 of the internal combustion engine and / or the coolant distributor housing 1a.
  • the pump impeller 20 has an inner partition 20a on the impeller side, which in the pump chamber 3 interacts with an annular partition 23 and divides the pump chamber 3 into two pump flows 34, 35. Both pump flows 34, 35 are thereby separated from one another, but minimal leakages are permitted.
  • the partition 23 is preferably an integral part of the pump housing 19 and thus divides the Pump chamber 3 in such a way that the two outflow openings 24, 25 to the pressure lines 7, 12 are separated from one another on the pressure side.
  • Each of the two pump flows 34, 35 is assigned an impeller 20b, 20c of the pump impeller 20 or is essentially formed by them, with the inner partition 20a extending as an impeller separating element and the impellers 20b and 20c between the impellers 20b, 20c functionally separates from each other.
  • the centrifugal pump 4 or the pump impeller 20 draws cooling liquid into the pump flow 34 via the suction opening 11a or into the pump flow 35 via the suction opening 11b, which is only shown in an extremely schematic and exemplary manner, and conveys it via the outflow openings 24 by means of the two impellers 20b, 20c , 25 radially outward to those in the Fig. 1 shown pressure lines 7, 12 of the first and second cooling circuit.
  • annular base plate 26 On the rear side of the pump impeller 20, an annular base plate 26 is formed which has a plurality of guide bolts 27 (in the sectional drawing, preferably evenly spaced apart from one another in the circumferential direction) Fig. 2 only one guide pin 27 can be seen) accommodates.
  • the guide pins 27 carry or guide a radial wall 21a of the ring slide 21, the peripheral wall 21b of which covers the impeller 20b of the pump impeller 20 to a predetermined extent, depending on the ring slide position, and thus controls the flow rate of coolant in the low-temperature cooling circuit.
  • the actuating pistons 29 or their bearing bores open into an annular space 19c of the hub section 19b and can be pressurized via this with coolant from the first pump flow 34 in a manner to be described in more detail, so that the ring slide 21 is extended into the position that reduces the delivery rate of coolant .
  • a pressure line 31 is connected to the annular space 19c, which is flow-connected via branch ducts 32, 33 in the cylinder housing 1 to the pump space 3 or to the first pump flow 34 for supplying the first cooling circuit in the area of the outflow opening 24.
  • the pump pressure of the first pump flood 34 can propagate via the pressure line 31 into the annular space 19c and determines the delivery rate and the delivery pressure of the second pump flood 35 in the above-described low-temperature circuit in a simple manner in terms of control technology.
  • the helical compression springs 28 ensure that, in the event of any malfunctions, the second pump flow 35 of the impeller 20 is fully functional or works with the maximum delivery rate provided by the design.
  • the pump flows 34, 35 with the partition 20a in the pump impeller 20 and the partition 23 in the pump chamber 3 are structurally z. B. designed so that in the Fig. 2 shown open position of the ring slide 21 z. B. about 80% of the flow rate of cooling liquid in the first main cooling circuit through the internal combustion engine and about 20% in the second low-temperature cooling circuit with the intercooler 13 flow.
  • the open position is designed so that in the Fig. 2 shown open position of the ring slide 21 z. B. about 80% of the flow rate of cooling liquid in the first main cooling circuit through the internal combustion engine and about 20% in the second low-temperature cooling circuit with the intercooler 13 flow.
  • other pre-settings are also possible for the open position.
  • the delivery rate and delivery pressure of the low-temperature cooling circuit can be reduced by activating the ring slide 21 via the delivery pressure of the first cooling circuit and the actuating piston 29, the ring slide 21 with its peripheral wall 21b, the impeller 20c and, accordingly, the second pump flow 35 in a predetermined manner Enclose or cover dimensions.
  • the first pump flow 34 can optionally also be designed to be adjustable in terms of its delivery rate via a second adjusting means.
  • the second adjustment means can also be formed by a ring slide, which is acted upon by a pressure medium source operated by the internal combustion engine, e.g. hydraulically or pneumatically, depending on temperature, speed and / or pressure and which is preferably in a with the pump housing or the cylinder housing 1 and / or the coolant distributor housing 1a communicating, the pump chamber 3 at least partially surrounding the housing is arranged.
  • a pressure medium source operated by the internal combustion engine, e.g. hydraulically or pneumatically, depending on temperature, speed and / or pressure and which is preferably in a with the pump housing or the cylinder housing 1 and / or the coolant distributor housing 1a communicating, the pump chamber 3 at least partially surrounding the housing is arranged.
  • the pump impeller 20 can optionally be formed by two impellers arranged axially adjacent to one another, which are optionally designed with different outside diameters and / or widths in order to design their delivery rates and thus the pump flows accordingly.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Claims (12)

  1. Système de refroidissement de moteurs à combustion interne refroidis par liquide, le système comprenant une pompe à liquide de refroidissement régulable (4) et un élément de régulation (21) qui régule le débit, la pompe à liquide de refroidissement (4) étant conçue à flux multiples avec plusieurs flux de pompe (34, 35) associés à chaque circuit de liquide de refroidissement séparé, au moins un des flux de pompe (35) étant variable en termes de débit au moyen de l'élément de régulation (21), caractérisé en ce que, pour réguler le débit variable d'au moins un des flux de pompe (35), l'élément de régulation (21) peut être soumis à une quantité prédéterminée d'un liquide de refroidissement provenant d'un autre premier flux de pompe séparé (34).
  2. Système de refroidissement selon la revendication 1, caractérisé en ce que les flux de pompe (34, 35) sont conçus différemment en termes de débits et une régulation du débit d'au moins un des flux de pompe (34, 35) est effectuée au moyen de l'élément de régulation (21) dans des plages de régulation prédéterminées.
  3. Système de refroidissement selon la revendication 2, caractérisé en ce qu'un premier flux de pompe (34) alimente un système de refroidissement du moteur à combustion interne et un deuxième flux de pompe (35) à débit variable alimente un circuit à basse température du moteur à combustion interne, le premier flux de pompe (34) étant conçu pour une pression de refoulement plus élevée que le deuxième flux de pompe (35), en particulier par une division et/ou conception appropriée de rouets (20b, 20c) au moins fonctionnellement séparés et associés aux flux de pompe (34, 35).
  4. Système de refroidissement selon l'une des revendications 1 à 3, caractérisé en ce que les deux flux de pompe (34, 35) sont relié fluidiquement au moyen d'au moins une conduite de trop-plein (31), la conduite de trop-plein (31) étant de préférence conçue comme une conduite sous pression dérivant du côté sous pression du premier flux de pompe (34) transférant par pompage le liquide de refroidissement.
  5. Système de refroidissement selon la revendication 4, caractérisé en ce que la conduite de trop-plein (31) débouche dans une chambre sous pression (19c) associée à l'élément de commande (21) de telle sorte que l'élément de régulation (21) puisse être déplacé suivant un chemin de déplacement spécifié conformément à la quantité de liquide de refroidissement acheminé dans la chambre sous pression (19c) et libère ainsi complètement ou ferme au moins partiellement le flux de pompe respectif (35) variable en termes de débit.
  6. Système de refroidissement selon la revendication 5, caractérisé en ce que la conduite de trop-plein (31) débouche dans une chambre sous pression (19c) réalisée sous la forme d'un espace annulaire autour d'un arbre d'entraînement (5) de la pompe entre le corps de pompe (19) et l'élément de régulation (21) conçu comme une coulisseau annulaire.
  7. Système de refroidissement selon l'une des revendications 1 à 6, caractérisé en ce que l'au moins un flux de pompe (35), variable en termes de débit, est conçu en fonction de son débit de sorte qu'une pression de pompe définie dans le circuit de liquide de refroidissement associé n'est pas dépassée à plein débit.
  8. Système de refroidissement selon l'une des revendications 1 à 7, caractérisé en ce que les flux de pompe (34, 35) dans la chambre de pompe (3) au moyen d'une paroi de séparation (23) faisant de préférence partie intégrante d'un boîtier de pompe (19) sont séparés complètement les uns des autres ou sensiblement les uns des autres avec des fuites d'ordres de grandeur définis.
  9. Système de refroidissement selon l'une des revendications 1 à 8, caractérisé en ce qu'un rouet séparé (20b, 20c) d'une roue de pompe (20) est associé à chacun des flux de pompe (34, 35).
  10. Système de refroidissement selon la revendication 9, caractérisé en ce que les rouets (20b, 20c) sont disposés sur un arbre d'entraînement commun (5) de la pompe à liquide de refroidissement et sont entraînés par celui-ci.
  11. Système de refroidissement selon l'une des revendications 1 à 10, caractérisé en ce que les différents circuits de liquide de refroidissement ou flux de pompe (34, 35) sont reliés à un vase d'expansion (18).
  12. Système de refroidissement selon l'une des revendications 1 à 11, caractérisé en ce que les deux flux de pompe (34, 35) sont conçus chacun de manière à être réglable en termes de débit par le biais d'un moyen de réglage.
EP09009316.2A 2008-09-27 2009-07-17 Système de refroidissement pour véhicules dotés d'un moteur à combustion interne refroidi par du liquide Active EP2169233B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102008049204A DE102008049204A1 (de) 2008-09-27 2008-09-27 Kühlsystem für Fahrzeuge mit flüssigkeitsgekühlter Brennkraftmaschine

Publications (3)

Publication Number Publication Date
EP2169233A2 EP2169233A2 (fr) 2010-03-31
EP2169233A3 EP2169233A3 (fr) 2017-03-29
EP2169233B1 true EP2169233B1 (fr) 2021-03-31

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EP09009316.2A Active EP2169233B1 (fr) 2008-09-27 2009-07-17 Système de refroidissement pour véhicules dotés d'un moteur à combustion interne refroidi par du liquide

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EP (1) EP2169233B1 (fr)
DE (1) DE102008049204A1 (fr)

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DE102010025560B4 (de) 2010-06-30 2019-03-07 Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr Schaltbare Kühlmittelpumpe
DE102010026132A1 (de) * 2010-07-05 2012-01-05 Mahle International Gmbh Laufrad und Fluidpumpe
DE102010046316B4 (de) * 2010-09-23 2020-03-19 Audi Ag Pumpenantrieb mit Viskokupplung und mechanischer Drehzahlregelung
DE102010044167A1 (de) * 2010-11-19 2012-05-24 Mahle International Gmbh Pumpe
EP2455615B1 (fr) * 2010-11-19 2017-08-16 MAHLE International GmbH Pompe
DE102011012826B3 (de) * 2011-03-02 2012-01-12 Geräte- und Pumpenbau GmbH Dr. Eugen Schmidt Regelbare Kühlmittelpumpe
DE102011001090A1 (de) * 2011-03-04 2012-09-06 Geräte- und Pumpenbau GmbH Dr. Eugen Schmidt Merbelsrod Regelbares Kühlsystem für ein Kraftfahrzeug, Kühlmittelpumpe hierfür, in der Kühlmittelpumpe verwendbares Flügelrad sowie Verfahren zum Regeln eines Kühlmittelflusses in einem derartigen Kühlsystem
DE102011079311A1 (de) * 2011-07-18 2013-01-24 Schaeffler Technologies AG & Co. KG Kühlmittelpumpe für einen Kühlmittelkreiskreislauf einer Brennkraftmaschine
DE102011113040B3 (de) * 2011-09-09 2012-04-26 Geräte- und Pumpenbau GmbH Dr. Eugen Schmidt "Regelbare Kühlmittelpumpe"
DE102012214503B4 (de) 2012-08-14 2017-10-12 Schwäbische Hüttenwerke Automotive GmbH Rotationspumpe mit verstellbarem Fördervolumen, insbesondere zum Verstellen einer Kühlmittelpumpe
US9739194B2 (en) 2013-03-04 2017-08-22 Ford Global Technologies, Llc Charge-air intercooler system with integrated heating device
DE102014219565B4 (de) * 2013-10-07 2015-10-15 Schaeffler Technologies AG & Co. KG Äußerer Aktuator für eine Läuferabdeckscheibe einer verstellbaren Wasserpumpe
DE102014202979A1 (de) * 2014-02-18 2015-08-20 Volkswagen Aktiengesellschaft Pumpe
DE102014004009A1 (de) * 2014-03-20 2015-12-03 Daimler Ag Kühlmittelkreislauf zum Kühlen einer Verbrennungskraftmaschine, insbesondere für einen Kraftwagen, sowie Verfahren zum Betreiben eines solchen Kühlmittelkreislaufs
DE102014009367B3 (de) * 2014-06-21 2015-03-05 Geräte- und Pumpenbau GmbH Dr. Eugen Schmidt Regelbare Kühlmittelpumpe
DE102016116636B4 (de) * 2016-09-06 2019-08-14 Pierburg Gmbh Kühlmittelpumpe für den Kfz-Bereich sowie ein Kühlmittelkreislauf für eine Verbrennungskraftmaschine

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DE102005062200B3 (de) 2005-12-23 2007-02-22 Geräte- und Pumpenbau GmbH Dr. Eugen Schmidt Regelbare Kühlmittelpumpe
DE102006034960B4 (de) * 2006-07-28 2008-05-15 Audi Ag Kühlmittelpumpe für einen Kühlkreislauf einer Verbrennungskraftmaschine

Non-Patent Citations (1)

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Publication number Publication date
EP2169233A3 (fr) 2017-03-29
DE102008049204A1 (de) 2010-04-01
EP2169233A2 (fr) 2010-03-31

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