EP2681425B1 - Controllable cooling system for a motor vehicle, coolant pump therefor, impeller for use in the coolant pump, and method for controlling a coolant flow in such a cooling system - Google Patents

Controllable cooling system for a motor vehicle, coolant pump therefor, impeller for use in the coolant pump, and method for controlling a coolant flow in such a cooling system Download PDF

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Publication number
EP2681425B1
EP2681425B1 EP11793659.1A EP11793659A EP2681425B1 EP 2681425 B1 EP2681425 B1 EP 2681425B1 EP 11793659 A EP11793659 A EP 11793659A EP 2681425 B1 EP2681425 B1 EP 2681425B1
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EP
European Patent Office
Prior art keywords
coolant
pump
impeller
coolant pump
control slide
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
EP11793659.1A
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German (de)
French (fr)
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EP2681425A2 (en
Inventor
Franz Pawellek
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.)
Nidec GPM GmbH
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Nidec GPM GmbH
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Publication date
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Publication of EP2681425A2 publication Critical patent/EP2681425A2/en
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Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28HEAT EXCHANGE IN GENERAL
    • F28FDETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00Tubular elements; Assemblies of tubular elements
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01PCOOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P5/00Pumping cooling-air or liquid coolants
    • F01P5/10Pumping liquid coolant; Arrangements of coolant pumps
    • F01P5/12Pump-driving arrangements
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04DNON-POSITIVE-DISPLACEMENT PUMPS
    • F04D13/00Pumping installations or systems
    • F04D13/02Units comprising pumps and their driving means
    • F04D13/06Units comprising pumps and their driving means the pump being electrically driven
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04DNON-POSITIVE-DISPLACEMENT PUMPS
    • F04D13/00Pumping installations or systems
    • F04D13/12Combinations of two or more pumps
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04DNON-POSITIVE-DISPLACEMENT PUMPS
    • F04D15/00Control, e.g. regulation, of pumps, pumping installations or systems
    • F04D15/0027Varying behaviour or the very pump
    • F04D15/0038Varying behaviour or the very pump by varying the effective cross-sectional area of flow through the rotor
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04DNON-POSITIVE-DISPLACEMENT PUMPS
    • F04D15/00Control, e.g. regulation, of pumps, pumping installations or systems
    • F04D15/02Stopping of pumps, or operating valves, on occurrence of unwanted conditions
    • F04D15/029Stopping of pumps, or operating valves, on occurrence of unwanted conditions for pumps operating in parallel
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01PCOOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P5/00Pumping cooling-air or liquid coolants
    • F01P5/10Pumping liquid coolant; Arrangements of coolant pumps
    • F01P5/12Pump-driving arrangements
    • F01P2005/125Driving auxiliary pumps electrically

Definitions

  • the present invention relates to a controllable cooling system for a motor vehicle according to claim 1, an electrically operated, controllable coolant pump according to claim 6, a usable in the coolant pump impeller according to claim 16 and a method for controlling a flow of coolant in such a cooling system according to claim 22 ,
  • coolant pumps In motor vehicles, in order to circulate coolant in a coolant circuit between the vehicle radiator and the internal combustion engine, mechanically actuated coolant pumps are generally used. Such designed as axial or radial pumps coolant pumps are arranged between the vehicle radiator and the internal combustion engine.
  • the coolant pumps are driven by a belt drive by the drive power of the internal combustion engine. Examples of such pumps are in the DE 10 2005 004 315 B4 and the DE 10 2005 062 200 B3 the same applicant.
  • start-stop systems which an internal combustion engine in the vehicle, for example when stopping at a red light, a railway barrier, etc., temporarily switch off.
  • the stop situation for example the traffic light switches to green and the vehicle driver presses the gas pedal, the internal combustion engine is restarted.
  • electrical coolant pumps have the disadvantage that they must be sufficiently large to provide the coolant performance. Such large-sized electrically operated coolant pumps then require a corresponding power supply from the electrical system of the motor vehicle.
  • hybrid coolant pump An example of such a coolant pump, referred to as a hybrid coolant pump, is disclosed in MTZ, Issue 11, 2010.
  • the hybrid coolant pump discussed therein is, as the main drive, driven by a belt drive via the drive power of the internal combustion engine.
  • this pump includes in its pump housing a brushless electric motor which can be switched by appropriate control via clutches on the drive shaft, thereby either boosted the driving force of the belt drive, or, in the start-stop state with the internal combustion engine off, the sole circulation of the coolant takes over.
  • the hybrid coolant pump disclosed in the MTZ, Issue 11, 2010, however, is not suitable for satisfactorily serving all operating states of the internal combustion engine.
  • the pump disclosed in the MTZ, Issue 11, 2010 shows the disadvantage that, when the pump is operated via the belt pulley, and thus via the internal combustion engine, the electric motor arranged in the pump housing acts as a generator. The generated electrical power must therefore be discharged accordingly from the pump and fed into the electrical system. In order to avoid the generator effect of the electric pump, it is alternatively necessary to isolate selbige of the shaft when the operation of the electric pump is not needed.
  • the present invention Based on the disadvantages of the above-described prior art, it is an object of the present invention to provide a cooling system which shows a simple structure, and with a simple way, a coolant flow in a coolant circuit of an internal combustion engine is ensured even when the internal combustion engine without drive is.
  • the present invention is intended Furthermore, create a cooling system by means of which different cooling effects can be achieved depending on different operating conditions of the internal combustion engine.
  • a controllable cooling system for a motor vehicle which has a coolant circuit for supplying and discharging coolant to and from an internal combustion engine of the vehicle.
  • this cooling system are a mechanically operated, controllable main coolant pump having a supply for supplying the coolant in the main coolant pump and a discharge for discharging the coolant to the internal combustion engine, and an electrically operated, controllable secondary coolant pump, which is a supply to Supplying the coolant into the secondary coolant pump and a discharge for discharging a conveyed as bypass coolant flow in the direction of the main coolant pump, wherein the secondary coolant pump from a leading coolant in the flow direction of the coolant to the main coolant pump coolant line branching in the flow direction the main coolant pump is arranged.
  • the pumped by the secondary coolant pump coolant is fed to the main coolant pump, without flowing through the main coolant pump, leading to the internal combustion engine exhaust.
  • the secondary coolant pump furthermore has a pump housing with a pump chamber formed therein, wherein an electric motor is arranged on a portion of the pump housing, which provides a drive power for the secondary coolant pump by means of a drive shaft extending into the pump chamber.
  • the secondary coolant pump Serving as a conveyor organ impeller is arranged in the pump chamber of the secondary coolant pump, which is arranged coaxially on the drive shaft and is drivably connected thereto, wherein the secondary coolant pump has a control valve formed on the impeller, at least in an open and closed position can be moved, for controlling the funded by the secondary coolant pump bypass coolant flow, in particular for Preventing the return flow of the coolant against the conveying direction of the secondary coolant pump.
  • a cooling system can be created in a surprisingly simple and cost-effective manner, showing a simple structure, and with the simple way a coolant flow in a coolant circuit of an internal combustion engine is ensured even then, even if the internal combustion engine is de-energized and thus can not generate drive power for the mechanically operated main coolant pump.
  • the proven in practice, mechanically operated coolant pump is maintained in the cooling system in an advantageous manner, whereby during operation of the cooling system with the mechanical pump, possibly supported by the electric pump, high efficiencies can be achieved.
  • the achievable with the cooling system according to the invention efficiencies are significantly higher than is the case with a single-shaft hybrid pump discussed above.
  • cooling system which has the two discussed controllable pumps, it is also advantageously possible to provide so-called stagnant water, in particular during cold start of the internal combustion engine, a rapid warm-up of the internal combustion engine allows, so that the vehicle within a very short time in an optimal Temperature fuel consumption range can be operated.
  • a cooling system can also be realized which, with manageable development and application costs, a reliable cooling performance in modern fuel-saving engine concepts , For example, with automatic start-stop, engine shutdown in sailing or the like, ensures.
  • the main coolant pump in this case has a pump housing with a pump chamber formed therein, wherein in the pump chamber serving as a conveyor organ impeller is arranged, which is driven via a reaching into the pump chamber shaft, which is preferably driven by a belt drive.
  • the main coolant pump may in this case be designed as an axial or radial pump according to one embodiment.
  • the use of the belt drive utilizing the driving force of the internal combustion engine has the advantage that even at low engine speed, the impeller can still be rotated in the main coolant pump, thereby ensuring coolant circulation even at low speed reliable overheating of the engine can be avoided.
  • the main coolant pump also has a control slide which is arranged coaxially with the impeller and which is movable, at least in an open and closed position, preferably along the impeller mounted in the pump chamber, for controlling the control of the main coolant pump funded coolant flow.
  • the slider can namely, for example, for generating stagnant water at cold start of the internal combustion engine, are moved to its closed position in which it includes the impeller and prevents the continuation of the pumped coolant from the derivative, thus interrupting the promoted by the impeller coolant flow.
  • the electric motor of the secondary coolant pump is designed as a dry runner or as a wet rotor.
  • the cooling system further comprises a control device which controls the main coolant pump and / or the secondary coolant pump in dependence on assigned operating states of the internal combustion engine.
  • control device which is implemented for example as a software module in the vehicle control unit or is designed as an independent control unit, it is advantageously possible to control the main coolant pump and / or the secondary coolant pump in parallel or independently of each other, in this way always a desired Make coolant flow in the cooling circuit.
  • the main coolant pump and / or the secondary coolant pump in such a way that they are decelerated in the warm-up mode during the cold start of the internal combustion engine, so that no coolant is circulated.
  • the pumps can be controlled in parallel or separately from each other to control the coolant flow by respective displacement of the arranged in the respective pump chamber control valve.
  • Another aspect of the present invention is to provide an electrically operated coolant pump suitable for such a cooling system.
  • An electrically operated coolant pump which is particularly suitable for use in a cooling system discussed above, is designed as an axial pump or as a radial pump.
  • the electrically operated coolant pump comprises: a pump housing; a, preferably flange-like, supply and a, preferably flange-like, discharge; a pump chamber formed in the pump housing, wherein in the pump chamber on a pump shaft, an impeller is arranged, which is driven by means of the pump shaft of an electric motor, and a slide which is movable at least in an open and closed position, for controlling one of the Coolant pump promoted bypass coolant flow.
  • the electrically operated pump according to the invention is in this case activatable such that in the closed position of the control slide, a return flow of the coolant from the internal combustion engine counter to the conveying direction of the secondary coolant pump can be prevented.
  • the parallel flow paths also represent bypass paths.
  • the medium to be pumped always flows in the direction of the lower pressure.
  • the main coolant pump builds a significantly higher delivery pressure during operation, it can be ensured by moving the control slide of the secondary coolant pump in its closed position that when the main pump is active, a return flow from the pressure side of the main pump via the secondary pump to the suction side is prevented.
  • the electric coolant pump is designed as a radial pump, wherein with the, substantially conically extending supply branched off from a coolant line to be conveyed coolant in the pump housing formed in the pump chamber can be introduced, and arranged with the, substantially radially perpendicular to the supply line , Leaching the introduced into the pump chamber coolant from the pump chamber can be discharged.
  • the impeller arranged in the pump chamber designed as a radial pump impeller, sucks the coolant by means of a rotational movement in the axial direction and conveys it in the radial direction into the discharge.
  • the slide is designed as a coaxial with the pump shaft arranged on the impeller control slide; and the electric motor is arranged, preferably at a portion of the pump housing facing away from the supply; wherein the electric motor has a drive shaft which projects into the pump chamber, the impeller and the control slide are arranged coaxially on the drive shaft, and are preferably held by means of holding elements form-fitting manner on the drive shaft, and the control slide the impeller encompassing, cylindrical and in the axial direction the impeller is displaceable in an open and closed position.
  • control slide is connected to the impeller so that vanes of the impeller penetrate the control slide.
  • the electric motor is designed as a dry rotor and sealed by means of a arranged on the drive shaft shaft seal against the pump chamber.
  • the electric motor is designed as a wet rotor and is cooled by means of the coolant pumped by the coolant pump.
  • control slide is moved over at least one provided in the pump housing actuator in its open and / or closed position.
  • This actuator can be designed as a pneumatically, magnetically and / or hydraulically operated slide or as an electric servomotor.
  • the actuator may, in an exemplary embodiment, be disposed in an end region of the drive shaft and engage in a chamber-like shaped section formed on the front of the control slide to move the control slide to its open and closed positions relative to the impeller.
  • the actuator may also be arranged between the impeller and the control slide.
  • the actuator is a rocker arm connecting the impeller with the control slide, which is hydraulically, pneumatically or magnetically movable from its at rest on the impeller (the open position of the control slide) in a position spaced from the impeller (the closed position of the control slide).
  • the actuator may also be formed in the wall of the pump housing, for example in recesses or chambers provided for this purpose.
  • control slide on the drive shaft encompassing, the supply facing, a chamber-like shaped portion, on the inner circumference of a threaded portion is formed, wherein on a side remote from the electric motor portion of the drive shaft of the electric coolant pump, a threaded portion is formed, which is complementary to the threaded portion of the control slide is.
  • the control slide is inventively, by mutual engagement of the threaded portions into one another, along the drive shaft slidably.
  • control slide is designed such that it follows the contour of the front of the impeller and at its outer end has a radially disposed closing element arranged thereon, wherein at a side remote from the electric motor end of the closing element a radially outside of the control slide arranged first sealing element is arranged.
  • a receptacle is formed in the pump chamber into which the closing element of the control slide in its open position can be introduced.
  • the size of the coolant pump can advantageously be further reduced because no additional space for the closing element of the control slide must be created within the pump chamber.
  • a second sealing element arranged radially inside the control slide is arranged on a radially outer end of the impeller facing the electric motor.
  • the diameter of the first sealing element may be made larger than the diameter of the second sealing element according to a preferred embodiment.
  • the discharge of the electric pump by means of the control slide in its closed position via the closing element, the first sealing element and the second sealing element is tightly closed.
  • the assembly of impeller and control slide can be made compact.
  • the provision of the sealing element on the control slide and on the impeller also advantageously allows a safe sealing of the discharge from the electric pump in the closed position of the control slide, wherein at the same time the closing element of the control slide is supported in its closed position against the impeller so that a possibly generated by the coolant back pressure can not bend or move the control slide so that a leakage flow is generated in the coolant pump.
  • a brake element is further provided, by means of which the impeller can be fixed against an inner wall of the pump housing.
  • the brake element is formed according to the one embodiment of the impeller, and preferably consists of a preloaded brake spring or plate-shaped brake disc, preferably at their radially outer ends, in the radial direction inwardly substantially wedge-shaped tapered, having thickenings, wherein the brake element preferably means the thickening, with the adjacent to the electric motor inner wall of the pump housing is frictionally engageable to set the impeller against the pump housing.
  • the braking element in particular with its thickenings, is designed such that it dissolves with increasing, caused by the drive shaft of the electric motor, the rotational speed of the impeller from the inner wall of the pump housing to release the impeller.
  • a kind of starting operation can be achieved in an advantageous manner when the control slide and the impeller are engaged with each other and the rotation of the drive shaft is transmitted by the adhesion between the impeller and control slide on the impeller. In this way, a smooth start of the pump power of the electric coolant pump can be realized.
  • the invention further provides a suitable impeller and a method for controlling a flow of coolant in a cooling system according to the invention.
  • the impeller comprises: a plurality of impeller blades, preferably radial pump-shaped, formed on the impeller surface facing a coolant supply; a recess for receiving a drive shaft; a control slide connected to the impeller; and a brake element disposed on the impeller.
  • the impeller according to the invention is advantageous for use in a coolant pump according to the invention discussed above, and a corresponding, this coolant pump having cooling system used.
  • control slide at its front end to a radially outwardly disposed first sealing element, wherein the impeller has at its radially outer end a radially disposed within the control slide second sealing element.
  • control slide is, according to another embodiment, formed integrally with the impeller such that the blades of the impeller penetrate the control slide in the axial direction.
  • the braking element is formed on a rear surface of the impeller.
  • the brake element consists of a preloaded brake spring or plate-shaped brake disc, which is frictionally engageable with an opposite surface of the rear surface of the impeller to set the impeller against this surface.
  • the braking element is designed such that its braking effect decreases with increasing rotational speed of the impeller, wherein it approaches the rear surface of the impeller to release the impeller.
  • control slide is designed such that it follows the contour of the impeller and has at its outer end a radially encircling closing element.
  • control slide in this case in its end region on a hollow, chamber-like portion formed on the inner peripheral wall, a threaded portion is formed.
  • the current operating state of the internal combustion engine has at least a start-stop state, a warm-up state, a low-load state, a normal load state, an eco state, a high-speed state, and a residual heat storage state on.
  • the start-stop state denotes a drive state in which the internal combustion engine is temporarily stopped, for example, when stopping at a red light or the like, to save fuel in this way.
  • the warm-up state means a driving state in which, particularly at the cold start of the internal combustion engine, water standing in the cooling system is generated due to intermittent circulation of the coolant, so that the temperature of the internal combustion engine can be quickly brought to its optimum operating temperature.
  • the low-load state means a drive state in which the internal combustion engine is operated at a low speed, for example, in idling operation.
  • the normal load state means a drive state in which the internal combustion engine, preferably in the middle speed range, is operated to apply a drive power to the vehicle.
  • the eco-state refers to a driving state in which the internal combustion engine is normally operated, and by means of a control intervention in the cooling system, the coolant temperature is maintained in an increased range, so that a more efficient fuel combustion and thus a more economical driving operation is possible.
  • the high-speed state refers to a driving state in which the internal combustion engine is operated at high speed with increased cooling demand, for example when driving on a highway or the like.
  • the residual heat storage state finally designates a drive state in which the internal combustion engine is switched off and the temperature of the coolant is to be kept high as long as possible in order to achieve a shortened warm-up phase when the internal combustion engine is restarted, whereby the internal combustion engine is faster in its optimum temperature range can be operated.
  • control parameters in the refrigeration cycle map include at least a desired coolant temperature, and / or a desired engine temperature, and / or a desired coolant flow rate, and / or the like.
  • the secondary coolant pump when the current operating state of the internal combustion engine is a warm-up state, the secondary coolant pump is switched to an OFF state with the control valve closed and a coolant flow through the main coolant pump is arranged by means disposed in the main coolant pump Control valve interrupted, so that a circulation of the coolant is interrupted.
  • the secondary coolant pump when the current operating state of the internal combustion engine is a start-stop state in which the main coolant pump is temporarily without power during a stop phase of the internal combustion engine, the secondary coolant pump is switched to an ON state , whereby the coolant is circulated through the secondary coolant pump.
  • a coolant flow through the main coolant pump is interrupted by means of a control spool disposed in the main coolant pump and the secondary coolant pump is switched to an ON state , whereby the coolant is circulated through the secondary coolant pump.
  • the secondary coolant pump when the current operating state of the internal combustion engine is a normal load state, the secondary coolant pump is switched to an OFF state and its control valve is closed, whereby the coolant in the coolant circuit is circulated through the main coolant pump.
  • the operation of the main coolant pump is selectively interrupted by means of an overrunning clutch provided on the belt drive of the main coolant pump or a control slide arranged in the main coolant pump is activated in such a way is that the coolant flow in the main coolant pump is interrupted, and the coolant is circulated through the secondary coolant pump to obtain a desired increased engine temperature.
  • the coolant flow of the main coolant pump when the current operating state of the internal combustion engine is the high-speed state is, the coolant flow of the main coolant pump, at least partially, is passed in the bypass mode via the secondary coolant pump to the inlet side of the main coolant pump.
  • both the control slide of the main coolant pump and the control slide of the secondary coolant pump are closed in order to prevent circulation of the coolant in the cooling circuit.
  • Fig. 1A shows a perspective view of a controllable cooling system 1 according to an embodiment of the present invention.
  • the cooling system 1 consists of a coolant circuit for supplying and discharging coolant from and to an internal combustion engine (not shown) of a vehicle, wherein the coolant via a arranged in the coolant line radiator (not shown) with the environment of the vehicle in heat exchange occurs.
  • a coolant line 13 from the vehicle radiator to a formed on a main coolant pump 3 feed 17.
  • This feed 17 is formed in the embodiment shown in a flange, but can also be in the form of a line, a nozzle, an opening, a screw or Bayonet connection or the like may be formed.
  • the main coolant pump 3 is formed in the present embodiment as a radial pump and comprises a pump housing with a pump chamber (not shown) formed therein, in which an impeller is arranged.
  • This impeller is designed as a radial pump impeller and arranged on a pump shaft in the pump housing of the main coolant pump 3.
  • a pulley 57 which is connected via a (not shown) wedge or toothed belt with a pulley of the internal combustion engine.
  • a rotation movement is transmitted to the pulley 57 of the main coolant pump 3 by the belt, whereby it is driven.
  • the main coolant pump 3 shown in this embodiment is an axially impinged coolant pump which, by means of the impeller arranged in the pump chamber, forwards the coolant to be conveyed radially outwards to a discharge 15.
  • This discharge 15 is analogous to the feed 17, formed in the embodiment shown in a flange. However, it may also be in the form of a line, a nozzle, an opening, a screw or bayonet connection or the like.
  • the main coolant pump 3 also has in its pump chamber a (also not shown) concentrically on the drive shaft, the impeller encompassing arranged control slide, which surrounds the impeller in its closed position in its closed position to one through the coolant pump 3 interrupted flow of coolant to interrupt.
  • Such pumps are marketed successfully by the same Applicant in the market and are for example in the document DE 10 2005 004 315 B4 .
  • the main coolant pump 3 of this embodiment the discharge 15, via which the coolant is conveyed from the main coolant pump 3 to the internal combustion engine.
  • a heating circuit may be provided in the cooling system, by means of which from the main coolant pump 3, a cooling medium via a heating line 19 in the heating circuit can be introduced.
  • a regulator or valve may be arranged in the main coolant pump 3 which conducts the coolant flow conveyed by the pump 3 into the heating circuit.
  • a secondary coolant pump 5 is arranged parallel to the main coolant pump 3, Parallel to the main coolant pump 3, a secondary coolant pump 5 is arranged.
  • the feed 9 to the secondary coolant pump 5 branches off at a point in front of the feed 17 of the main pump 3 from the coolant line 13.
  • the secondary coolant pump 5 is also formed in this embodiment as an axially impinged radially conveying pump, and is operated by an electric motor 7, which is arranged on a coolant supply 9 facing away portion of the secondary coolant pump 5.
  • the coolant supplied from the supply line 13 is sucked by the suction effect of a arranged in the secondary coolant pump 5 impeller 25 in the secondary coolant pump 5 and from there via the arranged in a pump chamber 53 impeller 25 via the discharge 11th discharged into the discharge 15 of the main coolant pump 3, without being affected by the Main pump 3 to flow.
  • the secondary coolant pump 5 thus forms a type of bypass path through which the coolant to be delivered can be circulated as a bypass coolant flow, bypassing the main coolant pump 5 in the cooling circuit coming from the radiator to the internal combustion engine
  • the supply 9 and the discharge 11 of the secondary coolant pump of the embodiment shown are formed in a flange. However, they may also be in the form of a line, a nozzle, an opening, a screw or bayonet connection or the like.
  • FIG. 2A A partial sectional view of the in the Characters. 1A and 1B shown, electrically operated coolant pump 5 is in Fig. 2A shown.
  • coolant pump 5 is, as described above, formed as an axially impinged radial pump, and includes a pump chamber 53 which is formed in a pump housing 51.
  • an electric motor 7 is arranged on an end of the secondary coolant pump 5 facing away from the feed 9.
  • the electric motor of this embodiment has a power between 20W and 100W and is designed as a dry runner, whereby high engine speeds of over 12,000 U / min are possible with low power consumption.
  • the drive shaft 21 is sealed in the embodiment shown here via a shaft seal 29 against the coolant to prevent ingress of coolant into the electric motor 7.
  • the impeller 25 and a control slide 31 Concentric on the drive shaft 21, the impeller 25 and a control slide 31 are arranged.
  • the impeller 25 is held by retaining elements 47 positively on the drive shaft.
  • control slide 31 essentially follows the contour of the end face of the impeller 25, wherein the wing blades 39 penetrate the control slide top.
  • a sleeve-shaped or chamber-like shaped portion 33 is formed on the inner wall circumference, a threaded portion is provided.
  • a complementary threaded portion is formed on a front portion 23 of the drive shaft 21.
  • the Fig. 2A shows the secondary coolant pump 5 in a state in which the control slide 31 is open.
  • a sealing element 45 is arranged at a radially outer end of the impeller 25, within a closing element 35 of the control slide 31, a sealing element 45 is arranged.
  • Another sealing element 43 is arranged on the radially outer end face of the control slide 31.
  • a closing member 35 receiving, circular the circumferential contour of the control slide 31 following, recess 37 is formed.
  • the closing element 35 formed thereon is received in this recess 37 and is rotatably held therein, so that the impeller 25 can rotate with the control slide formed thereon 31 by the driving force of the drive shaft 21.
  • the Fig. 3A shows the electrically operated, controllable secondary coolant pump 5 from FIGS. 2A and 2B in the closed state of the control slide 31.
  • the control slide 31 of the coolant pump 5 is, as shown schematically in the FIGS. 2A and 3A indicated, moved by slow forward or reverse rotation of the drive shaft 21 of the electric motor 7 in the respective working position.
  • control valve 31 is moved from its closed position to the open position, in which it rests against the contour of the impeller 25 at its surface, so that the impeller blades 39 can penetrate the control slide 31 and can generate the pumping action in the coolant pump 5 when the impeller rotates at operating speed.
  • control slide 31 When the control slide 31 by a reverse rotation of the drive shaft 21 in the in Fig. 3A In contrast, the control slide 31, in its fully closed position, comes into contact with a wall section of the pump housing 51 facing the feed 9.
  • the trained on the control slide 31 sealing element 43 is pressed against the pump housing wall and seals the pump chamber 53 against the Outlet 11 of the pump 5 from.
  • the sealing element 45 formed on the rear section of the impeller 25 supports the closing element 35 formed as the outer circumferential leg of the control slide 31 from below, thus producing a sufficiently reliable sealing effect.
  • the sealing element 43 formed on the control slide 31 is formed larger than the sealing element 45 formed on the impeller 25 in order to achieve a sufficiently large sealing effect against the wall surface of the pump chamber.
  • the pressure acting back on the annular surface from the pressure side of the main coolant pump 3, which results from the diameter differences of the sealing elements 43, 45 due to the different sealing diameters, the pressure acting back on the annular surface from the pressure side of the main coolant pump 3, which results from the diameter differences of the sealing elements 43, 45.
  • the sealing function of the sealing elements 43, 45 is thereby reinforced hydraulically, regardless of whether the electric motor 7 of the secondary coolant pump 5 is running or not.
  • a brake element 27 is arranged on one of the feed 9 facing away from the end of the impeller 25, which presses against an adjacent to the electric motor 7 inner wall surface 49 in the pump housing 51.
  • This brake element 27 is designed as a brake disk or prestressed plate spring and has in the embodiment shown at its radially outer ends wedge-shaped tapered thickenings 41, which come into frictional engagement with the inner wall surface 49 of the pump housing 51.
  • the brake element 27 dissolves due to the increasing centrifugal force by the rotation of the drive shaft 21 of the wall 49 of the pump housing 51 and are the rotation of the impeller 25, and thus the pumping function of the coolant pump 5 free.
  • Fig. 4 shows a perspective view of the in the Figures 2 and 3 shown impeller 25 of the electrically controllable coolant pump 5 with a control slide 31 arranged thereon.
  • control slide 31 As shown in this view from the front, the control slide 31, the (not shown) impeller 25 completely, wherein the impeller blades 39 penetrate the control slide 31.
  • the control slide 31 has in its center a drive shaft 21 of the electric motor 7 receiving, chamber-like portion 33.
  • This chamber-like portion 33 has, as shown schematically in FIG Fig. 5 indicated on the inner wall a threaded portion which is complementary to in Fig. 5 not shown threaded portion 23 of the drive shaft 21 is.
  • Fig. 5 shows a partial sectional view of an axially impinged, radially conveying impeller 25, as it comes in a designed as a radial pump pump 3, 5 of the embodiment discussed here used.
  • a hub-like receptacle 55 for receiving the (not shown) drive shaft 21 is formed.
  • Fig. 6 shows the impeller 25 from Fig. 5 with the control slide 31 arranged thereon in a complete sectional view.
  • the impeller 25 and the control slide 31 are arranged concentrically to each other and run along the drive shaft 21 reaching from the electric motor 7 in the pumping chamber 51, which are not shown here for simplicity of illustration.
  • control slide 31 By forward or reverse rotation of the drive shaft 21 of the electric motor 7, the control slide 31 can thereby be moved to the desired open or closed position.
  • cooling system which uses the mechanically operated, controllable coolant pump 3 and the electrically operated, controllable coolant pump 5, can be advantageously in consideration of predetermined control parameters such as a desired coolant temperature, and / or a desired engine temperature, and / or a desired coolant flow rates and / or the like set different operating conditions.
  • a control device is therefore additionally provided according to the embodiment discussed here, which controls the mechanically operated main coolant pump 3 and the electrically operated secondary coolant pump 5 in order to achieve the respective operating states.
  • Exemplary operating states are a start-stop state, a warm-up state, a low-load state, a normal-load state, an eco state, a high-speed state, and a residual heat storage state.
  • the start-stop state denotes a drive state in which the internal combustion engine is temporarily stopped, for example, when stopping at a red light or the like, to save fuel in this way.
  • the secondary coolant pump 5 is switched to an ON state. State is switched, whereby the coolant is circulated through the secondary coolant pump 5.
  • the warm-up state further designates a driving state in which, particularly at the cold start of the internal combustion engine, water standing in the cooling system 1 due to intermittent circulation of the coolant is generated, so that the temperature of the internal combustion engine can be quickly brought to its optimum operating temperature.
  • the secondary coolant pump 5 is switched to an OFF state, and a coolant flow through the main coolant pump 3 is interrupted by means of the control spool disposed in the main coolant pump, so that circulation of the coolant is interrupted.
  • the cooling system 1 of the embodiment discussed here it is possible to control the pumps 3, 5 in the warm-up phase of the internal combustion engine such that the slides of both pumps 3, 5 are closed, so that no coolant is circulated through the two pumps 3, 5 can.
  • the electrically operated coolant pump 5 can also be switched off, wherein a backflow and circulation of the coolant can be prevented by the closed control slide 31.
  • the pump 5 is controlled such that the control slide 31 prevents circulation of the coolant.
  • the low-load state further designates a drive state in which the internal combustion engine is operated at a low speed, for example, in idling operation.
  • a coolant flow through the main coolant pump 3 is interrupted by means of the control spool disposed in the main coolant pump and the secondary coolant pump 5 is switched to an ON state is, whereby the coolant is circulated through the secondary coolant pump 5.
  • the secondary electric coolant pump 5 it is possible to switch on the secondary electric coolant pump 5 to carry out so-called electric boosting, in other words, the circulation of the coolant by the delivery rate of the internal combustion engine and thereby possibly insufficient circulation performance of the main coolant pump 3 electrically controlled secondary coolant pump 5 to assist.
  • control slide 31 of the electrically operated coolant pump 3 is usually brought into its closed position or the pump 3 is switched off and realized the circulation of the coolant exclusively via the mechanically operated main coolant pump 3 ,
  • the electric coolant pump 5 can be switched on to support the coolant delivery through the mechanical coolant pump 3.
  • the normal load state means a drive state in which the internal combustion engine, preferably in the middle speed range, is operated to apply a drive power to the vehicle.
  • the secondary coolant pump 5 is switched to an OFF state and its control slide 31 is usually brought into the closed position, whereby the coolant in the coolant circuit is circulated through the main coolant pump 3.
  • the eco-state refers to a driving state in which the internal combustion engine is normally operated, and by means of a control intervention in the cooling system, the coolant temperature is maintained in an increased range, so that a more efficient fuel combustion and thus a more economical driving operation is possible.
  • the operation of the main coolant pump 3 is selectively interrupted by means of a provided on the pulley 57 of the main coolant pump 3 overrunning clutch, and / or arranged in the main coolant pump 3 control slide controlled in such a way that the coolant flow in the main coolant pump 3 is interrupted.
  • the coolant is circulated through the secondary coolant pump 5 to obtain a desired increased engine temperature.
  • the high-speed state refers to a driving state in which the internal combustion engine is operated at high speed with increased cooling demand, for example when driving on a highway or the like.
  • the coolant flow of the main coolant pump 3 is, at least partially, bypassed via the secondary coolant pump 5 to the intake side of the main coolant pump 5 leading to the internal combustion engine ,
  • the residual heat storage state finally designates a drive state in which the internal combustion engine is switched off and the temperature of the coolant is to be kept high as long as possible in order to achieve a shortened warm-up phase when the internal combustion engine is restarted, whereby the internal combustion engine is faster in its optimum temperature range can be operated.
  • the coolant flow from the engine back to the radiator is shut off by shutting off the two pumps 3, 5 by means of the slides arranged therein, whereby a heat exchange of the coolant with the environment of the vehicle can take place only very hesitant.
  • the heat generated by the internal combustion engine is thus maintained over a longer period of time when the motor vehicle is at a standstill and can be used, and later restarted, to speed up the operating temperature.
  • control slide 31 is displaced along the drive shaft 21 by means of a drive configured as a threaded spindle
  • the control slide may be pneumatically actuated relative to the impeller rather than via the threaded spindle , magnetically and / or hydraulically operated actuator or an electric servomotor along the drive shaft 21 is moved.
  • control slide 31 formed separately on the impeller 25, it is also conceivable that the control slide 31 is integrally formed in the impeller 25.
  • integrally formed in the impeller 25 control slide 31 may be formed such that on the outer surfaces of the impeller 25 leg-like wall surfaces are formed, which are the same effect as the closing element 35 of the control slide 31.
  • an impeller 25 designed in this way can be displaced along the drive axis 21, so that the thigh-like wall elements protruding toward the pump housing rear side seal the discharge 11 in a closed position of the impeller 25 thus formed close.
  • the wall elements in the formed in the housing wall of the pump housing 51 receptacle 37 are rotatably mounted about the drive shaft 21.
  • the impeller 25 is arranged encompassing in the pump chamber 53 and can be rotatably moved into an open and closed position. It is also possible to arrange a sleeve-shaped control slide 31 behind the impeller 25, which is then pushed over the impeller 25, for example by the above-discussed threaded spindle drive or a pneumatically, magnetically and / or hydraulically operated actuator or an electric servomotor, and the Outlet 11 of the secondary pump sealingly closes.
  • the impeller discussed above with the control slide arranged thereon can also be used as a kind of check valve in a piping system.
  • the slide can continue to promote on the impeller and the shaft shaft holding the oncoming medium or, at a correspondingly high flow pressure against the conveying direction, close the pipe system by moving the control slide in its closed position.
  • the electric coolant pump 5 discussed here has an electric motor 7 with a power between 20W and 100W, a more powerful electric motor, for example up to 2 kW, can also be used, so that the electric coolant pump may possibly also take over the circulation of the coolant as the only pump in the cooling circuit can.
  • the present invention relates to a controllable cooling system 1 for a motor vehicle with a coolant circuit which leads and discharges a coolant to an internal combustion engine, as well as a mechanically operated, controllable main coolant pump 3 and an electrically operated, controllable secondary coolant pump 5.
  • the cooling system further includes a control device that controls the main coolant pump 3 and the secondary coolant pump 5 depending on operating conditions of the internal combustion engine.
  • the invention further provides an electrically operated, controllable secondary coolant pump 5 for such a cooling system 1, an impeller 25 which can be used in this secondary coolant pump 5 and a method for regulating the coolant flow in such a cooling system 1.

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

GEBIET DER ERFINDUNGFIELD OF THE INVENTION

Die vorliegende Erfindung betrifft ein regelbares Kühlsystem für ein Kraftfahrzeug nach Anspruch 1, eine hierfür geeignete, elektrisch betriebene, regelbare Kühlmittelpumpe nach Anspruch 6, ein in der Kühlmittelpumpe verwendbares Flügelrad nach Anspruch 16 sowie ein Verfahren zum Regeln eines Kühlmittelflusses in einem derartigen Kühlsystem nach Anspruch 22.The present invention relates to a controllable cooling system for a motor vehicle according to claim 1, an electrically operated, controllable coolant pump according to claim 6, a usable in the coolant pump impeller according to claim 16 and a method for controlling a flow of coolant in such a cooling system according to claim 22 ,

STAND DER TECHNIKSTATE OF THE ART

In Kraftfahrzeugen werden, um Kühlmittel in einem Kühlmittelkreislauf zwischen Fahrzeugkühler und Verbrennungskraftmaschine zu zirkulieren, in der Regel mechanisch betätige Kühlmittelpumpen eingesetzt. Derartige als Axial- oder Radialpumpen ausgebildete Kühlmittelpumpen sind dabei zwischen dem Fahrzeugkühler und der Verbrennungskraftmaschine angeordnet.In motor vehicles, in order to circulate coolant in a coolant circuit between the vehicle radiator and the internal combustion engine, mechanically actuated coolant pumps are generally used. Such designed as axial or radial pumps coolant pumps are arranged between the vehicle radiator and the internal combustion engine.

Die Kühlmittelpumpen werden dabei über einen Riemenantrieb durch die Antriebsleistung der Verbrennungskraftmaschine angetrieben. Beispiele für derartige Pumpen sind in der DE 10 2005 004 315 B4 und der DE 10 2005 062 200 B3 derselben Anmelderin diskutiert.The coolant pumps are driven by a belt drive by the drive power of the internal combustion engine. Examples of such pumps are in the DE 10 2005 004 315 B4 and the DE 10 2005 062 200 B3 the same applicant.

Aufgrund zunehmender Knappheit fossiler Brennstoffe ist die aktuelle Entwicklung im Kraftfahrzeugbereich auf immer kraftstoffeffizientere und energiesparende Fahrzeuge gerichtet. Hierfür kommen beispielsweise Start-Stop-Systeme zur Anwendung, welche eine Verbrennungskraftmaschine im Fahrzeug, beispielsweise beim Halt an einer roten Ampel, einer Bahnschranke etc., vorübergehend abschalten. Sobald die Stop-Situation beendet ist, beispielsweise die Ampel auf grün umschaltet und der Fahrzeugführer das Gaspedal betätigt, wird die Verbrennungskraftmaschine wieder gestartet.Due to increasing scarcity of fossil fuels, the current development in the automotive sector is directed towards increasingly fuel-efficient and energy-efficient vehicles. For this purpose, for example, start-stop systems are used, which an internal combustion engine in the vehicle, for example when stopping at a red light, a railway barrier, etc., temporarily switch off. As soon as the stop situation has ended, for example the traffic light switches to green and the vehicle driver presses the gas pedal, the internal combustion engine is restarted.

Aufgrund des systembedingten Abschaltens der Verbrennungskraftmaschine bei derartigen Start-Stop-Systemen in modernen Kraftfahrzeugen wird jedoch auch der Betrieb der Kühlmittelpumpe gestoppt. Insbesondere wird, aufgrund des Anhaltens der Verbrennungskraftmaschine über den Riemenantrieb keine Antriebsleistung mehr auf die Kühlmittelpumpe übertragen, so dass deren Betrieb eingestellt wird, das Kühlmittel mithin nicht mehr im Kühlmittelkreislauf zirkuliert werden kann.Due to the system-related shutdown of the internal combustion engine in such start-stop systems in modern motor vehicles, however, the operation of the coolant pump is stopped. In particular, due to the stopping of the internal combustion engine via the belt drive no more drive power is transmitted to the coolant pump, so that their operation is stopped, the coolant can therefore no longer be circulated in the coolant circuit.

Dies kann, insbesondere bei hohen Außentemperaturen oder bereits entsprechend hoher Motor- beziehungsweise Kühlmitteltemperatur dazu führen, dass die Temperatur über das erlaubte Maß hinaus ansteigt.This can lead, in particular at high outside temperatures or already correspondingly high engine or coolant temperature, to the temperature rising beyond the permitted level.

Um das Kühlmittel im Kühlmittelkreislauf auch in Fahrzeugen mit Start-Stop-Systemen weiter zu zirkulieren, wenn die Verbrennungskraftmaschine nicht arbeitet, wäre es grundsätzlich denkbar, die herkömmlich eingesetzten, mechanisch betriebenen Kühlmittelpumpen durch elektrisch betriebene Kühlmittelpumpen zu ersetzten.In order to circulate the coolant in the coolant circuit even in vehicles with start-stop systems, if the internal combustion engine is not working, it would be fundamentally conceivable to replace the conventionally used, mechanically operated coolant pumps by electrically operated coolant pumps.

Eine Anordnung mit einer elektrisch und einer meche nisch betriebenen Kühlmittelpumpen wird im Dokument DE 100 37 823 A1 gezeigt.An arrangement with an electrically and a mech nisch operated coolant pumps is in the document DE 100 37 823 A1 shown.

Gleichwohl zeigen elektrische Kühlmittelpumpen den Nachteil, dass diese ausreichend groß dimensioniert sein müssen, um die Kühlmittelleistung zu erbringen. Derartig groß dimensionierte elektrisch betriebene Kühlmittelpumpen benötigen dann eine entsprechende Stromzufuhr aus dem Bordnetz des Kraftfahrzeuges.Nevertheless, electrical coolant pumps have the disadvantage that they must be sufficiently large to provide the coolant performance. Such large-sized electrically operated coolant pumps then require a corresponding power supply from the electrical system of the motor vehicle.

Da dies unter Umständen über die Lichtmaschine abgefangen werden muss, die entsprechend mehr Leistung erzeugen muss, um im Fahrzeug vorhandene Batterien auf einen Mindestladewert zu halten, sowie das Bordnetz ausreichend zu versorgen, hat sich die Verwendung elektrischer Pumpen als Kühlmittelpumpen für Kraftfahrzeuge bisher nicht durchgesetzt.Since this may have to be intercepted via the alternator, which must generate correspondingly more power in order to keep existing batteries in the vehicle to a minimum charging value, as well as to adequately supply the electrical system, the use of electric pumps has never prevailed as coolant pumps for motor vehicles.

Um dennoch eine Möglichkeit zu schaffen, bei modernen Start-Stop-Systemen einen ausreichenden Kühlmittelfluss zu gewährleisten, wurde jüngst versucht, durch die Kombination elektrischer und mechanischer Antriebe eine adaptierte Kühlmittelpumpe bereitzustellen.In order nevertheless to create a possibility to ensure a sufficient coolant flow in modern start-stop systems, it has recently been attempted to provide an adapted coolant pump by combining electrical and mechanical drives.

Ein Beispiel einer derartigen, als Hybridkühlmittelpumpe bezeichneten, Kühlmittelpumpe ist in der MTZ, Ausgabe 11, 2010, offenbart. Die darin diskutierte Hybridkühlmittelpumpe wird, als Hauptantrieb, von einem Riemenantrieb über die Antriebsleistung der Verbrennungskraftmaschine angetrieben. Zusätzlich umfasst diese Pumpe in ihrem Pumpengehäuse einen bürstenlosen Elektromotor, der durch entsprechende Steuerung über Kupplungen auf die Antriebswelle zugeschaltet werden kann, und dabei entweder die Antriebskraft des Riemenantriebes verstärkt, oder, im Start-Stop-Zustand bei ausgeschalteten Verbrennungskraftmaschine, die alleinige Zirkulation des Kühlmittels übernimmt.An example of such a coolant pump, referred to as a hybrid coolant pump, is disclosed in MTZ, Issue 11, 2010. The hybrid coolant pump discussed therein is, as the main drive, driven by a belt drive via the drive power of the internal combustion engine. In addition, this pump includes in its pump housing a brushless electric motor which can be switched by appropriate control via clutches on the drive shaft, thereby either boosted the driving force of the belt drive, or, in the start-stop state with the internal combustion engine off, the sole circulation of the coolant takes over.

Die in der MTZ, Ausgabe 11, 2010, offenbarte Hybridkühlmittelpumpe ist dabei jedoch nicht geeignet, sämtliche Betriebszustände der Verbrennungskraftmaschine zufriedenstellend zu bedienen.The hybrid coolant pump disclosed in the MTZ, Issue 11, 2010, however, is not suitable for satisfactorily serving all operating states of the internal combustion engine.

Insbesondere ist es bei der in der MTZ, Ausgabe 11, 2010, diskutierten Kühlmittelpumpe nicht möglich, einen raschen Aufwärmzyklus der Verbrennungskraftmaschine durch leckflussfreies Unterbrechen des Kühlmittelstromes zu gewährleisten. Bei derartigen, offenen Kühlmittelpumpen kann nämlich kein so genanntes stehendes Wasser erzeugt werden. Vielmehr ist immer eine gewisse Grundzirkulation des Kühlmittels festzustellen, so dass ein beschleunigter Aufwärmbetrieb nicht realisierbar ist.In particular, in the MTZ, Issue 11, 2010, discussed coolant pump is not possible to ensure a rapid warm-up cycle of the internal combustion engine by leakage flow-free interruption of the coolant flow. In fact, in such open coolant pumps, no so-called stagnant water can be generated. Rather, there is always a certain basic circulation of the coolant to determine, so that an accelerated warm-up operation is not feasible.

Zwar diskutiert der Artikel über die Hybridkühlmittelpumpe aus der MTZ, Ausgabe 11, 2010, dass derartige Pumpen antriebslos geschalten werden können, um auf diese Art und Weise einen beschleunigten Aufwärmvorgang in der Verbrennungskraftmaschine durchzuführen.Although the article on the hybrid coolant pump from the MTZ, Issue 11, 2010 discusses that such pumps can be switched without drive, in this way to perform an accelerated warm-up operation in the internal combustion engine.

Gleichwohl ist es mit der Hybridkühlmittelpumpe dieser Bauart nicht möglich, einen Rückfluss bzw. Leckfluss des Kühlmittels aus der Pumpe zu vermeiden, wodurch minimale Zirkulationen entstehen können, die den Aufwärmvorgang als solche verzögern.However, with the hybrid coolant pump of this type, it is not possible to prevent backflow or leakage of the coolant from the pump, which may cause minimal circulation that retards the warm-up process as such.

Überdies ist es mit der in der MTZ, Ausgabe 11, 2010, offenbarten Pumpe nicht möglich, in Abhängigkeit von unterschiedlichen Betriebszuständen der Verbrennungskraftmaschinen, beispielsweise Leerlauf-Betriebszustand, Schubbetrieb oder dergleichen, entsprechend geeignete Kühlmitteizirkulationsflussraten einzustellen, sodass die Kühlmitteltemperatur für den jeweiligen Betriebszustand in einem idealen Kühlmitteltemperaturbereich gehalten werden kann.Moreover, it is not possible with the MTZ, Issue 11, 2010, disclosed pump, depending on different operating conditions of the internal combustion engines, such as idle mode, overrun or the like to set appropriate Kühlmitteizirkulationsflussraten so that the coolant temperature for the respective operating state in a ideal coolant temperature range can be maintained.

Auch zeigt die in der MTZ, Ausgabe 11, 2010 offenbart Pumpe den Nachteil, dass bei Betrieb der Pumpe über die Riemenscheibe, und somit über die Verbrennungskraftmaschine der im Pumpengehäuse angeordnete Elektromotor als Generator wirkt. Die erzeugte elektrische Leistung muss daher entsprechend aus der Pumpe abgeführt und in das Bordnetz eingespeist werden. Um die Generatorwirkung der elektrischen Pumpe zu vermeiden ist es alternativ nötig, selbige von der Welle zu isolieren, wenn der Betrieb der elektrischen Pumpe nicht benötigt wird.Also, the pump disclosed in the MTZ, Issue 11, 2010 shows the disadvantage that, when the pump is operated via the belt pulley, and thus via the internal combustion engine, the electric motor arranged in the pump housing acts as a generator. The generated electrical power must therefore be discharged accordingly from the pump and fed into the electrical system. In order to avoid the generator effect of the electric pump, it is alternatively necessary to isolate selbige of the shaft when the operation of the electric pump is not needed.

Hierdurch wird der Aufbau einer derartigen Hybridpumpe noch komplexer, wodurch die Kosten für das System über das wirtschaftlich sinnvolle Maß ansteigen. Auch der mit einer derartigen Pumpe erzielbare Wirkungsgrad ist, im Vergleich zu herkömmlichen Systemen eher gering.As a result, the structure of such a hybrid pump is even more complex, which increases the cost of the system over the economically meaningful measure. Also achievable with such a pump efficiency is rather low compared to conventional systems.

ZUSAMMENFASSUNG DER ERFINDUNGSUMMARY OF THE INVENTION

Ausgehend von den Nachteilen des vorstehend beschriebenen Standes der Technik ist es Aufgabe der vorliegenden Erfindung, ein Kühlsystem zu schaffen, das einen einfachen Aufbau zeigt, und mit dem auf einfache Weise ein Kühlmittelstrom in einem Kühlmittelkreislauf einer Verbrennungskraftmaschine auch dann gewährleistet ist, wenn die Verbrennungskraftmaschine antriebslos ist. Die vorliegende Erfindung soll ferner ein Kühlsystem schaffen, mittels dem abhängig von verschiedenen Betriebszuständen der Verbrennungskraftmaschine unterschiedliche Kühlwirkungen erzielt werden können.Based on the disadvantages of the above-described prior art, it is an object of the present invention to provide a cooling system which shows a simple structure, and with a simple way, a coolant flow in a coolant circuit of an internal combustion engine is ensured even when the internal combustion engine without drive is. The present invention is intended Furthermore, create a cooling system by means of which different cooling effects can be achieved depending on different operating conditions of the internal combustion engine.

Diese Aufgabe wird gelöst mit dem Kühlsystem nach Anspruch 1.This object is achieved with the cooling system according to claim 1.

Erfindungsgemäß wird dabei ein regelbares Kühlsystem für ein Kraftfahrzeug, vorgeschlagen, das einen Kühlmittelkreislauf zum Zuführen und Abführen von Kühlmittel zu und von einer Verbrennungskraftmaschine des Fahrzeugs aufweist. In diesem Kühlsystem sind eine mechanisch betriebene, regelbare Haupt-Kühlmittelpumpe, die eine Zuführung zum Zuführen des Kühlmittels in die Haupt-Kühlmittelpumpe sowie eine Abführung zum Abführen des Kühlmittels zur Verbrennungskraftmaschine aufweist, sowie eine elektrisch betriebene, regelbare Sekundär-Kühlmittelpumpe, die eine Zuführung zum Zuführen des Kühlmittels in die Sekundär-Kühlmittelpumpe sowie eine Abführung zum Abführen eines als Bypass-Kühlmittelstrom geförderten Kühlmittels in Richtung zur Haupt-Kühlmittelpumpe aufweist angeordnet, wobei die Sekundär-Kühlmittelpumpe von einer in Strömungsrichtung des Kühlmittels zur Haupt-Kühlmittelpumpe führenden Kühlmittelleitung abzweigend in Strömungsrichtung vor der Haupt-Kühlmittelpumpe angeordnet ist. Das mittels der Sekundär-Kühlmittelpumpe geförderte Kühlmittel wird nach der Haupt-Kühlmittelpumpe, ohne die Haupt-Kühlmittelpumpe zu durchströmen, in die zur Verbrennungskraftmaschine führende Abführung zugeführt. Die Sekundär-Kühlmittelpumpe weist ferner ein Pumpengehäuse mit einer darin ausgebildeten Pumpenkammer auf, wobei an einem Abschnitt des Pumpengehäuses ein Elektromotor angeordnet ist, der vermittels einer in die Pumpenkammer reichenden Antriebswelle eine Antriebsleistung für die Sekundär-Kühlmittelpumpe bereit stellt. Ein als Förderorgan dienendes Flügelrad ist in der Pumpenkammer der Sekundär-Kühlmittelpumpe angeordnet, das koaxial auf der Antriebswelle angeordnet und mit dieser antreibbar verbunden ist, wobei die Sekundär-Kühlmittelpumpe einen am Flügelrad ausgebildeten Regelschieber aufweist, der zumindest in eine Offen- und Geschlossen-Stellung verfahrbar ist, zur Regelung des von der Sekundär-Kühlmittelpumpe geförderten Bypass-Kühlmittelstromes, insbesondere zur Verhinderung des Rückströmens des Kühlmittels entgegen der Förderrichtung der Sekundär-Kühlmittelpumpe.According to the invention, a controllable cooling system for a motor vehicle is proposed, which has a coolant circuit for supplying and discharging coolant to and from an internal combustion engine of the vehicle. In this cooling system are a mechanically operated, controllable main coolant pump having a supply for supplying the coolant in the main coolant pump and a discharge for discharging the coolant to the internal combustion engine, and an electrically operated, controllable secondary coolant pump, which is a supply to Supplying the coolant into the secondary coolant pump and a discharge for discharging a conveyed as bypass coolant flow in the direction of the main coolant pump, wherein the secondary coolant pump from a leading coolant in the flow direction of the coolant to the main coolant pump coolant line branching in the flow direction the main coolant pump is arranged. The pumped by the secondary coolant pump coolant is fed to the main coolant pump, without flowing through the main coolant pump, leading to the internal combustion engine exhaust. The secondary coolant pump furthermore has a pump housing with a pump chamber formed therein, wherein an electric motor is arranged on a portion of the pump housing, which provides a drive power for the secondary coolant pump by means of a drive shaft extending into the pump chamber. Serving as a conveyor organ impeller is arranged in the pump chamber of the secondary coolant pump, which is arranged coaxially on the drive shaft and is drivably connected thereto, wherein the secondary coolant pump has a control valve formed on the impeller, at least in an open and closed position can be moved, for controlling the funded by the secondary coolant pump bypass coolant flow, in particular for Preventing the return flow of the coolant against the conveying direction of the secondary coolant pump.

Vermittels des erfindungsgemäßen Kühlsystems sind dabei folgende Vorteile erzielbar.By means of the cooling system according to the invention, the following advantages can be achieved.

Durch die parallele Verwendung einer mechanischen Pumpe als Haupt-Kühlmittelpumpe und einer elektrischen Pumpe als Sekundär-Kühlmittelpumpe kann auf verblüffend einfache und kostengünstige Weise ein Kühlsystem geschaffen werden, das einen einfachen Aufbau zeigt, und mit dem auf einfache Weise ein Kühlmittelstrom in einem Kühlmittelkreislauf einer Verbrennungskraftmaschine auch dann gewährleistet ist, selbst wenn die Verbrennungskraftmaschine antriebslos ist und somit keine Antriebsleistung für die mechanisch betriebene Haupt-Kühlmittelpumpe erzeugen kann.By the parallel use of a mechanical pump as a main coolant pump and an electric pump as a secondary coolant pump, a cooling system can be created in a surprisingly simple and cost-effective manner, showing a simple structure, and with the simple way a coolant flow in a coolant circuit of an internal combustion engine is ensured even then, even if the internal combustion engine is de-energized and thus can not generate drive power for the mechanically operated main coolant pump.

Hierbei bleibt in vorteilhafter Weise die in der Praxis bewährte, mechanisch betriebene Kühlmittelpumpe in dem Kühlsystem erhalten, wodurch beim Betrieb des Kühlsystems mit der mechanischen Pumpe, ggf. unterstützt durch die elektrische Pumpe, hohe Wirkungsgrade erzielt werden können. Die mit dem erfindungsgemäßen Kühlsystem erzielbaren Wirkungsgrade liegen dabei signifikant höher als dies bei einer vorstehend diskutierten Einwellen-Hybridpumpe der Fall ist.In this case, the proven in practice, mechanically operated coolant pump is maintained in the cooling system in an advantageous manner, whereby during operation of the cooling system with the mechanical pump, possibly supported by the electric pump, high efficiencies can be achieved. The achievable with the cooling system according to the invention efficiencies are significantly higher than is the case with a single-shaft hybrid pump discussed above.

Vermittels des erfindungsgemäßen Kühlsystems, das die beiden diskutierten regelbaren Pumpen aufweist, ist es ferner vorteilhaft möglich, so genanntes stehendes Wasser bereitzustellen, das, insbesondere beim Kaltstart der Verbrennungskraftmaschine, ein schnelles Aufwärmen der Verbrennungskraftmaschine ermöglicht, so dass das Fahrzeug innerhalb kürzester Zeit in einem optimalen Temperatur-Kraftstoffverbrauch-Bereich betrieben werden kann.By means of the cooling system according to the invention, which has the two discussed controllable pumps, it is also advantageously possible to provide so-called stagnant water, in particular during cold start of the internal combustion engine, a rapid warm-up of the internal combustion engine allows, so that the vehicle within a very short time in an optimal Temperature fuel consumption range can be operated.

Durch das Ansteuern des Schiebers in der Sekundär-Kühlmittelpumpe, insbesondere das Verfahren des Schiebers in dessen Geschlossen-Stellung, kann dabei vorteilhaft sichergestellt werden, dass aufgrund fehlender bzw. abgeschalteter Pumpwirkung von der Verbrennungskraftmaschine zurückströmendes Kühlmittel entgegen der Förderrichtung der Sekundärkühlmittelpumpe in Richtung auf den Fahrzeugkühler zu fließt.By controlling the slide in the secondary coolant pump, in particular the method of the slide in its closed position, can be advantageously ensured that due to lack of or switched off pumping back from the internal combustion engine coolant against the conveying direction of the secondary coolant pump to flow towards the vehicle radiator.

Durch die Verwendung der bereits bekannten, mechanisch betriebenen regelbaren Haupt-Kühlmittelpumpe und die zusätzliche, parallele Anordnung der regelbaren, elektrisch betriebenen Sekundär-Kühlmittelpumpe kann ferner ein Kühlsystem realisiert werden, das bei überschaubaren Entwicklungs- und Applikationskosten eine zuverlässige Kühlleistung bei modernen, Kraftstoff sparenden Motorkonzepten, beispielsweise mit Start-Stop-Automatik, Motorabschaltung im Segelbetrieb oder dergleichen, sicherstellt.By using the already known, mechanically operated controllable main coolant pump and the additional, parallel arrangement of the controllable, electrically operated secondary coolant pump, a cooling system can also be realized which, with manageable development and application costs, a reliable cooling performance in modern fuel-saving engine concepts , For example, with automatic start-stop, engine shutdown in sailing or the like, ensures.

Hierbei ist es ferner nicht notwendig, durch die integrale Ausbildung von mechanisch betriebener und elektrisch betriebener Kühlmittelpumpe, wie dies in der vorgenannten Hybridpumpe, die in der MTZ Ausgabe 11, 2010 offenbart ist, diskutiert wird, neue Lagerungs- und Dichtungssysteme für die Wasserpumpenwelle zu implementieren, deren Dauerbetriebsfestigkeit und Wirtschaftlichkeit sich erst nach einigen Jahren zeigt.It is also not necessary to implement new storage and sealing systems for the water pump shaft through the integral design of mechanically operated and electrically operated coolant pump, as discussed in the aforementioned hybrid pump, which is disclosed in the MTZ edition 11, 2010 , whose continuous operation and profitability only show up after a few years.

Vielmehr ist es mit dem erfindungsgemäßen Kühlsystem möglich, auf die in der Praxis vielfach bewährten Lagerungs- und Dichtungssysteme zuzugreifen, wodurch ein zuverlässiger und wirtschaftlicher Betrieb des Kühlsystems sichergestellt werden kann.Rather, it is possible with the cooling system according to the invention to access the proven in practice storage and sealing systems, whereby a reliable and economical operation of the cooling system can be ensured.

Weitere Ausgestaltungen des erfindungsgemäßen Kühlsystems sind Gegenstand der Unteransprüche.Further embodiments of the cooling system according to the invention are the subject of the dependent claims.

Gemäß einer Ausführungsform weist die Haupt-Kühlmittelpumpe hierbei ein Pumpengehäuse mit einer darin ausgebildeten Pumpenkammer auf, wobei in der Pumpenkammer ein als Förderorgan dienendes Flügelrad angeordnet ist, das über eine in die Pumpenkammer reichende Welle angetrieben wird, die vorzugsweise von einem Riemenantrieb angetrieben wird.According to one embodiment, the main coolant pump in this case has a pump housing with a pump chamber formed therein, wherein in the pump chamber serving as a conveyor organ impeller is arranged, which is driven via a reaching into the pump chamber shaft, which is preferably driven by a belt drive.

Die Haupt-Kühlmittelpumpe kann hierbei, gemäß einer Ausführungsform als Axial- oder Radialpumpe ausgebildet sein.The main coolant pump may in this case be designed as an axial or radial pump according to one embodiment.

Durch den Antrieb der Haupt-Kühlmittelpumpe über eine mit einer Riemenscheibe der Verbrennungskraftmaschine verbundene Riemenscheibe ist es vorteilhaft möglich, ohne zusätzliche Antriebsaggregate die Haupt-Kühlmittelpumpe anzutreiben. Überdies bringt die Verwendung des von der laufenden Verbrennungskraftmaschine angetriebenen Riemenantriebs nahezu keine Reibungsverluste mit sich, so dass die Haupt-Kühlmittelpumpe mit hohem Wirkungsgrad betrieben werden kann.By driving the main coolant pump via a pulley connected to a pulley of the internal combustion engine, it is advantageously possible to drive the main coolant pump without additional drive units. Moreover, the use of the belt driven by the current internal combustion engine belt drive brings almost no friction losses, so that the main coolant pump can be operated with high efficiency.

Ferner bringt die Verwendung des Riemenantriebs, der die Antriebskraft der Verbrennungskraftmaschine nutzt den Vorteil mit sich, dass selbst bei niedriger Drehzahl der Verbrennungskraftmaschine noch eine Rotationsbewegung des Flügelrades in der Haupt-Kühlmittelpumpe erzeugt werden kann, wodurch dieses selbst bei niedriger Drehzahl eine Kühlmittelzirkulation sicherstellt, wodurch zuverlässig ein Überhitzen des Motors vermieden werden kann.Further, the use of the belt drive utilizing the driving force of the internal combustion engine has the advantage that even at low engine speed, the impeller can still be rotated in the main coolant pump, thereby ensuring coolant circulation even at low speed reliable overheating of the engine can be avoided.

Die Haupt-Kühlmittelpumpe weist gemäß einer weiteren Ausführungsform ferner einen am Flügelrad ausgebildeten, koaxial zu selbigem angeordneten, Regelschieber auf, der zumindest in eine Offen- und Geschlossen-Stellung, vorzugsweise entlang des in der Pumpenkammer gelagerten Flügelrades, verfahrbar ist, zur Regelung des von der Haupt-Kühlmittelpumpe geförderten Kühlmittelstromes.According to a further embodiment, the main coolant pump also has a control slide which is arranged coaxially with the impeller and which is movable, at least in an open and closed position, preferably along the impeller mounted in the pump chamber, for controlling the control of the main coolant pump funded coolant flow.

Vermittels des erfindungsgemäß in der Haupt-Kühlmittelpumpe angeordneten Regelschiebers ist es dabei vorteilhaft möglich, den Kühlmittelstrom gewollt zu unterbrechen, ohne dabei den Betrieb der Haupt-Kühlmittelpumpe zu unterbrechen. So kann der Schieber nämlich, beispielsweise zum Erzeugen von stehendem Wasser beim Kaltstart der Verbrennungskraftmaschine, in seine Geschlossen-Stellung verfahren werden, in der er das Flügelrad umfasst und die Weiterführung des geförderten Kühlmittels aus der Ableitung verhindert, somit den vom Flügelrad geförderten Kühlmittelstrom unterbricht.By means of the present invention arranged in the main coolant pump control slide, it is advantageously possible to interrupt the coolant flow intentionally, without interrupting the operation of the main coolant pump. Thus, the slider can namely, for example, for generating stagnant water at cold start of the internal combustion engine, are moved to its closed position in which it includes the impeller and prevents the continuation of the pumped coolant from the derivative, thus interrupting the promoted by the impeller coolant flow.

Das Anordnen eines derartigen Schiebers koaxial zum Flügelrad vereinfacht zudem die Gesamtkonstruktion der Haupt-Kühlmittelpumpe. So ist nämlich kein Freilauf oder dergleichen notwendig, um die Übertragung der Antriebsleistung der Verbrennungskraftmaschine auf die Antriebswelle der Haupt-Kühlmittelpumpe zu unterbrechen. Vielmehr ist es möglich, durch Verschieben des Regelschiebers entlang der Antriebswelle der Haupt-Kühlmittelpumpe die Kühlmittelzirkulation durch die Haupt-Kühlmittelpumpe zu unterbrechen, ohne hierbei die Übertragung der Antriebsleistung der Verbrennungskraftmaschine auf die Antriebswelle der Haupt-Kühlmittelpumpe aufzuheben.Placing such a slider coaxial with the impeller also simplifies the overall construction of the main coolant pump. Thus, no free-wheel or the like is necessary to interrupt the transmission of the drive power of the internal combustion engine to the drive shaft of the main coolant pump. Rather, it is possible to interrupt the circulation of coolant through the main coolant pump by displacing the control slide along the drive shaft of the main coolant pump, without thereby canceling the transmission of the drive power of the internal combustion engine to the drive shaft of the main coolant pump.

Gemäß einer Ausführungsform ist der Elektromotor der Sekundär-Kühlmittelpumpe als Trockenläufer oder als Nassläufer ausgebildet ist.According to one embodiment, the electric motor of the secondary coolant pump is designed as a dry runner or as a wet rotor.

Die Verwendung eines als Trockenläufer konzipierten Elektromotors für die Sekundär-Kühlmittelpumpe ermöglicht dabei vorteilhaft hohe Drehzahlen der Sekundär-Kühlmittelpumpe bei minimaler Baugröße.The use of a designed as a dry rotor electric motor for the secondary coolant pump allows advantageously high speeds of the secondary coolant pump with a minimum size.

Die alternative Verwendung eines als Naßläufer konzipierten Elektromotors für die Sekundär-Kühlmittelpumpe stellt eine vergleichsweise einfache Kühlung für den Elektromotor sicher, da hierzu das im Kühlkreislauf des Fahrzeugs ohnehin vorhandene Kühlmittel zur Anwendung kommen kann.The alternative use of a designed as a wet rotor electric motor for the secondary coolant pump ensures a comparatively simple cooling for the electric motor, since this can be used in the cooling circuit of the vehicle anyway existing coolant.

Durch die Verwendung derartiger Elektromotoren ist es vorteilhaft möglich, bei geringer Baugröße eine als elektrische Einheitspumpe konzipierte Sekundär-Kühlmittelpumpe zu schaffen, die hohe Stückzahlen bei geringen Herstellungskosten erlaubt.By using such electric motors, it is advantageously possible to create a small size designed as a single-pump electrical secondary coolant pump that allows high volumes at low cost.

Das Kühlsystem gemäß einer weiteren Ausführungsform weist ferner eine Steuervorrichtung auf, welche die Haupt-Kühlmittelpumpe und/oder die Sekundär-Kühlmittelpumpe in Abhängigkeit von vergebenen Betriebszuständen der Verbrennungskraftmaschine steuert.The cooling system according to a further embodiment further comprises a control device which controls the main coolant pump and / or the secondary coolant pump in dependence on assigned operating states of the internal combustion engine.

Durch die erfindungsgemäß vorgesehene Steuervorrichtung, die beispielsweise als Softwaremodul im Fahrzeugsteuergerät implementiert ist oder als eigenständige Steuereinheit ausgebildet ist, ist es vorteilhaft möglich, die Haupt-Kühlmittelpumpe und/oder die Sekundär-Kühlmittelpumpe parallel oder unabhängig voneinander anzusteuern, um auf diese Weise immer einen gewünschten Kühlmittelfluss im Kühlkreislauf herzustellen.By inventively provided control device, which is implemented for example as a software module in the vehicle control unit or is designed as an independent control unit, it is advantageously possible to control the main coolant pump and / or the secondary coolant pump in parallel or independently of each other, in this way always a desired Make coolant flow in the cooling circuit.

Insbesondere ist es dabei möglich, die Haupt-Kühlmittelpumpe und/oder die Sekundär-Kühlmittelpumpe derart anzusteuern, dass diese im Aufwärmbetrieb beim Kaltstart der Verbrennungskraftmaschine abgeregelt sind, so dass kein Kühlmittel zirkuliert wird. Sobald die Verbrennungskraftmaschine ihre Betriebstemperatur erreicht hat, können die Pumpen parallel oder separat voneinander geregelt werden, um durch jeweiliges Verschieben des in der jeweiligen Pumpenkammer angeordneten Regelschiebers den Kühlmittelfluss zu steuern.In particular, it is possible to control the main coolant pump and / or the secondary coolant pump in such a way that they are decelerated in the warm-up mode during the cold start of the internal combustion engine, so that no coolant is circulated. Once the internal combustion engine has reached its operating temperature, the pumps can be controlled in parallel or separately from each other to control the coolant flow by respective displacement of the arranged in the respective pump chamber control valve.

Vermittels dieser Steuerung ist es dabei vorteilhaft möglich, in Abhängigkeit von bestimmten Betriebszuständen der Verbrennungskraftmaschine, beispielsweise wenn diese im Leerlauf ist, oder des Fahrzeugs, beispielsweise bei einer Stadtfahrt, die Kühlmitteltemperatur unter Verwendung von Kennfeldem aktiv zu steuern, so dass die Kühlmitteltemperatur in einem Bereich gehalten werden kann, in dem eine optimale Kraftstoffausnutzung, und somit ein sparsamer und wirtschaftlicher Betrieb des Fahrzeugs, realisiert werden kann.By means of this control, it is advantageously possible, depending on certain operating conditions of the internal combustion engine, for example when it is idling, or the vehicle, for example in a city driving, to actively control the coolant temperature using maps, so that the coolant temperature in one area can be maintained, in which an optimal fuel economy, and thus a more economical and economical operation of the vehicle, can be realized.

Ein weiterer Aspekt der vorliegenden Erfindung ist es, eine für ein derartiges Kühlsystem geeignete, elektrisch betriebene Kühlmittelpumpe anzubieten.Another aspect of the present invention is to provide an electrically operated coolant pump suitable for such a cooling system.

Die mit dem vorstehend diskutierten Kühlsystem erzielbaren Vorteile lassen sich in analoger Weise auch mit der nachfolgend diskutierten, erfindungsgemäßen elektrischen Kühlmittelpumpe erzielen, so dass auf eine erneute Aufzählung dieser Vorteile verzichtet wird.The advantages achievable with the cooling system discussed above can also be achieved in an analogous manner with the electric coolant pump according to the invention discussed below, so that a renewed enumeration of these advantages is dispensed with.

Eine elektrisch betriebene Kühlmittelpumpe gemäß einer Ausführungsform der Erfindung, die insbesondere zur Verwendung in einem vorstehend diskutierten Kühlsystem geeignet ist, ist dabei als Axialpumpe oder als Radialpumpe ausgebildet. Die elektrisch betriebene Kühlmittelpumpe weist auf: ein Pumpengehäuse; eine, vorzugsweise flanschartige, Zuführung und eine, vorzugsweise flanschartige, Abführung; eine im Pumpengehäuse ausgebildete Pumpenkammer, wobei in der Pumpenkammer auf einer Pumpenwelle ein Pumpenrad angeordnet ist, das mittels der Pumpenwelle von einem Elektromotor antreibbar ist, und einen Schieber, der zumindest in eine Offen- und Geschlossen-Stellung verfahrbar ist, zur Regelung eines von der Kühlmittelpumpe geförderten Bypass-Kühlmittelstromes. Die erfindungsgemäße elektrisch betriebene Pumpe ist dabei derart ansteuerbar, dass bei der Geschlossen Stellung des Regelschiebers ein Rückströmen des Kühlmittels von der Verbrennungskraftmaschine entgegen der Förderrichtung der Sekundär-Kühlmittelpumpe verhindert werden kann.An electrically operated coolant pump according to an embodiment of the invention, which is particularly suitable for use in a cooling system discussed above, is designed as an axial pump or as a radial pump. The electrically operated coolant pump comprises: a pump housing; a, preferably flange-like, supply and a, preferably flange-like, discharge; a pump chamber formed in the pump housing, wherein in the pump chamber on a pump shaft, an impeller is arranged, which is driven by means of the pump shaft of an electric motor, and a slide which is movable at least in an open and closed position, for controlling one of the Coolant pump promoted bypass coolant flow. The electrically operated pump according to the invention is in this case activatable such that in the closed position of the control slide, a return flow of the coolant from the internal combustion engine counter to the conveying direction of the secondary coolant pump can be prevented.

Durch das Ansteuern des Schiebers in der elektrisch betriebenen Pumpe derart, dass der Schiebers in seine Geschlossen-Stellung fährt, kann dabei vorteilhaft sichergestellt werden, dass aufgrund fehlender bzw. abgeschalteter Pumpwirkung von der Verbrennungskraftmaschine zurückströmendes Kühlmittel entgegen der Förderrichtung der Kühlmittelpumpe in Richtung auf den Fahrzeugkühler zu fließt.By controlling the slide in the electrically operated pump in such a way that the slide moves into its closed position, it can advantageously be ensured that coolant flowing back from the internal combustion engine due to lacking or switched off pumping action counter to the conveying direction of the coolant pump in the direction of the vehicle radiator to flow.

Bei der Parallelschaltung zweier Pumpen ist zu beachten, dass die parallelen Strömungspfade auch Bypasspfade darstellen. Das zu fördernde Medium fließt dabei immer in die Richtung des niedrigeren Drucks.When connecting two pumps in parallel, it should be noted that the parallel flow paths also represent bypass paths. The medium to be pumped always flows in the direction of the lower pressure.

Da die Haupt-Kühlmittelpumpe im laufenden Betrieb einen deutlich höheren Förderdruck aufbaut, kann durch Verschieben des Regelschiebers der Sekundär-Kühlmittelpumpe in dessen Geschlossen-Stellung sichergestellt werden, dass bei aktiver Hauptpumpe eine Rückströmung von der Druckseite der Hauptpumpe über die Sekundärpumpe zur Saugseite unterbunden wird.Since the main coolant pump builds a significantly higher delivery pressure during operation, it can be ensured by moving the control slide of the secondary coolant pump in its closed position that when the main pump is active, a return flow from the pressure side of the main pump via the secondary pump to the suction side is prevented.

Gemäß einer Ausführungsform ist die elektrische Kühlmittelpumpe als Radialpumpe ausgebildet, wobei mit der, im Wesentlichen konisch verlaufenden, Zuführung das von einer Kühlmittelleitung abgezweigte, zu fördernde Kühlmittel in die im Pumpengehäuse ausgebildete Pumpenkammer einbringbar ist, und mit der, im Wesentlichen radial rechtwinklig zur Zufuhrleitung angeordneten, Abführung das in die Pumpenkammer eingebrachte Kühlmittel aus der Pumpenkammer abführbar ist.According to one embodiment, the electric coolant pump is designed as a radial pump, wherein with the, substantially conically extending supply branched off from a coolant line to be conveyed coolant in the pump housing formed in the pump chamber can be introduced, and arranged with the, substantially radially perpendicular to the supply line , Leaching the introduced into the pump chamber coolant from the pump chamber can be discharged.

Das in der Pumpenkammer angeordnete, als Radialpumpen-Flügelrad ausgebildete Pumpenrad saugt das Kühlmittel durch eine Rotationsbewegung in axialer Richtung an und fördert es in radialer Richtung in die Abführung. Der Schieber ist als ein koaxial zur Pumpenwelle am Flügelrad angeordneter Regelschieber ausgebildet; und der Elektromotor ist, vorzugsweise an einem von der Zuführung abgewandten, Abschnitt des Pumpengehäuses angeordnet; wobei der Elektromotor eine Antriebswelle aufweist, die in die Pumpenkammer hineinragt, das Flügelrad und der Regelschieber koaxial auf der Antriebswelle angeordnet sind, und vorzugsweise vermittels Halteelementen formschlüssig auf der Antriebswelle gehalten werden, und der Regelschieber das Flügelrad umgreifend, zylindrisch ausgebildet ist und in axialer Richtung des Flügelrades in eine Offen- und Geschlossen-Stellung verschiebbar ist.The impeller arranged in the pump chamber, designed as a radial pump impeller, sucks the coolant by means of a rotational movement in the axial direction and conveys it in the radial direction into the discharge. The slide is designed as a coaxial with the pump shaft arranged on the impeller control slide; and the electric motor is arranged, preferably at a portion of the pump housing facing away from the supply; wherein the electric motor has a drive shaft which projects into the pump chamber, the impeller and the control slide are arranged coaxially on the drive shaft, and are preferably held by means of holding elements form-fitting manner on the drive shaft, and the control slide the impeller encompassing, cylindrical and in the axial direction the impeller is displaceable in an open and closed position.

Gemäß einer Ausführungsform ist der Regelschieber derart mit dem Flügelrad verbunden, dass Flügelschaufeln des Flügelrades den Regelschieber durchdringen.According to one embodiment, the control slide is connected to the impeller so that vanes of the impeller penetrate the control slide.

Auf diese Weise ist es möglich, den benötigten Bauraum für die elektrische Kühlmittelpumpe deutlich zu verringern, da die aus dem Flügelrad und dem Regelschieber bestehende Baugruppe kompakt ausgebildet ist.In this way it is possible to significantly reduce the space required for the electric coolant pump, since the existing of the impeller and the control slide assembly is compact.

Gemäß einer Ausführungsform ist der Elektromotor als Trockenläufer ausgebildet und vermittels einer an der Antriebswelle angeordneten Wellendichtung gegen die Pumpenkammer abgedichtet. In einer alternativen Ausführungsform ist der Elektromotor als Nassläufer ausgebildet und wird vermittels des von der Kühlmittelpumpe geförderten Kühlmittels gekühlt.According to one embodiment, the electric motor is designed as a dry rotor and sealed by means of a arranged on the drive shaft shaft seal against the pump chamber. In an alternative embodiment, the electric motor is designed as a wet rotor and is cooled by means of the coolant pumped by the coolant pump.

Gemäß einer Ausführungsform wird der Regelschieber über zumindest ein in dem Pumpengehäuse vorgesehenes Stellglied in seine Offen- und/oder Geschlossen Stellung verfahren. Dieses Stellglied kann dabei als ein pneumatisch, magnetisch und/oder hydraulisch betriebener Schieber oder als ein elektrischer Stellmotor ausgebildet sein.According to one embodiment, the control slide is moved over at least one provided in the pump housing actuator in its open and / or closed position. This actuator can be designed as a pneumatically, magnetically and / or hydraulically operated slide or as an electric servomotor.

Das Stellglied kann in einer beispielhaften Ausführungsform in einem Stirnbereich der Antriebswelle angeordnet sein und in einen an der Vorderseite des Regelschiebers ausgebildeten, kammerartig geformten Abschnitt eingreifen, um den Regelschieber relativ zum Flügelrad in seine Offen- und Geschlossen-Stellung zu verschieben.The actuator may, in an exemplary embodiment, be disposed in an end region of the drive shaft and engage in a chamber-like shaped section formed on the front of the control slide to move the control slide to its open and closed positions relative to the impeller.

Alternativ, oder zusätzlich, kann das Stellglied auch zwischen dem Flügelrad und dem Regelschieber angeordnet sein. Beispielsweise ist das Stellglied ein das Flügelrad mit dem Regelschieber verbindender Kipphebel, der hydraulisch, pneumatisch oder magnetisch aus seiner am Flügelrad anliegenden Ruhestellung (die Offen-Stellung des Regelschiebers) in eine vom Flügelrad beabstandete Position (die Geschlossen-Stellung des Regelschiebers) bewegbar ist.Alternatively, or in addition, the actuator may also be arranged between the impeller and the control slide. For example, the actuator is a rocker arm connecting the impeller with the control slide, which is hydraulically, pneumatically or magnetically movable from its at rest on the impeller (the open position of the control slide) in a position spaced from the impeller (the closed position of the control slide).

Das Stellglied kann auch in der Wandung des Pumpengehäuses ausgebildet sein, beispielsweise in hierfür vorgesehenen Ausnehmungen oder Kammern.The actuator may also be formed in the wall of the pump housing, for example in recesses or chambers provided for this purpose.

Gemäß einer weiter Ausführungsform weist der Regelschieber einen die Antriebswelle umgreifenden, der Zuführung zugewandten, kammerartig geformten Abschnitt auf, an dessen Innenumfang ein Gewindeabschnitt ausgebildet ist, wobei an einem vom Elektromotor abgewandten Abschnitt der Antriebswelle der elektrischen Kühlmittelpumpe ein Gewindeabschnitt ausgebildet ist, der komplementär zum Gewindeabschnitt des Regelschiebers ist. Der Regelschieber ist dabei erfindungsgemäß, durch gegenseitiges Eingreifen der Gewindeabschnitte ineinander, entlang der Antriebswelle verschiebbar.According to a further embodiment, the control slide on the drive shaft encompassing, the supply facing, a chamber-like shaped portion, on the inner circumference of a threaded portion is formed, wherein on a side remote from the electric motor portion of the drive shaft of the electric coolant pump, a threaded portion is formed, which is complementary to the threaded portion of the control slide is. The control slide is inventively, by mutual engagement of the threaded portions into one another, along the drive shaft slidably.

Durch das Anordnen der komplementär ausgebildeten Gewindeabschnitte kann in vorteilhafter Weise ein zusätzlicher Antrieb für den Regelschieber in der elektrischen Kühlmittelpumpe vermieden werden, wodurch die Kosten sowie der Aufbau der Pumpe weiter vereinfacht werden könne und gleichzeitig der für die Pumpe benötigte Bauraum verringert werden kann.By arranging the complementarily formed threaded portions may advantageously be an additional drive for the control slide in the electrical Coolant pump can be avoided, whereby the cost and construction of the pump could be further simplified while the space required for the pump space can be reduced.

Gemäß einer weiteren Ausführungsform ist der Regelschieber derart ausgebildet, dass er der Kontur der Vorderseite des Flügelrades folgt und an seinem äußeren Ende ein daran angeordnetes, radial umlaufendes Schließelement aufweist, wobei an einem vom Elektromotor abgewandten Ende des Schließelements ein radial außerhalb vom Regelschieber angeordnetes erstes Dichtungselement angeordnet ist.According to a further embodiment, the control slide is designed such that it follows the contour of the front of the impeller and at its outer end has a radially disposed closing element arranged thereon, wherein at a side remote from the electric motor end of the closing element a radially outside of the control slide arranged first sealing element is arranged.

Gemäß einer weiteren Ausführungsform der elektrischen Kühlmittelpumpe ist in der Pumpenkammer eine Aufnahme ausgebildet, in die das Schließelement des Regelschiebers in dessen Offen-Stellung einbringbar ist.According to a further embodiment of the electric coolant pump, a receptacle is formed in the pump chamber into which the closing element of the control slide in its open position can be introduced.

Durch die Ausbildung dieser Aufnahme kann die Baugröße der Kühlmittelpumpe vorteilhaft weiter verringert werden, da kein zusätzlicher Raum für das Schließelement des Regelschiebers innerhalb der Pumpenkammer geschaffen werden muss.Due to the design of this recording, the size of the coolant pump can advantageously be further reduced because no additional space for the closing element of the control slide must be created within the pump chamber.

Gemäß einer Ausführungsform der Kühlmittelpumpe ist an einem dem Elektromotor zugewandten, radial äußeren Ende des Flügelrades ein radial innerhalb vom Regelschieber angeordnetes, zweites Dichtungselement angeordnet. Der Durchmesser des ersten Dichtungselements kann dabei gemäß einer bevorzugten Ausführungsform größer ausgestaltet sein als der Durchmesser des zweiten Dichtungselements.According to one embodiment of the coolant pump, a second sealing element arranged radially inside the control slide is arranged on a radially outer end of the impeller facing the electric motor. The diameter of the first sealing element may be made larger than the diameter of the second sealing element according to a preferred embodiment.

Gemäß einer Ausführungsform ist die dabei Abführung der elektrischen Pumpe vermittels des Regelschiebers in dessen Geschlossen-Stellung über das Schließelement, das erste Dichtungselement und das zweite Dichtungselement dicht verschließbar.According to one embodiment, the discharge of the electric pump by means of the control slide in its closed position via the closing element, the first sealing element and the second sealing element is tightly closed.

Durch die Ausbildung des Regelschiebers derart, dass dieser der Kontur der Vorderseite des Flügelrades folgt, kann die Baugruppe aus Flügelrad und Regelschieber kompakt gestaltet werden. Das Vorsehen der Dichtungselement am Regelschieber und am Flügelrad erlaubt zudem in vorteilhafter Weise ein sicheres Abdichten der Abführung aus der elektrischen Pumpe in der Geschlossen-Stellung des Regelschiebers, wobei gleichzeitig das Schließelement des Regelschiebers in dessen Geschlossen-Stellung gegen das Flügelrad abgestützt wird, so dass ein durch das Kühlmittel möglicherweise erzeugter Gegendruck den Regelschieber nicht derart aufbiegen oder bewegen kann, dass ein Leckfluss in der Kühlmittelpumpe erzeugt wird.Due to the design of the control slide so that it follows the contour of the front of the impeller, the assembly of impeller and control slide can be made compact. The provision of the sealing element on the control slide and on the impeller also advantageously allows a safe sealing of the discharge from the electric pump in the closed position of the control slide, wherein at the same time the closing element of the control slide is supported in its closed position against the impeller so that a possibly generated by the coolant back pressure can not bend or move the control slide so that a leakage flow is generated in the coolant pump.

Bei einer weiteren Ausführungsform der erfindungsgemäßen Kühlmittelpumpe ist ferner ein Bremselement vorgesehen, vermittels dem das Flügelrad gegen eine Innenwand des Pumpengehäuses festgelegt werden kann.In a further embodiment of the coolant pump according to the invention, a brake element is further provided, by means of which the impeller can be fixed against an inner wall of the pump housing.

Das Bremselement ist dabei gemäß der einer Ausführungsform am Flügelrad ausgebildet, und besteht vorzugsweise aus einer vorgespannten Bremsfeder oder tellerförmigen Bremsscheibe, die vorzugsweise an ihren radial äußeren Enden, in radialer Richtung nach innen hin im Wesentlichen keilförmig zulaufende, Verdickungen aufweist, wobei das Bremselement vorzugsweise mittels der Verdickungen, mit der an den Elektromotor angrenzenden Innenwand des Pumpengehäuses in Reibeingriff bringbar ist, um das Flügelrad gegen das Pumpengehäuse festzulegen.The brake element is formed according to the one embodiment of the impeller, and preferably consists of a preloaded brake spring or plate-shaped brake disc, preferably at their radially outer ends, in the radial direction inwardly substantially wedge-shaped tapered, having thickenings, wherein the brake element preferably means the thickening, with the adjacent to the electric motor inner wall of the pump housing is frictionally engageable to set the impeller against the pump housing.

Gemäß einer weiteren Ausführungsform ist das Bremselement, insbesondere mit dessen Verdickungen, derart ausgebildet, dass es sich mit zunehmender, durch die Antriebswelle des Elektromotors verursachte, Rotationsgeschwindigkeit des Flügelrades von der Innenwand des Pumpengehäuses löst, um das Flügelrad freizugeben.According to a further embodiment, the braking element, in particular with its thickenings, is designed such that it dissolves with increasing, caused by the drive shaft of the electric motor, the rotational speed of the impeller from the inner wall of the pump housing to release the impeller.

Vermittels dieser Anordnung ist es in vorteilhaft einfacher Weise möglich, das Flügelrad gegen die Pumpenkammerwand festzulegen, wodurch bei Drehung der Antriebswelle nur der Regelschieber in seine Offen- oder Geschlossen-Stellung verfahrbar ist.By means of this arrangement, it is possible in an advantageously simple manner, set the impeller against the pump chamber wall, whereby upon rotation of the drive shaft, only the control slide is moved into its open or closed position.

Wenn der Regelschieber in seiner vollständig offenen Stellung angelangt ist, wird ein Kraftschluß zwischen dem auf der Antriebswelle sitzenden Flügelrad und dem Regelschieber bewirkt, so dass die Rotation der Antriebswelle auf das Flügelrad übertragen wird. Mit zunehmender Rotationsgeschwindigkeit der Antriebswelle löst sich aufgrund der Fliehkraft das Bremselement von der Pumpenkammerwand und gibt die Drehung des Flügelrades frei. Somit lässt sich vorteilhaft ein zuverlässiges Verfahren des Regelschiebers entlang der Antriebswelle realisieren, ohne dass dabei das Flügelrad mit gedreht werden würde.When the control slide has reached its fully open position, a frictional connection between the seated on the drive shaft impeller and the control slide is effected, so that the rotation of the drive shaft to the impeller is transmitted. With increasing rotational speed of the drive shaft due to the centrifugal force, the brake element releases from the pump chamber wall and releases the rotation of the impeller. Thus, a reliable method of the control slide along the drive shaft can be advantageously realized without the impeller would be rotated with it.

Überdies lässt sich in vorteilhafter Weise eine Art Anfahrbetrieb erreichen, wenn der Regelschieber und das Flügelrad miteinander in Eingriff stehen und die Rotation der Antriebswelle durch den Kraftschluß zwischen Flügelrad und Regelschieber auf das Flügelrad übertragen wird. Auf diese Weise kann ein sanftes Anfahren der Pumpleistung der elektrischen Kühlmittelpumpe realisiert werden.Moreover, a kind of starting operation can be achieved in an advantageous manner when the control slide and the impeller are engaged with each other and the rotation of the drive shaft is transmitted by the adhesion between the impeller and control slide on the impeller. In this way, a smooth start of the pump power of the electric coolant pump can be realized.

Die Erfindung schafft ferner ein geeignetes Flügellaufrad sowie ein Verfahren zur Regelung eines Kühlmittelstromes in einem erfindungsgemäßen Kühlsystem.The invention further provides a suitable impeller and a method for controlling a flow of coolant in a cooling system according to the invention.

Die vorstehend diskutierten Vorteile gelten dabei in analoger Weise auch für das erfindungsgemäße Flügelrad sowie das Verfahren zum Regeln des Kühlmittelstromes in einem Kühlsystem.The advantages discussed above also apply analogously to the impeller according to the invention and the method for controlling the coolant flow in a cooling system.

Gemäß einer Ausführungsform weist das Flügelrad dabei auf: eine Mehrzahl von auf der einer Kühlmittel-Zuführung zugewandten Flügelradoberfläche ausgebildeten, vorzugsweise radialpumpentypischen, Flügelschaufeln; eine Aussparung zur Aufnahme einer Antriebswelle; einen mit dem Flügelrad verbundenen Regelschieber; sowie ein am Flügelrad angeordnetes Bremselement.According to one embodiment, the impeller comprises: a plurality of impeller blades, preferably radial pump-shaped, formed on the impeller surface facing a coolant supply; a recess for receiving a drive shaft; a control slide connected to the impeller; and a brake element disposed on the impeller.

Das erfindungsgemäße Flügelrad ist dabei vorteilhaft für die Verwendung in einer vorstehend diskutierten, erfindungsgemäßen Kühlmittelpumpe, sowie einem entsprechendem, diese Kühlmittelpumpe aufweisenden Kühlsystem verwendbar.The impeller according to the invention is advantageous for use in a coolant pump according to the invention discussed above, and a corresponding, this coolant pump having cooling system used.

Bei einer Ausführungsform des Flügelrades weist der Regelschieber an seinem vorderen Ende ein radial außerhalb angeordnetes erstes Dichtungselement auf, wobei das Flügelrad an seinem radial äußeren Ende ein radial innerhalb vom Regelschieber angeordnetes zweites Dichtungselement aufweist.In one embodiment of the impeller, the control slide at its front end to a radially outwardly disposed first sealing element, wherein the impeller has at its radially outer end a radially disposed within the control slide second sealing element.

Der Regelschieber ist, gemäß einer weiteren Ausführungsform, derart integral mit dem Flügelrad ausgebildet, dass die Flügelschaufeln des Flügelrades den Regelschieber in axialer Richtung durchdringen.The control slide is, according to another embodiment, formed integrally with the impeller such that the blades of the impeller penetrate the control slide in the axial direction.

In einer weiteren Ausführungsform des erfindungsgemäßen Flügelrades ist das Bremselement an einer rückseitigen Oberfläche des Flügelrades ausgebildet.In a further embodiment of the impeller according to the invention, the braking element is formed on a rear surface of the impeller.

Gemäß der erfindungsgemäßen Ausführungsform besteht das Bremselement aus einer vorgespannten Bremsfeder oder tellerförmigen Bremsscheibe, die mit einer der rückseitigen Oberfläche des Flügelrades gegenüberliegenden Fläche in Reibeingriff bringbar ist, um das Flügelrad gegen diese Fläche festzulegen.According to the embodiment of the invention, the brake element consists of a preloaded brake spring or plate-shaped brake disc, which is frictionally engageable with an opposite surface of the rear surface of the impeller to set the impeller against this surface.

Gemäß einer weiteren Ausführungsform ist das Bremselement derart ausgebildet, dass dessen Bremswirkung mit zunehmender Rotationsgeschwindigkeit des Flügelrades abnimmt, wobei es sich der rückseitigen Oberfläche des Flügelrades annähert, um das Flügelrad freizugeben.According to a further embodiment, the braking element is designed such that its braking effect decreases with increasing rotational speed of the impeller, wherein it approaches the rear surface of the impeller to release the impeller.

In einer weiteren Ausführungsform des erfindungsgemäßen Flügelrades ist der Regelschieber derart ausgebildet, dass er der Kontur des Flügelrades folgt und an seinem äußeren Ende ein radial umlaufendes Schließelement aufweist.In a further embodiment of the impeller according to the invention, the control slide is designed such that it follows the contour of the impeller and has at its outer end a radially encircling closing element.

Gemäß einer Ausführungsform weist der Regelschieber dabei in seinem Stirnbereich einen hohlen, kammerartig ausgebildeten Abschnitt auf, an dessen Innenumfangswandung ein Gewindeabschnitt ausgebildet ist.According to one embodiment, the control slide in this case in its end region on a hollow, chamber-like portion formed on the inner peripheral wall, a threaded portion is formed.

Ein erfindungsgemäßes Verfahren zum Regeln eines Kühlmittelflusses in einem Kühlsystem eines Kraftfahrzeuges, wobei das Kühlsystem eine durch eine Antriebskraft einer im Fahrzeug angeordneten Verbrennungskraftmaschine mechanisch betriebene, regelbare Haupt-Kühlmittelpumpe sowie eine durch einen separat angeordneten Elektromotor elektrisch betriebene, regelbare Sekundär-Kühlmittelpumpe aufweist, umfasst gemäß einer Ausführungsform folgende Schritte: Erfassen eines aktuellen Betriebszustandes einer Verbrennungskraftmaschine des Fahrzeugs; Erfassen eine Kühlmitteltemperatur eines in einem Kühlmittelkreislauf des Fahrzeugs zirkulierenden Kühlmittels; Auslesen von Steuerparametern aus einem Kühlkreislauf-Kennfeld; Ansteuern der Haupt-Kühlmittelpumpe sowie der Sekundär-Kühlmittelpumpe basierend auf den aus dem Kühlkreislauf-Kennfeld ausgelesenen Steuerparametern; und Regeln des Kühlmittelstroms durch selektives Schalten der Haupt-Kühlmittelpumpe und/oder der Sekundär-Kühlmittelpumpe.An inventive method for controlling a coolant flow in a cooling system of a motor vehicle, wherein the cooling system by a driving force of a vehicle arranged in the internal combustion engine mechanically operated, controllable main coolant pump and by a separately arranged Electric motor electrically operated, controllable secondary coolant pump comprises, according to one embodiment, the following steps: detecting a current operating state of an internal combustion engine of the vehicle; Detecting a coolant temperature of a coolant circulating in a coolant circuit of the vehicle; Reading control parameters from a refrigeration cycle map; Driving the main coolant pump and the secondary coolant pump based on the control parameters read from the cooling cycle map; and controlling the coolant flow by selectively switching the main coolant pump and / or the secondary coolant pump.

Gemäß einer vorteilhaften Ausführungsform des erfindungsgemäßen Verfahrens weist der aktuelle Betriebszustand der Verbrennungskraftmaschine zumindest einen Start-Stop-Zustand, einen Aufwärm-Zustand, einen Niedriglast-Zustand, einen Normallast-Zustand, einen Eco-Zustand, einen Hochdrehzahl-Zustand sowie einen Restwärme-Speicherzustand auf.According to an advantageous embodiment of the inventive method, the current operating state of the internal combustion engine has at least a start-stop state, a warm-up state, a low-load state, a normal load state, an eco state, a high-speed state, and a residual heat storage state on.

Der Start-Stop-Zustand bezeichnet dabei einen Antriebszustand, bei dem die Verbrennungskraftmaschine zeitweilig gestoppt wird, beispielsweise beim Halten an einer roten Ampel oder dergleichen, um auf diese Weise Kraftstoff zu sparen.The start-stop state denotes a drive state in which the internal combustion engine is temporarily stopped, for example, when stopping at a red light or the like, to save fuel in this way.

Der Aufwärmzustand bezeichnet einen Antriebszustand, bei dem, insbesondere beim Kaltstart der Verbrennungskraftmaschine, in dem Kühlsystem aufgrund einer unterbrochenen Zirkulation des Kühlmittels stehendes Wasser erzeugt wird, so dass die Temperatur der Verbrennungskraftmaschine schnell auf ihre optimale Betriebstemperatur gebracht werden kann.The warm-up state means a driving state in which, particularly at the cold start of the internal combustion engine, water standing in the cooling system is generated due to intermittent circulation of the coolant, so that the temperature of the internal combustion engine can be quickly brought to its optimum operating temperature.

Der Niedriglast-Zustand bezeichnet einen Antriebszustand, bei dem die Verbrennungskraftmaschine mit niedriger Drehzahl betrieben wird, beispielsweise im Leerlaufbetrieb.The low-load state means a drive state in which the internal combustion engine is operated at a low speed, for example, in idling operation.

Der Normallast-Zustand bezeichnet einen Antriebszustand, bei dem die Verbrennungskraftmaschine, vorzugsweise im mittleren Drehzahlbereich, betrieben wird, um eine Antriebsleistung auf das Fahrzeug aufzubringen.The normal load state means a drive state in which the internal combustion engine, preferably in the middle speed range, is operated to apply a drive power to the vehicle.

Der Eco-Zustand bezeichnet einen Antriebszustand, bei dem die Verbrennungskraftmaschine normal betrieben wird und vermittels eines Steuereingriffs in das Kühlsystem die Kühlmitteltemperatur in einem erhöhten Bereich gehalten wird, so dass eine effizientere Kraftstoffverbrennung und damit ein sparsamerer Fahrbetrieb möglich ist.The eco-state refers to a driving state in which the internal combustion engine is normally operated, and by means of a control intervention in the cooling system, the coolant temperature is maintained in an increased range, so that a more efficient fuel combustion and thus a more economical driving operation is possible.

Der Hochdrehzahl-Zustand bezeichnet einen Antriebszustand, bei dem die Verbrennungskraftmaschine mit hoher Drehzahl mit erhöhtem Kühlbedarf betrieben wird, beispielsweise bei der Fahrt auf einer Autobahn oder dergleichen.The high-speed state refers to a driving state in which the internal combustion engine is operated at high speed with increased cooling demand, for example when driving on a highway or the like.

Der Restwärme-Speicherzustand bezeichnet schließlich einen Antriebszustand, bei dem die Verbrennungskraftmaschine ausgeschalten ist und die Temperatur des Kühlmittels so lange wie möglich hoch gehalten werden soll, um bei einem erneuten Start der Verbrennungskraftmaschine eine verkürzte Aufwärmphase zu erreichen, wodurch die Verbrennungskraftmaschine schneller in ihrem optimalen Temperaturbereich betrieben werden kann.The residual heat storage state finally designates a drive state in which the internal combustion engine is switched off and the temperature of the coolant is to be kept high as long as possible in order to achieve a shortened warm-up phase when the internal combustion engine is restarted, whereby the internal combustion engine is faster in its optimum temperature range can be operated.

Gemäß einer Ausführungsform umfassen die Steuerparameter in dem Kühlkreislauf-Kennfeld zumindest eine gewünschte Kühlmitteltemperatur, und/oder eine gewünschte Motortemperatur, und/oder eine gewünschte Kühlmittelflussrate und/oder dergleichen.In one embodiment, the control parameters in the refrigeration cycle map include at least a desired coolant temperature, and / or a desired engine temperature, and / or a desired coolant flow rate, and / or the like.

Gemäß einer Ausführungsform des erfindungsgemäßen Verfahrens wird, wenn der aktuelle Betriebszustand der Verbrennungskraftmaschine ein Aufwärm-Zustand ist, die Sekundär-Kühlmittelpumpe in einen AUS-Zustand bei geschlossenem Regelschieber geschalten und ein Kühlmittelstrom durch die Haupt-Kühlmittelpumpe wird vermittels eines in der Haupt-Kühlmittelpumpe angeordneter Regelschiebers unterbrochen, so dass eine Zirkulation des Kühlmittels unterbrochen ist.According to an embodiment of the method according to the invention, when the current operating state of the internal combustion engine is a warm-up state, the secondary coolant pump is switched to an OFF state with the control valve closed and a coolant flow through the main coolant pump is arranged by means disposed in the main coolant pump Control valve interrupted, so that a circulation of the coolant is interrupted.

Gemäß einer Ausführungsform des erfindungsgemäßen Verfahrens wird, wenn der aktuelle Betriebszustand der Verbrennungskraftmaschine ein Start-Stop-Zustand ist, bei dem die Haupt-Kühlmittelpumpe während einer Stop-Phase der Verbrennungskraftmaschine zeitweise antriebslos ist, die Sekundär-Kühlmittelpumpe in einen EIN-Zustand geschalten wird, wodurch das Kühlmittel durch die Sekundär-Kühlmittelpumpe zirkuliert wird.According to an embodiment of the method according to the invention, when the current operating state of the internal combustion engine is a start-stop state in which the main coolant pump is temporarily without power during a stop phase of the internal combustion engine, the secondary coolant pump is switched to an ON state , whereby the coolant is circulated through the secondary coolant pump.

Gemäß einer Ausführungsform des erfindungsgemäßen Verfahrens wird, wenn der aktuelle Betriebszustand der Verbrennungskraftmaschine ein Niedriglast-Zustand ist, ein Kühlmittelstrom durch die Haupt-Kühlmittelpumpe vermittels eines in der Haupt-Kühlmittelpumpe angeordneten Regelschiebers unterbrochen wird und die Sekundär-Kühlmittelpumpe in einen EIN-Zustand geschalten wird, wodurch das Kühlmittel durch die Sekundär-Kühlmittelpumpe zirkuliert wird.According to an embodiment of the method according to the invention, when the current operating state of the internal combustion engine is a low-load state, a coolant flow through the main coolant pump is interrupted by means of a control spool disposed in the main coolant pump and the secondary coolant pump is switched to an ON state , whereby the coolant is circulated through the secondary coolant pump.

Gemäß einer Ausführungsform des erfindungsgemäßen Verfahrens wird, wenn der aktuelle Betriebszustand der Verbrennungskraftmaschine ein Normallast-Zustand ist, die Sekundär-Kühlmittelpumpe in einen AUS-Zustand geschalten und deren Regelschieber geschlossen wird, wodurch das Kühlmittel im Kühlmittelkreislauf durch die Haupt-Kühlmittelpumpe zirkuliert wird.According to an embodiment of the method according to the invention, when the current operating state of the internal combustion engine is a normal load state, the secondary coolant pump is switched to an OFF state and its control valve is closed, whereby the coolant in the coolant circuit is circulated through the main coolant pump.

Gemäß einer Ausführungsform des erfindungsgemäßen Verfahrens wird, wenn der aktuelle Betriebszustand der Verbrennungskraftmaschine ein Eco-Zustand ist, der Betrieb der Haupt-Kühlmittelpumpe vermittels einer am Riemenantrieb der Haupt-Kühlmittelpumpe vorgesehenen Freilaufkupplung selektiv unterbrochen wird oder ein in der Haupt-Kühlmittelpumpe angeordneter Regelschieber derart angesteuert wird, dass der Kühlmittelstrom in der Haupt-Kühlmittelpumpe unterbrochen wird, und das Kühlmittel zur Erlangung einer gewünschten erhöhten Motortemperatur durch die Sekundär-Kühlmittelpumpe zirkuliert wird.According to one embodiment of the method according to the invention, when the current operating state of the internal combustion engine is an eco-state, the operation of the main coolant pump is selectively interrupted by means of an overrunning clutch provided on the belt drive of the main coolant pump or a control slide arranged in the main coolant pump is activated in such a way is that the coolant flow in the main coolant pump is interrupted, and the coolant is circulated through the secondary coolant pump to obtain a desired increased engine temperature.

Gemäß einer Ausführungsform des erfindungsgemäßen Verfahrens wird, wenn der aktuelle Betriebszustand der Verbrennungskraftmaschine der Hochdrehzahlzustand ist, der Kühlmittelstrom der Haupt-Kühlmittelpumpe, zumindest teilweise, im Bypassbetrieb über die Sekundär-Kühlmittelpumpe auf die Zulaufseite der Haupt-Kühlmittelpumpe geleitet wird.According to one embodiment of the method according to the invention, when the current operating state of the internal combustion engine is the high-speed state is, the coolant flow of the main coolant pump, at least partially, is passed in the bypass mode via the secondary coolant pump to the inlet side of the main coolant pump.

Gemäß einer Ausführungsform des erfindungsgemäßen Verfahrens werden, wenn der aktuelle Betriebszustand der Verbrennungskraftmaschine der Restwärmespeicherzustand bei stillstehender Verbrennungskraftmaschine ist, sowohl der Regelschieber der Haupt-Kühlmittelpumpe als auch der Regelschieber der Sekundär-Kühlmittelpumpe geschlossen, um eine Zirkulation des Kühlmittels im Kühlkreislauf zu verhindern.According to one embodiment of the method according to the invention, when the current operating state of the internal combustion engine is the residual heat storage state with the internal combustion engine stationary, both the control slide of the main coolant pump and the control slide of the secondary coolant pump are closed in order to prevent circulation of the coolant in the cooling circuit.

KURZE BESCHREIBUNG DER FIGURENBRIEF DESCRIPTION OF THE FIGURES

Die vorstehend beschriebenen Merkmale und Funktionen der vorliegenden Erfindung sowie weitere Aspekte und Merkmale werden nachfolgend anhand einer detaillierten Beschreibung von bevorzugten Ausführungsformen unter Bezugnahme auf die beigefügten Figuren weiter beschrieben. Hierbei zeigt:

Fig. 1A
eine perspektivische Frontansicht eines erfindungsgemäßen regelbaren Kühlsystems;
Fig. 1B
eine perspektivische Rückansicht eines erfindungsgemäßen regelbaren Kühlsystems;
Fig. 2A
eine Teilschnittansicht einer elektrisch betriebenen Kühlmittelpumpe gemäß einer Ausführungsform der Erfindung in einer Offen-Stellung;
Fig. 2B
eine Detailansicht des Ausschnitts A der Fig. 2A;
Fig. 3A
eine Teilschnittansicht einer elektrisch betriebenen Kühlmittelpumpe gemäß einer Ausführungsform der Erfindung in einer Geschlossen-Stellung;
Fig. 3B
eine Detailansicht des Ausschnitts A der Fig. 3A;
Fig. 3C
eine Detailansicht des Ausschnitts B der Fig. 3A;
Fig. 4
eine perspektivische Darstellung eines erfindungsgemäßen Flügelrades mit einem daran angeordneten Regelschieber;
Fig. 5
eine Teilschnittdarstellung der Ansicht aus Fig. 4, in welcher der Regelschieber im Schnitt dargestellt ist; und
Fig. 6
eine Schnittdarstellung des Flügelrades mit daran angeordnetem Schieber aus Fig. 4.
The above-described features and functions of the present invention, as well as other aspects and features, will be further described below with reference to a detailed description of preferred embodiments with reference to the accompanying drawings. Hereby shows:
Fig. 1A
a perspective front view of a controllable cooling system according to the invention;
Fig. 1B
a perspective rear view of a controllable cooling system according to the invention;
Fig. 2A
a partial sectional view of an electrically operated coolant pump according to an embodiment of the invention in an open position;
Fig. 2B
a detailed view of the section A of Fig. 2A ;
Fig. 3A
a partial sectional view of an electrically operated coolant pump according to an embodiment of the invention in a closed position;
Fig. 3B
a detailed view of the section A of Fig. 3A ;
Fig. 3C
a detailed view of the section B of Fig. 3A ;
Fig. 4
a perspective view of an impeller according to the invention with a control slide arranged thereon;
Fig. 5
a partial sectional view of the view Fig. 4 in which the control slide is shown in section; and
Fig. 6
a sectional view of the impeller with arranged thereon slide Fig. 4 ,

BESCHREIBUNG BEVORZUGTER AUSFÜHRUNGSFORMENDESCRIPTION OF PREFERRED EMBODIMENTS

Fig. 1A zeigt eine perspektivische Darstellung eines regelbaren Kühlsystems 1 gemäß einer Ausführungsform der vorliegenden Erfindung. Fig. 1A shows a perspective view of a controllable cooling system 1 according to an embodiment of the present invention.

Das Kühlsystem 1 gemäß dieser Ausführungsform besteht dabei aus einem Kühlmittelkreislauf zum Zuführen und Abführen von Kühlmittel von und zu einer (nicht dargestellten) Verbrennungskraftmaschine eines Fahrzeuges, wobei das Kühlmittel über einen in der Kühlmittelleitung angeordneten Kühler (nicht dargestellt) mit der Umgebung des Fahrzeuges in Wärmeaustausch tritt.The cooling system 1 according to this embodiment consists of a coolant circuit for supplying and discharging coolant from and to an internal combustion engine (not shown) of a vehicle, wherein the coolant via a arranged in the coolant line radiator (not shown) with the environment of the vehicle in heat exchange occurs.

Wie in Fig. 1 dargestellt, führt eine Kühlmittelleitung 13 vom Fahrzeugkühler zu einer an einer Haupt-Kühlmittelpumpe 3 ausgebildeten Zuführung 17. Diese Zuführung 17 ist dabei in der gezeigten Ausführungsform flanschartig ausgebildet, kann jedoch auch in Form einer Leitung, eines Stutzens, einer Öffnung, eines Schraub- oder Bajonettanschlusses oder dergleichen ausgebildet sein.As in Fig. 1 shown, leads a coolant line 13 from the vehicle radiator to a formed on a main coolant pump 3 feed 17. This feed 17 is formed in the embodiment shown in a flange, but can also be in the form of a line, a nozzle, an opening, a screw or Bayonet connection or the like may be formed.

Die Haupt-Kühlmittelpumpe 3 ist in der vorliegenden Ausführungsform als Radialpumpe ausgebildet und umfasst ein Pumpengehäuse mit einer darin ausgebildeten (nicht dargestellten) Pumpenkammer, in der ein Flügelrad angeordnet ist. Dieses Flügelrad ist als Radialpumpen-Flügelrad ausgebildet und auf einer Pumpenwelle im Pumpengehäuse der Haupt-Kühlmittelpumpe 3 angeordnet.The main coolant pump 3 is formed in the present embodiment as a radial pump and comprises a pump housing with a pump chamber (not shown) formed therein, in which an impeller is arranged. This impeller is designed as a radial pump impeller and arranged on a pump shaft in the pump housing of the main coolant pump 3.

Als Antrieb für die Haupt-Kühlmittelpumpe 3 kommt in der diskutierten Ausführungsform ein Riemenantrieb zum Einsatz.As drive for the main coolant pump 3, a belt drive is used in the embodiment discussed.

Wie in der in Fig. 1B gezeigten Rückansicht des Kühlsystems dargestellt, ist an einem der Zuführung 17 abgewandten Abschnitt der Haupt-Kühlmittelpumpe 3 eine Riemenscheibe 57, die über einen (nicht dargestellten) Keil- oder Zahnriemen mit einer Riemenscheibe der Verbrennungskraftmaschine verbunden ist. Beim Betrieb der Verbrennungskraftmaschine wird durch den Riemen eine Rotationsbewegung auf die Riemenscheibe 57 der Haupt-Kühlmittelpumpe 3 übertragen, wodurch diese angetrieben wird.As in the Fig. 1B shown rear view of the cooling system, is on a side facing away from the feed 17 of the main coolant pump 3, a pulley 57 which is connected via a (not shown) wedge or toothed belt with a pulley of the internal combustion engine. During operation of the internal combustion engine, a rotation movement is transmitted to the pulley 57 of the main coolant pump 3 by the belt, whereby it is driven.

Wie vorstehend angeführt, ist die in dieser Ausführungsform dargestellte Haupt-Kühlmittelpumpe 3 eine axial angeströmte Kühlmittelpumpe, die mittels des in der Pumpenkammer angeordneten Flügelrades das zu fördernde Kühlmittel radial nach außen zu einer Abführung 15 weiterleitet. Diese Abführung 15 ist dabei, analog zur Zuführung 17, in der gezeigten Ausführungsform flanschartig ausgebildet. Sie kann jedoch auch in Form einer Leitung, eines Stutzens, einer Öffnung, eines Schraub- oder Bajonettanschlusses oder dergleichen ausgebildet sein.As stated above, the main coolant pump 3 shown in this embodiment is an axially impinged coolant pump which, by means of the impeller arranged in the pump chamber, forwards the coolant to be conveyed radially outwards to a discharge 15. This discharge 15 is analogous to the feed 17, formed in the embodiment shown in a flange. However, it may also be in the form of a line, a nozzle, an opening, a screw or bayonet connection or the like.

Die in dieser Ausführungsform diskutierte Haupt-Kühlmittelpumpe 3 weist in ihrer Pumpenkammer ferner einen (ebenfalls nicht dargestellten) konzentrisch auf der Antriebswelle, das Flügelrad umgreifend angeordneten Regelschieber auf, der in seiner Geschlossen-Stellung das Flügelrad in dessen Randbereichen umschließt, um einen durch die Kühlmittelpumpe 3 geförderten Kühlmittelstrom zu unterbrechen.The discussed in this embodiment, the main coolant pump 3 also has in its pump chamber a (also not shown) concentrically on the drive shaft, the impeller encompassing arranged control slide, which surrounds the impeller in its closed position in its closed position to one through the coolant pump 3 interrupted flow of coolant to interrupt.

Derartige Pumpen werden von der gleichen Anmelderin erfolgreich auf dem Markt vertrieben und sind beispielsweise in der Druckschrift DE 10 2005 004 315 B4 , DE 10 2005 062 200 B3 und WO 2009/14382 A2 diskutiert.Such pumps are marketed successfully by the same Applicant in the market and are for example in the document DE 10 2005 004 315 B4 . DE 10 2005 062 200 B3 and WO 2009/14382 A2 discussed.

Wie in Fig. 1A ferner dargestellt ist, umfasst die Haupt-Kühlmittelpumpe 3 dieser Ausführungsform die Abführung 15, über welche das Kühlmittel aus der Haupt-Kühlmittelpumpe 3 zur Verbrennungskraftmaschine gefördert wird.As in Fig. 1A is further shown, the main coolant pump 3 of this embodiment, the discharge 15, via which the coolant is conveyed from the main coolant pump 3 to the internal combustion engine.

Zudem kann auch ein Heizkreislauf im Kühlsystem vorgesehen sein, vermittels dem aus der Haupt-Kühlmittelpumpe 3 ein Kühlmedium über eine Heizleitung 19 in den Heizkreislauf einbringbar ist. Beispielsweise kann ein Regler oder Ventil in der Haupt-Kühlmittelpumpe 3 angeordnet sein, der bzw. das den von der Pumpe 3 geförderten Kühlmittelstrom in den Heizkreislauf leitet.In addition, a heating circuit may be provided in the cooling system, by means of which from the main coolant pump 3, a cooling medium via a heating line 19 in the heating circuit can be introduced. For example, a regulator or valve may be arranged in the main coolant pump 3 which conducts the coolant flow conveyed by the pump 3 into the heating circuit.

Über die zur Haupt-Kühlmittelpumpe 3 führende Kühlmittelleitung 13 wird das aus dem Fahrzeugkühler kommende Kühlmittel der Haupt-Kühlmittelpumpe 3 zugeführt.About the coolant line leading to the main coolant pump 3 13, the coming of the vehicle radiator coolant of the main coolant pump 3 is supplied.

Parallel zur Haupt-Kühlmittelpumpe 3 ist eine Sekundär-Kühlmittelpumpe 5 angeordnet. Die Zuführung 9 zur Sekundär-Kühlmittelpumpe 5 zweigt dabei an einer Stelle vor der Zuführung 17 der Hauptpumpe 3 von der Kühlmittelleitung 13 ab.Parallel to the main coolant pump 3, a secondary coolant pump 5 is arranged. The feed 9 to the secondary coolant pump 5 branches off at a point in front of the feed 17 of the main pump 3 from the coolant line 13.

Die Sekundär-Kühlmittelpumpe 5 ist in dieser Ausführungsform ebenfalls als axial angeströmte radial fördernde Pumpe ausgebildet, und wird von einem Elektromotor 7 betrieben, der an einem der Kühlmittelzuführung 9 abgewandten Abschnitt der Sekundär-Kühlmittelpumpe 5 angeordnet ist.The secondary coolant pump 5 is also formed in this embodiment as an axially impinged radially conveying pump, and is operated by an electric motor 7, which is arranged on a coolant supply 9 facing away portion of the secondary coolant pump 5.

Über die konisch zulaufende Zuführung 9 wird das von der Zuleitung 13 gelieferte Kühlmittel durch die Sogwirkung eines in der Sekundär-Kühlmittelpumpe 5 angeordneten Flügelrades 25 in die Sekundär-Kühlmittelpumpe 5 gesaugt und von dort über das in einer Pumpenkammer 53 angeordnete Flügelrad 25 über die Abführung 11 in die Abführung 15 der Haupt-Kühlmittelpumpe 3 ausgetragen, ohne hierbei durch die Hauptpumpe 3 zu strömen. Die Sekundär-Kühlmittelpumpe 5 bildet somit eine Art Bypass-Weg, durch welchen das zu fördernde Kühlmittel als Bypasskühlmittelstrom unter Umgehung der Haupt-Kühlmittelpumpe 5 im Kühlkreislauf vom Kühler kommend zur Verbrennungskraftmaschine zirkuliert werden kannVia the tapered feed 9, the coolant supplied from the supply line 13 is sucked by the suction effect of a arranged in the secondary coolant pump 5 impeller 25 in the secondary coolant pump 5 and from there via the arranged in a pump chamber 53 impeller 25 via the discharge 11th discharged into the discharge 15 of the main coolant pump 3, without being affected by the Main pump 3 to flow. The secondary coolant pump 5 thus forms a type of bypass path through which the coolant to be delivered can be circulated as a bypass coolant flow, bypassing the main coolant pump 5 in the cooling circuit coming from the radiator to the internal combustion engine

Die Zuführung 9 sowie die Abführung 11 der Sekundär-Kühlmittelpumpe der gezeigten Ausführungsform sind dabei flanschartig ausgebildet. Sie können jedoch auch in Form einer Leitung, eines Stutzens, einer Öffnung, eines Schraub- oder Bajonettanschlusses oder dergleichen ausgebildet sein.The supply 9 and the discharge 11 of the secondary coolant pump of the embodiment shown are formed in a flange. However, they may also be in the form of a line, a nozzle, an opening, a screw or bayonet connection or the like.

Eine Teilschnittansicht der in den Figuren. 1A und 1B gezeigten, elektrisch betriebenen Kühlmittelpumpe 5 ist in Fig. 2A dargestellt.A partial sectional view of the in the Characters. 1A and 1B shown, electrically operated coolant pump 5 is in Fig. 2A shown.

Die in Fig. 2A gezeigte Kühlmittelpumpe 5 ist dabei, wie vorstehend beschrieben, als axial angeströmte Radialpumpe ausgebildet, und umfasst eine Pumpenkammer 53, die in einem Pumpengehäuse 51 ausgebildet ist.In the Fig. 2A shown coolant pump 5 is, as described above, formed as an axially impinged radial pump, and includes a pump chamber 53 which is formed in a pump housing 51.

Bei der in Fig. 2A gezeigten Ausführungsform ist, an einem der Zuführung 9 abgewandten Ende der Sekundär-Kühlmittelpumpe 5, ein Elektromotor 7 angeordnet. Der Elektromotor dieser Ausführungsform hat dabei eine Leistung zwischen 20W und 100W und ist als Trockenläufer konzipiert, wodurch hohe Motordrehzahlen von über 12.000 U/min bei geringer Leistungsaufnahme ermöglicht werden.At the in Fig. 2A In the embodiment shown, an electric motor 7 is arranged on an end of the secondary coolant pump 5 facing away from the feed 9. The electric motor of this embodiment has a power between 20W and 100W and is designed as a dry runner, whereby high engine speeds of over 12,000 U / min are possible with low power consumption.

Von diesem Motor 7 ausgehend ragt eine Antriebswelle 21 in die Pumpenkammer 51 der Sekundär-Kühlmittelpumpe 5.Starting from this motor 7, a drive shaft 21 protrudes into the pump chamber 51 of the secondary coolant pump 5.

Die Antriebswelle 21 ist in der hier gezeigten Ausführungsform über eine Wellendichtung 29 gegen das Kühlmittel abgedichtet, um ein Eindringen von Kühlmittel in den Elektromotor 7 zu vermeiden.The drive shaft 21 is sealed in the embodiment shown here via a shaft seal 29 against the coolant to prevent ingress of coolant into the electric motor 7.

Konzentrisch auf der Antriebswelle 21 sind das Flügelrad 25 sowie ein Regelschieber 31 angeordnet. Das Flügelrad 25 wird dabei von Halteelementen 47 formschlüssig auf der Antriebswelle gehalten.Concentric on the drive shaft 21, the impeller 25 and a control slide 31 are arranged. The impeller 25 is held by retaining elements 47 positively on the drive shaft.

Die Gestalt des Regelschiebers 31 folgt dabei im Wesentlichen der Kontur der Stirnfläche des Flügelrades 25, wobei die Flügelschaufeln 39 die Regelschieberoberseite durchdringen.The shape of the control slide 31 essentially follows the contour of the end face of the impeller 25, wherein the wing blades 39 penetrate the control slide top.

An einem Stimabschnitt des Regelschiebers 31 ist ein hülsenförmiger bzw. kammerartig geformter Abschnitt 33 ausgebildet, an dessen Innenwandumfang ein Gewindeabschnitt vorgesehen ist.At a front portion of the control slide 31, a sleeve-shaped or chamber-like shaped portion 33 is formed on the inner wall circumference, a threaded portion is provided.

Ein hierzu komplementärer Gewindeabschnitt ist an einem Stirnabschnitt 23 der Antriebswelle 21 ausgebildet.A complementary threaded portion is formed on a front portion 23 of the drive shaft 21.

Die Fig. 2A zeigt die Sekundär-Kühlmittelpumpe 5 in einem Zustand, bei dem der Regelschieber 31 geöffnet ist.The Fig. 2A shows the secondary coolant pump 5 in a state in which the control slide 31 is open.

In dem in Fig. 2A gezeigten Zustand kann somit das durch das Flügelrad 25 geförderte Kühlmittel aus der Sekundär-Kühlmittelpumpe 5 radial nach außen ausgetragen werden.In the in Fig. 2A shown state, thus, the promoted by the impeller 25 coolant from the secondary coolant pump 5 are discharged radially outward.

Wie in der Detailansicht des Bereiches A aus Fig. 2A gezeigt, ist an einem radial äußeren Ende des Flügelrades 25, innerhalb eines Schließelementes 35 des Regelschiebers 31, ein Dichtungselement 45 angeordnet. Ein weiteres Dichtelement 43 ist an der radial außen gelegenen Stirnseite des Regelschiebers 31 angeordnet.As in the detail view of area A off Fig. 2A is shown, at a radially outer end of the impeller 25, within a closing element 35 of the control slide 31, a sealing element 45 is arranged. Another sealing element 43 is arranged on the radially outer end face of the control slide 31.

Ferner ist in der dem Elektromotor 7 zugewandten Pumpengehäusewand eine das Schließelement 35 aufnehmende, kreisförmig der Umfangskontur des Regelschiebers 31 folgende, Ausnehmung 37 ausgebildet. In der Offen-Stellung des Regelschiebers 31 ist das daran ausgebildete Schließelement 35 in dieser Aufnehmung 37 aufgenommen und wird darin drehbar gehalten, so dass das Flügelrad 25 mit dem daran ausgebildeten Regelschieber 31 durch die Antriebskraft der Antriebswelle 21 rotieren können.Further, in the electric motor 7 facing the pump housing wall, a closing member 35 receiving, circular the circumferential contour of the control slide 31 following, recess 37 is formed. In the open position of the control slide 31, the closing element 35 formed thereon is received in this recess 37 and is rotatably held therein, so that the impeller 25 can rotate with the control slide formed thereon 31 by the driving force of the drive shaft 21.

Die Fig. 3A zeigt die elektrisch betriebene, regelbare Sekundär-Kühlmittelpumpe 5 aus Fig. 2A und 2B bei geschlossenen Zustand des Regelschiebers 31.The Fig. 3A shows the electrically operated, controllable secondary coolant pump 5 from FIGS. 2A and 2B in the closed state of the control slide 31.

Der Regelschieber 31 der Kühlmittelpumpe 5 wird dabei, wie schematisch in den Figuren 2A und 3A angedeutet, durch langsame Vorwärts- bzw. Rückwärtsrotation der Antriebswelle 21 des Elektromotors 7 in die jeweilige Arbeitsstellung verfahren.The control slide 31 of the coolant pump 5 is, as shown schematically in the FIGS. 2A and 3A indicated, moved by slow forward or reverse rotation of the drive shaft 21 of the electric motor 7 in the respective working position.

Insbesondere wird hierbei durch langsames Drehen der Antriebswelle 21 in Vorwärtsrichtung, das heißt in Pumpenrichtung, der Kühlmittelpumpe 5 der Regelschieber 31 aus seiner Geschlossen-Stellung in die Offen-Stellung verbracht, in welcher er der Kontur des Flügelrades 25 folgend an dessen Oberfläche anliegt, sodass die Flügelradschaufeln 39 den Regelschieber 31 durchdringen können und bei Drehung des Flügelrades in Arbeitsgeschwindigkeit die Pumpwirkung in der Kühlmittelpumpe 5 erzeugen können.In particular, by slow rotation of the drive shaft 21 in the forward direction, that is, in the pump direction, the control valve 31 is moved from its closed position to the open position, in which it rests against the contour of the impeller 25 at its surface, so that the impeller blades 39 can penetrate the control slide 31 and can generate the pumping action in the coolant pump 5 when the impeller rotates at operating speed.

Insbesondere wird, sobald der Regelschieber 31 mit dem Flügelrad 25 in Kontakt gelangt ist, ein Kraftschluss zwischen dem Regelschieber 31 und dem Flügelrad 25 hergestellt, sodass das Flügelrad 25 durch die von der Antriebswelle 21 auf den Regelschieber 31 übertragene Antriebsleistung in Rotation versetzt werden kann. In der in Fig. 2A gezeigten Offen-Stellung ist dabei ein Austrag des durch das Flügelrad 25 geförderten Kühlmittels aus der Kühlmittelpumpe 5 möglich.In particular, as soon as the control slide 31 has come into contact with the impeller 25, a frictional connection between the control slide 31 and the impeller 25 is made, so that the impeller 25 can be rotated by the transmitted from the drive shaft 21 to the control slide 31 drive power in rotation. In the in Fig. 2A shown open position is a discharge of the conveyed by the impeller 25 coolant from the coolant pump 5 possible.

Wenn der Regelschieber 31 durch eine Umkehrrotation der Antriebswelle 21 in die in Fig. 3A gezeigte Geschlossen-Stellung gefahren wird, gelangt der Regelschieber 31 dagegen in seiner vollständig-Geschlossen-Stellung mit einem der Zuführung 9 zugewandten Wandabschnitt des Pumpengehäuses 51 in Kontakt.When the control slide 31 by a reverse rotation of the drive shaft 21 in the in Fig. 3A In contrast, the control slide 31, in its fully closed position, comes into contact with a wall section of the pump housing 51 facing the feed 9.

Das am Regelschieber 31 ausgebildete Dichtungselement 43 wird dabei gegen die Pumpengehäusewand gedrückt und dichtet die Pumpenkammer 53 gegen über der Abführung 11 der Pumpe 5 ab. Das am hinteren Abschnitt des Flügelrades 25 ausgebildete Dichtungselement 45 stützt das als Außenumfangsschenkel des Regelschiebers 31 ausgebildete Schließelement 35 dabei von unten ab, um somit eine ausreichend zuverlässige Dichtwirkung zu erzeugen.The trained on the control slide 31 sealing element 43 is pressed against the pump housing wall and seals the pump chamber 53 against the Outlet 11 of the pump 5 from. The sealing element 45 formed on the rear section of the impeller 25 supports the closing element 35 formed as the outer circumferential leg of the control slide 31 from below, thus producing a sufficiently reliable sealing effect.

Wie schematisch in den Figuren 2B und 3B angedeutet, ist das am Regelschieber 31 ausgebildete Dichtungselement 43 größer ausgebildet als das am Flügelrad 25 ausgebildete Dichtungselement 45, um eine ausreichend große Dichtwirkung gegen die Wandfläche der Pumpenkammer zu erzielen. Insbesondere lastet durch die unterschiedlichen Dichtungsdurchmesser der von der Druckseite der HauptKühlmittelpumpe 3 zurückwirkende Druck auf der Ringfläche, die sich aus den Durchmesserdifferenzen der Dichtungselemente 43, 45 ergibt. Die Dichtungsfunktion der Dichtungselemente 43, 45 wird dabei hydraulisch verstärkt, unabhängig davon, ob der Elektromotor 7 der Sekundär-Kühlmittelpumpe 5 läuft oder nicht.As shown schematically in the FIGS. 2B and 3B indicated, the sealing element 43 formed on the control slide 31 is formed larger than the sealing element 45 formed on the impeller 25 in order to achieve a sufficiently large sealing effect against the wall surface of the pump chamber. In particular, due to the different sealing diameters, the pressure acting back on the annular surface from the pressure side of the main coolant pump 3, which results from the diameter differences of the sealing elements 43, 45. The sealing function of the sealing elements 43, 45 is thereby reinforced hydraulically, regardless of whether the electric motor 7 of the secondary coolant pump 5 is running or not.

Um zu vermeiden, dass sich das Flügelrad 25 unbeabsichtigt dreht, ist an einem der Zuführung 9 abgewandten Ende des Flügelrades 25 ein Bremselement 27 angeordnet, das gegen eine an den Elektromotor 7 angrenzende Innenwandfläche 49 im Pumpengehäuse 51 drückt.In order to avoid that the impeller 25 rotates unintentionally, a brake element 27 is arranged on one of the feed 9 facing away from the end of the impeller 25, which presses against an adjacent to the electric motor 7 inner wall surface 49 in the pump housing 51.

Dieses Bremselement 27 ist dabei als Bremsscheibe oder vorgespannte Tellerfeder ausgebildet und hat in der gezeigten Ausführungsform an seinen radial äußeren Enden keilförmig zulaufende Verdickungen 41, die in Reibeingriff mit der Innenwandfläche 49 des Pumpengehäuses 51 gelangen.This brake element 27 is designed as a brake disk or prestressed plate spring and has in the embodiment shown at its radially outer ends wedge-shaped tapered thickenings 41, which come into frictional engagement with the inner wall surface 49 of the pump housing 51.

Solange die Drehung der Antriebswelle 21 des Elektromotors 7 gering ist, um dabei den Regelschieber 31 in seine Offen-Stellung zu verfahren, wird das Flügelrad 25 durch das Bremselement 27 in Reibeingriff mit dem Pumpengehäuse 51 gehalten, sodass eine Drehung des Flügelrades 25 weitestgehend verhindert wird.As long as the rotation of the drive shaft 21 of the electric motor 7 is small in order to move the control slide 31 in its open position, the impeller 25 is held by the brake member 27 in frictional engagement with the pump housing 51, so that rotation of the impeller 25 is largely prevented ,

Bei Kraftschluss zwischen Regelschieber 31 und Flügelrad 25 und zunehmender Rotation der Antriebswelle 21 löst sich das Bremselement 27 aufgrund der zunehmenden Fliehkraft durch die Rotation der Antriebswelle 21 von der Wand 49 des Pumpengehäuses 51 und gibt die Drehung des Flügelrades 25, und damit die Pumpfunktion der Kühlmittelpumpe 5 frei.In traction between the control slide 31 and impeller 25 and increasing rotation of the drive shaft 21, the brake element 27 dissolves due to the increasing centrifugal force by the rotation of the drive shaft 21 of the wall 49 of the pump housing 51 and are the rotation of the impeller 25, and thus the pumping function of the coolant pump 5 free.

Fig. 4 zeigt eine perspektivische Ansicht des in den Figuren 2 und 3 gezeigten Flügelrades 25 der elektrisch regelbaren Kühlmittelpumpe 5 mit einem daran angeordneten Regelschieber 31. Fig. 4 shows a perspective view of the in the Figures 2 and 3 shown impeller 25 of the electrically controllable coolant pump 5 with a control slide 31 arranged thereon.

Wie bei dieser Ansicht von vorne gezeigt, umfasst der Regelschieber 31 das (nicht weiter gezeigte) Flügelrad 25 vollständig, wobei die Flügelradschaufeln 39 den Regelschieber 31 durchdringen.As shown in this view from the front, the control slide 31, the (not shown) impeller 25 completely, wherein the impeller blades 39 penetrate the control slide 31.

Der Regelschieber 31 weist in seiner Mitte einen die Antriebswelle 21 des Elektromotors 7 aufnehmenden, kammerartigen Abschnitt 33 auf. Dieser kammerartige Abschnitt 33 hat dabei, wie schematisch in Fig. 5 angedeutet, an der Innenwand einen Gewindeabschnitt, der komplementär zum in Fig. 5 nicht gezeigten Gewindeabschnitt 23 der Antriebswelle 21 ist.The control slide 31 has in its center a drive shaft 21 of the electric motor 7 receiving, chamber-like portion 33. This chamber-like portion 33 has, as shown schematically in FIG Fig. 5 indicated on the inner wall a threaded portion which is complementary to in Fig. 5 not shown threaded portion 23 of the drive shaft 21 is.

Fig. 5 zeigt eine Teilschnittdarstellung eines axial angeströmten, radial fördernden Flügelrades 25, wie es in einer als Radialpumpe ausgebildeten Pumpe 3, 5 der hier diskutierten Ausführungsform zur Anwendung kommt. Fig. 5 shows a partial sectional view of an axially impinged, radially conveying impeller 25, as it comes in a designed as a radial pump pump 3, 5 of the embodiment discussed here used.

Denkbar ist dabei jedoch auch, dass, wenn die Kühlmittelpumpen 3, 5 als Axialpumpen ausgebildet sind, das Flügelrad radial angeströmt wird und das Kühlmittel in axialer Richtung weiter fördert.It is also conceivable, however, that when the coolant pumps 3, 5 are designed as axial pumps, the impeller is radially impinged and further promotes the coolant in the axial direction.

In der Mitte des Flügelrades 25 ist eine nabenartige Aufnahme 55 zur Aufnahme der (nicht dargestellten) Antriebswelle 21 ausgebildet.In the center of the impeller 25 is a hub-like receptacle 55 for receiving the (not shown) drive shaft 21 is formed.

Fig. 6 zeigt das Flügelrad 25 aus Fig. 5 mit dem daran angeordneten Regelschieber 31 in vollständiger Schnittdarstellung. Wie hierbei ersichtlich ist, sind das Flügelrad 25 sowie der Regelschieber 31 konzentrisch zueinander angeordnet und verlaufen entlang der vom Elektromotor 7 in die Pumpkammer 51 erreichenden Antriebswelle 21, die zur Vereinfachung der Darstellung hier nicht gezeigt werden. Fig. 6 shows the impeller 25 from Fig. 5 with the control slide 31 arranged thereon in a complete sectional view. As can be seen here, the impeller 25 and the control slide 31 are arranged concentrically to each other and run along the drive shaft 21 reaching from the electric motor 7 in the pumping chamber 51, which are not shown here for simplicity of illustration.

Durch Vorwärts- beziehungsweise Rückwärtsdrehen der Antriebswelle 21 des Elektromotors 7 kann der Regelschieber 31 dabei in die gewünschte Offen- oder Geschlossenstellung verfahren werden.By forward or reverse rotation of the drive shaft 21 of the electric motor 7, the control slide 31 can thereby be moved to the desired open or closed position.

Vermittels des erfindungsgemäßen Kühlsystems, welches die mechanisch betriebene, regelbare Kühlmittelpumpe 3 und die elektrisch betriebene, regelbare Kühlmittelpumpe 5 verwendet, lassen sich dabei in vorteilhafter Weise unter Berücksichtigung von vorbestimmten Steuerparametern wie einer gewünschten Kühlmitteltemperatur, und/oder einer gewünschten Motortemperatur, und/oder eine gewünschter Kühlmittelflussraten und/oder dergleichen verschiedene Betriebszustände einstellen.By means of the cooling system according to the invention, which uses the mechanically operated, controllable coolant pump 3 and the electrically operated, controllable coolant pump 5, can be advantageously in consideration of predetermined control parameters such as a desired coolant temperature, and / or a desired engine temperature, and / or a desired coolant flow rates and / or the like set different operating conditions.

Zur Steuerung des Kühlsystem 1 ist gemäß der hier diskutierten Ausführungsform daher zusätzlich eine Steuervorrichtung vorgesehen, welche die mechanisch betriebene Haupt-Kühlmittelpumpe 3 sowie die elektrisch betriebene Sekundär-Kühlmittelpumpe 5 ansteuert, um die jeweiligen Betriebszustände zu erreichen.To control the cooling system 1, a control device is therefore additionally provided according to the embodiment discussed here, which controls the mechanically operated main coolant pump 3 and the electrically operated secondary coolant pump 5 in order to achieve the respective operating states.

Beispielhafte Betriebszustände sind dabei ein Start-Stop-Zustand, ein Aufwärm-Zustand, ein Niedriglast-Zustand, ein Normallast-Zustand, ein Eco-Zustand, ein Hochdrehzahl-Zustand sowie ein Restwärme-Speicherzustand.Exemplary operating states are a start-stop state, a warm-up state, a low-load state, a normal-load state, an eco state, a high-speed state, and a residual heat storage state.

Der Start-Stop-Zustand bezeichnet dabei einen Antriebszustand, bei dem die Verbrennungskraftmaschine zeitweilig gestoppt wird, beispielsweise beim Halten an einer roten Ampel oder dergleichen, um auf diese Weise Kraftstoff zu sparen.The start-stop state denotes a drive state in which the internal combustion engine is temporarily stopped, for example, when stopping at a red light or the like, to save fuel in this way.

Bei Verwendung des hier diskutierten Kühlmittelsystems 1 in einem Fahrzeug mit Start-Stop-Regelung kann, im Falle des Anhaltens der Verbrennungskraftmaschine beispielsweise an einer roten Ampel, die elektrische Kühlmittelpumpe 5 das Kühlmittel vollständig alleine zirkulieren, da die mechanisch betriebene Kühlmittelpumpe 3 aufgrund der stehenden Verbrennungskraftmaschine nicht länger betrieben wird.When using the coolant system 1 discussed here in a vehicle with start-stop control, in the case of stopping the internal combustion engine, for example at a red traffic light, the electric coolant pump 5, the coolant completely circulate alone, since the mechanically operated coolant pump 3 is no longer operated due to the stationary internal combustion engine.

Hierzu wird, gemäß der hier diskutierten Ausführungsform, wenn der aktuelle Betriebszustand der Verbrennungskraftmaschine der Start-Stop-Zustand ist, bei dem die Haupt-Kühlmittelpumpe 3 während einer Stop-Phase der Verbrennungskraftmaschine zeitweise antriebslos ist, die Sekundär-Kühlmittelpumpe 5 in einen EIN-Zustand geschalten wird, wodurch das Kühlmittel durch die Sekundär-Kühlmittelpumpe 5 zirkuliert wird.For this purpose, according to the embodiment discussed here, if the current operating state of the internal combustion engine is the start-stop state in which the main coolant pump 3 is temporarily without power during a stop phase of the internal combustion engine, the secondary coolant pump 5 is switched to an ON state. State is switched, whereby the coolant is circulated through the secondary coolant pump 5.

Der Aufwärmzustand bezeichnet ferner einen Antriebszustand, bei dem, insbesondere beim Kaltstart der Verbrennungskraftmaschine, in dem Kühlsystem 1 aufgrund einer unterbrochenen Zirkulation des Kühlmittels stehendes Wasser erzeugt wird, so dass die Temperatur der Verbrennungskraftmaschine schnell auf ihre optimale Betriebstemperatur gebracht werden kann.The warm-up state further designates a driving state in which, particularly at the cold start of the internal combustion engine, water standing in the cooling system 1 due to intermittent circulation of the coolant is generated, so that the temperature of the internal combustion engine can be quickly brought to its optimum operating temperature.

Hier wird, wenn der aktuelle Betriebszustand der Verbrennungskraftmaschine der Aufwärm-Zustand ist, die Sekundär-Kühlmittelpumpe 5 in einen AUS-Zustand geschalten und ein Kühlmittelstrom durch die Haupt-Kühlmittelpumpe 3 vermittels des in der Haupt-Kühlmittelpumpe angeordneter Regelschiebers unterbrochen, so dass eine Zirkulation des Kühlmittels unterbrochen ist.Here, when the current operating state of the internal combustion engine is the warm-up state, the secondary coolant pump 5 is switched to an OFF state, and a coolant flow through the main coolant pump 3 is interrupted by means of the control spool disposed in the main coolant pump, so that circulation of the coolant is interrupted.

Vermittels des Kühlsystems 1 der hier diskutierten Ausführungsform ist es dabei möglich, in der Aufwärmphase der Verbrennungskraftmaschine die Pumpen 3, 5 derart zu steuern, dass die Schieber beider Pumpen 3, 5 geschlossen sind, sodass kein Kühlmittel durch die beiden Pumpen 3, 5 zirkuliert werden kann. Die elektrisch betriebene Kühlmittelpumpe 5 kann dabei auch ausgeschaltet sein, wobei durch den geschlossenen Regelschieber 31 ein Rückströmen und Zirkulieren des Kühlmittels verhindert werden kann. Alternativ wird die Pumpe 5 derart angesteuert, dass der Regelschieber 31 eine Zirkulation des Kühlmittels verhindert.By means of the cooling system 1 of the embodiment discussed here, it is possible to control the pumps 3, 5 in the warm-up phase of the internal combustion engine such that the slides of both pumps 3, 5 are closed, so that no coolant is circulated through the two pumps 3, 5 can. The electrically operated coolant pump 5 can also be switched off, wherein a backflow and circulation of the coolant can be prevented by the closed control slide 31. Alternatively, the pump 5 is controlled such that the control slide 31 prevents circulation of the coolant.

Auf diese Weise ist es möglich, schnell die Betriebstemperatur der Verbrennungskraftmaschine zu erreichen.In this way it is possible to quickly reach the operating temperature of the internal combustion engine.

Der Niedriglast-Zustand bezeichnet ferner einen Antriebszustand, bei dem die Verbrennungskraftmaschine mit niedriger Drehzahl betrieben wird, beispielsweise im Leerlaufbetrieb.The low-load state further designates a drive state in which the internal combustion engine is operated at a low speed, for example, in idling operation.

Gemäß der hier diskutierten Ausführungsform wird, wenn der aktuelle Betriebszustand der Verbrennungskraftmaschine der Niedriglast-Zustand ist, ein Kühlmittelstrom durch die Haupt-Kühlmittelpumpe 3 vermittels des in der Haupt-Kühlmittelpumpe angeordneten Regelschiebers unterbrochen wird und die Sekundär-Kühlmittelpumpe 5 in einen EIN-Zustand geschalten wird, wodurch das Kühlmittel durch die Sekundär-Kühlmittelpumpe 5 zirkuliert wird.According to the embodiment discussed here, when the current operating state of the internal combustion engine is the low-load state, a coolant flow through the main coolant pump 3 is interrupted by means of the control spool disposed in the main coolant pump and the secondary coolant pump 5 is switched to an ON state is, whereby the coolant is circulated through the secondary coolant pump 5.

Auch ist es, bei nur sehr geringen Drehzahlen der Verbrennungskraftmaschine und dadurch unter Umständen nicht ausreichender Zirkulationsleistung der Haupt-Kühlmittelpumpe 3 möglich, die elektrische Sekundär-Kühlmittelpumpe 5 zuzuschalten, um ein sogenanntes elektrisches Boosten auszuführen, in anderen Worten die Zirkulation des Kühlmittels durch Förderleistung der elektrisch regelbaren Sekundär-Kühlmittelpumpe 5 zu unterstützten.Also, it is possible to switch on the secondary electric coolant pump 5 to carry out so-called electric boosting, in other words, the circulation of the coolant by the delivery rate of the internal combustion engine and thereby possibly insufficient circulation performance of the main coolant pump 3 electrically controlled secondary coolant pump 5 to assist.

Im Hochlastbetrieb der Verbrennungskraftmaschine, beispielsweise bei Fahrten auf Autobahnen etc. wird der Regelschieber 31 der elektrisch betriebenen Kühlmittelpumpe 3 in der Regel in seine Geschlossen-Stellung gebracht oder die Pumpe 3 abgeschaltet und die Zirkulation des Kühlmittels ausschließlich über die mechanisch betriebene Haupt-Kühlmittelpumpe 3 realisiert.In high-load operation of the internal combustion engine, for example when driving on highways, etc., the control slide 31 of the electrically operated coolant pump 3 is usually brought into its closed position or the pump 3 is switched off and realized the circulation of the coolant exclusively via the mechanically operated main coolant pump 3 ,

Sofern jedoch zusätzliche Kühlleistung erforderlich ist, kann die elektrische Kühlmittelpumpe 5 hinzugeschalten werden, um die Kühlmittelförderung durch die mechanische Kühlmittelpumpe 3 zu unterstützen.However, if additional cooling power is required, the electric coolant pump 5 can be switched on to support the coolant delivery through the mechanical coolant pump 3.

Der Normallast-Zustand bezeichnet einen Antriebszustand, bei dem die Verbrennungskraftmaschine, vorzugsweise im mittleren Drehzahlbereich, betrieben wird, um eine Antriebsleistung auf das Fahrzeug aufzubringen. Hierbei wird die Sekundär-Kühlmittelpumpe 5 in einen AUS-Zustand geschalten und deren Regelschieber 31 in der Regel in die Geschlossen-Stellung gebracht, wodurch das Kühlmittel im Kühlmittelkreislauf durch die Haupt-Kühlmittelpumpe 3 zirkuliert wird.The normal load state means a drive state in which the internal combustion engine, preferably in the middle speed range, is operated to apply a drive power to the vehicle. Here, the secondary coolant pump 5 is switched to an OFF state and its control slide 31 is usually brought into the closed position, whereby the coolant in the coolant circuit is circulated through the main coolant pump 3.

Der Eco-Zustand bezeichnet einen Antriebszustand, bei dem die Verbrennungskraftmaschine normal betrieben wird und vermittels eines Steuereingriffs in das Kühlsystem die Kühlmitteltemperatur in einem erhöhten Bereich gehalten wird, so dass eine effizientere Kraftstoffverbrennung und damit ein sparsamerer Fahrbetrieb möglich ist.The eco-state refers to a driving state in which the internal combustion engine is normally operated, and by means of a control intervention in the cooling system, the coolant temperature is maintained in an increased range, so that a more efficient fuel combustion and thus a more economical driving operation is possible.

Beim Betrieb der Verbrennungskraftmaschine im Eco-Modus (Eco-Zustand) wird der Betrieb der Haupt-Kühlmittelpumpe 3 vermittels einer an der Riemenscheibe 57 der Haupt-Kühlmittelpumpe 3 vorgesehenen Freilaufkupplung selektiv unterbrochen, und/oder der in der Haupt-Kühlmittelpumpe 3 angeordneter Regelschieber wird derart angesteuert, dass der Kühlmittelstrom in der Haupt-Kühlmittelpumpe 3 unterbrochen wird. In diesem Zustand wird das Kühlmittel zur Erlangung einer gewünschten erhöhten Motortemperatur durch die Sekundär-Kühlmittelpumpe 5 zirkuliert.In the operation of the internal combustion engine in the Eco mode (Eco state), the operation of the main coolant pump 3 is selectively interrupted by means of a provided on the pulley 57 of the main coolant pump 3 overrunning clutch, and / or arranged in the main coolant pump 3 control slide controlled in such a way that the coolant flow in the main coolant pump 3 is interrupted. In this state, the coolant is circulated through the secondary coolant pump 5 to obtain a desired increased engine temperature.

Der Hochdrehzahl-Zustand bezeichnet einen Antriebszustand, bei dem die Verbrennungskraftmaschine mit hoher Drehzahl mit erhöhtem Kühlbedarf betrieben wird, beispielsweise bei der Fahrt auf einer Autobahn oder dergleichen.The high-speed state refers to a driving state in which the internal combustion engine is operated at high speed with increased cooling demand, for example when driving on a highway or the like.

Gemäß einer Ausführungsform des erfindungsgemäßen Verfahrens wird, wenn der aktuelle Betriebszustand der Verbrennungskraftmaschine der Hochdrehzahlzustand ist, der Kühlmittelstrom der Haupt-Kühlmittelpumpe 3, zumindest teilweise, im Bypassbetrieb über die Sekundär-Kühlmittelpumpe 5 auf die zur Verbrennungskraftmaschine führende Zulaufseite der Haupt-Kühlmittelpumpe 5 geleitet wird.According to one embodiment of the method according to the invention, when the current operating state of the internal combustion engine is the high-speed state, the coolant flow of the main coolant pump 3 is, at least partially, bypassed via the secondary coolant pump 5 to the intake side of the main coolant pump 5 leading to the internal combustion engine ,

Der Restwärme-Speicherzustand bezeichnet schließlich einen Antriebszustand, bei dem die Verbrennungskraftmaschine ausgeschalten ist und die Temperatur des Kühlmittels so lange wie möglich hoch gehalten werden soll, um bei einem erneuten Start der Verbrennungskraftmaschine eine verkürzte Aufwärmphase zu erreichen, wodurch die Verbrennungskraftmaschine schneller in ihrem optimalen Temperaturbereich betrieben werden kann.The residual heat storage state finally designates a drive state in which the internal combustion engine is switched off and the temperature of the coolant is to be kept high as long as possible in order to achieve a shortened warm-up phase when the internal combustion engine is restarted, whereby the internal combustion engine is faster in its optimum temperature range can be operated.

Bei der hier diskutierten Ausführungsform des Kühlsystems 1 wird der Kühlmittelfluss aus dem Motor zurück zum Kühler durch Absperren der beiden Pumpen 3, 5 vermittels der darin angeordneten Schieber unterbunden, wodurch ein Wärmeaustausch des Kühlmittels mit der Umgebung des Fahrzeugs nur sehr zögerlich stattfinden kann. Die von der Verbrennungskraftmaschine erzeugte Wärme bleibt somit über einen längeren Zeitraum bei Stillstand des Kraftfahrzeuges erhalten und kann und späterem Neustart dazu verwendet werden, dass die Betriebstemperatur schneller erreicht werden kann.In the embodiment of the cooling system 1 discussed here, the coolant flow from the engine back to the radiator is shut off by shutting off the two pumps 3, 5 by means of the slides arranged therein, whereby a heat exchange of the coolant with the environment of the vehicle can take place only very hesitant. The heat generated by the internal combustion engine is thus maintained over a longer period of time when the motor vehicle is at a standstill and can be used, and later restarted, to speed up the operating temperature.

Obgleich die hier diskutierten Ausführungsformen eine elektrisch betriebene Sekundär-Kühlmittelpumpe 5 diskutieren, in welcher der Regelschieber 31 vermittels eines als Gewindespindel gestalteten Antriebs entlang der Antriebswelle 21 verschoben wird, ist es auch denkbar, dass der Regelschieber relativ zum Flügelrad statt über die Gewindespindel mit einem pneumatisch, magnetisch und/oder hydraulisch betriebenen Stellglied oder einem elektrischen Stellmotor entlang der Antriebswelle 21 verschoben wird.Although the embodiments discussed herein discuss an electrically operated secondary coolant pump 5 in which the control slide 31 is displaced along the drive shaft 21 by means of a drive configured as a threaded spindle, it is also conceivable that the control slide may be pneumatically actuated relative to the impeller rather than via the threaded spindle , magnetically and / or hydraulically operated actuator or an electric servomotor along the drive shaft 21 is moved.

Obgleich die hier diskutierten Ausführungsformen einen separat am Flügelrad 25 ausgebildeten Regelschieber 31 offenbaren, ist es auch denkbar, dass der Regelschieber 31 integral im Flügelrad 25 ausgebildet ist. Beispielsweise kann der integral im Flügelrad 25 ausgebildete Regelschieber 31 derart ausgebildet sein, dass auf den Außenflächen des Flügelrades 25 schenkelartige Wandflächen ausgebildet sind, die gleichwirkend wie das Schließelement 35 des Regelschiebers 31 sind.Although the embodiments discussed herein disclose a control slide 31 formed separately on the impeller 25, it is also conceivable that the control slide 31 is integrally formed in the impeller 25. For example, integrally formed in the impeller 25 control slide 31 may be formed such that on the outer surfaces of the impeller 25 leg-like wall surfaces are formed, which are the same effect as the closing element 35 of the control slide 31.

Zum Regeln des einer derart ausgestatteten Sekundär-Kühlmittelpumpe 5 geförderten Kühlmittelstromes kann ein so ausgebildetes Flügelrad 25 entlang der Antriebsachse 21 verschoben werden, so dass die zur Pumpengehäuserückseite ragenden, schenkelartigen Wandelemente die Abführung 11, in einer Geschlossen-Stellung des derart ausgebildeten Flügelrades 25, dicht verschließen. In einer Offen-Stellung des Flügelrades 25 mit dem integral ausgebildeten Regelschieber 31 sind die Wandelemente in der in der Gehäusewand des Pumpengehäuses 51 ausgebildeten Aufnahme 37 um die Antriebswelle 21 drehbar gelagert.For controlling the coolant flow conveyed to a secondary coolant pump 5 equipped in this way, an impeller 25 designed in this way can be displaced along the drive axis 21, so that the thigh-like wall elements protruding toward the pump housing rear side seal the discharge 11 in a closed position of the impeller 25 thus formed close. In an open position of the impeller 25 with the integrally formed control slide 31, the wall elements in the formed in the housing wall of the pump housing 51 receptacle 37 are rotatably mounted about the drive shaft 21.

Alternativ kann statt eines vor dem Flügelrad 25 angeordneten Regelschiebers 31 auch ein Rotationsschieber zur Anwendung kommen, der das Flügelrad 25 umgreifend in der Pumpenkammer 53 angeordnet ist und in eine Offen- und Geschlossen Stellung drehbar verschoben werden kann. Es ist ferner möglich, einen hülsenförmigen Regelschieber 31 hinter dem Flügelrad 25 anzuordnen, der dann, beispielsweise durch den vorstehend diskutierten Gewindespindel-Antrieb oder ein pneumatisch, magnetisch und/oder hydraulisch betriebenes Stellglied oder einen elektrischen Stellmotor über das Flügelrad 25 geschoben wird, und die Abführung 11 der Sekundärpumpe abdichtend verschließt.Alternatively, instead of a valve disposed in front of the impeller 25 control slide 31 and a rotary valve can be used, the impeller 25 is arranged encompassing in the pump chamber 53 and can be rotatably moved into an open and closed position. It is also possible to arrange a sleeve-shaped control slide 31 behind the impeller 25, which is then pushed over the impeller 25, for example by the above-discussed threaded spindle drive or a pneumatically, magnetically and / or hydraulically operated actuator or an electric servomotor, and the Outlet 11 of the secondary pump sealingly closes.

Das vorstehend diskutierte Flügelrad mit dem daran angeordneten Regelschieber kann auch als eine Art Rückschlagventil in einem Leitungssystem zur Anwendung kommen. Je nach Anströmrichtung und Anströmdruck kann der Schieber dabei auf der das Flügelrad und den Schieber haltenden Welle das anströmende Medium weiter fördern oder, bei entsprechend hohem Strömungsdruck entgegen der Förderrichtung, das Leitungssystem durch Verschieben des Regelschiebers in seine Geschlossen-Stellung verschließen.The impeller discussed above with the control slide arranged thereon can also be used as a kind of check valve in a piping system. Depending on the direction of flow and Anströmdruck the slide can continue to promote on the impeller and the shaft shaft holding the oncoming medium or, at a correspondingly high flow pressure against the conveying direction, close the pipe system by moving the control slide in its closed position.

Obgleich die hier diskutierte elektrische Kühlmittelpumpe 5 einen Elektromotor 7 mit einer Leistung zwischen 20W und 100W aufweist, kann auch ein leistungsstärkerer Elektromotor, beispielsweise bis hin zu 2kW eingesetzt werden, so dass die elektrische Kühlmittelpumpe gegebenenfalls auch als einzige Pumpe im Kühlkreislauf die Zirkulation des Kühlmittels übernehmen kann.Although the electric coolant pump 5 discussed here has an electric motor 7 with a power between 20W and 100W, a more powerful electric motor, for example up to 2 kW, can also be used, so that the electric coolant pump may possibly also take over the circulation of the coolant as the only pump in the cooling circuit can.

Die vorliegende Erfindung betrifft ein regelbares Kühlsystem 1 für ein Kraftfahrzeug mit einem Kühlmittelkreislauf, der ein Kühlmittel zu einer Verbrennungskraftmaschine hinführt und von dieser ableitet, sowie einer mechanisch betriebenen, regelbaren Haupt-Kühlmittelpumpe 3 und einer elektrisch betriebenen, regelbaren Sekundär-Kühlmittelpumpe 5.The present invention relates to a controllable cooling system 1 for a motor vehicle with a coolant circuit which leads and discharges a coolant to an internal combustion engine, as well as a mechanically operated, controllable main coolant pump 3 and an electrically operated, controllable secondary coolant pump 5.

Das Kühlsystem umfasst ferner eine Steuervorrichtung, welche die Haupt-Kühlmittelpumpe 3 und die Sekundär-Kühlmittelpumpe 5 in Abhängigkeit von Betriebszuständen der Verbrennungskraftmaschine steuert. Die Erfindung schafft ferner eine elektrisch betriebene, regelbare Sekundär-Kühlmittelpumpe 5 für ein derartiges Kühlsystem 1, ein in dieser Sekundär-Kühlmittelpumpe 5 verwendbares Flügelrad 25 sowie ein Verfahren zum Regeln des Kühlmittelflusses in einem derartigen Kühlsystem 1.The cooling system further includes a control device that controls the main coolant pump 3 and the secondary coolant pump 5 depending on operating conditions of the internal combustion engine. The invention further provides an electrically operated, controllable secondary coolant pump 5 for such a cooling system 1, an impeller 25 which can be used in this secondary coolant pump 5 and a method for regulating the coolant flow in such a cooling system 1.

Claims (25)

  1. A controllable cooling system (1) for a motor vehicle, comprising:
    a coolant circuit for supplying and discharging coolant to and from an internal combustion engine of the vehicle;
    a mechanically operated, controllable main coolant pump (3) comprising an inlet (17) for supplying the coolant into the main coolant pump (3) and an outlet (15) for discharging the coolant to the internal combustion engine, and
    an electrically operated, controllable secondary coolant pump (5) comprising an inlet (9) for supplying the coolant into the secondary coolant pump (5) and an outlet (11) for discharging a coolant, conveyed as a bypass coolant flow, towards the main coolant pump (3), wherein
    the secondary coolant pump (5) is arranged upstream of the main coolant pump (3) in the direction of flow, branching off from a coolant line (13) leading to the main coolant pump (3) in the direction of coolant flow,
    the coolant conveyed by means of the secondary coolant pump (5) is supplied, downstream of the main coolant pump (3) and without flowing through the main coolant pump (3), into the outlet (15) leading to the internal combustion engine,
    the secondary coolant pump (5) comprises a pump casing (51) with a pump chamber (53) formed therein, wherein on a section of the pump casing (51) an electric motor (7) is arranged which provides driving power for the secondary coolant pump (5) by means of a drive shaft (21) extending into the pump chamber (53),
    the secondary coolant pump (5) in the pump chamber (53) comprises an impeller (25) serving as a conveyor member which is coaxially arranged on the drive shaft (21) and drivably connected thereto, and
    the secondary coolant pump (5) comprises a control slide valve (31) formed on the impeller (25) which can be moved at least to open and closed positions, for controlling the bypass coolant flow conveyed by the secondary coolant pump (5), particularly for preventing back-flow of the coolant in a direction opposite to the conveying direction of the secondary coolant pump (5).
  2. The system according to claim 1, wherein the main coolant pump (3) comprises a pump casing with a pump chamber formed therein, wherein an impeller serving as a conveyor member is arranged in the pump chamber and is driven via a shaft extending into the pump chamber which is preferably driven by a belt drive.
  3. The system according to claim 1 or 2, wherein the main coolant pump (3) further comprises a control slide valve formed on the impeller and arranged coaxially thereto which can be moved at least to open and closed positions, preferably along the impeller mounted in the pump chamber, for controlling the coolant flow conveyed by the main coolant pump (3).
  4. The system according to claim 1, wherein the electric motor (7) of the secondary coolant pump (5) is designed as a dry rotor or wet rotor.
  5. The system according to any one of claims 1 to 4, further comprising a control device which controls the main coolant pump (3) and/or the secondary coolant pump (5) in dependence on assigned operating conditions of the internal combustion engine.
  6. An electric coolant pump (5) for use in a cooling system (1) according to any one of claims 1 to 5, wherein the electric coolant pump (5) is designed as a radial flow pump and comprises:
    a pump casing (51);
    a preferably flange-like inlet (9) and a preferably flange-like outlet (11);
    a pump chamber (53) formed in the pump casing (51), wherein a pump wheel (25) is arranged on a pump shaft (21) in the pump chamber (53), the pump wheel (25) being drivable by an electric motor (7) through the intermediary of the pump shaft (21), and
    a slide valve (31) that is displaceable at least to open and closed positions, for controlling a bypass coolant flow conveyed by the coolant pump (5), particularly for preventing back-flow of the coolant in a direction opposite to the conveying direction of the secondary coolant pump (5), wherein
    the coolant to be conveyed, diverted from a coolant line (13), can be introduced into the pump chamber (53) formed in the pump casing (51) through the substantially conically extending inlet (9), and the coolant introduced into the pump chamber (53) can be discharged from the pump chamber (53) through the outlet (11) arranged substantially at a right angle radially to the inlet line (9); wherein
    the impeller (25) arranged in the pump chamber (53) and designed as a radial flow pump impeller sucks the coolant in through rotational movement in an axial direction and conveys it into the outlet (11) in a radial direction;
    the slide valve (31) is designed as a control slide valve (31) arranged coaxially to the pump shaft (21) on the impeller (25); and
    the electric motor (7) is preferably arranged on a section of the pump casing (51) facing away from the inlet (9); wherein
    the electric motor (7) comprises a drive shaft (21) protruding into the pump chamber (53),
    the impeller (25) and the control slide valve (31) are coaxially arranged on the drive shaft (21) and are retained on the drive shaft (21) in a positive fit manner, preferably by means of retaining members (47), and
    the control slide valve (31) is cylindrically designed, enclosing the impeller (25), and is displaceable in an axial direction of the impeller (25) to open and closed positions.
  7. The coolant pump (5) according to claim 6, wherein the control slide valve (31) is connected to the impeller (25) such that blades (39) of the impeller (25) penetrate the control slide valve (31).
  8. The coolant pump (5) according to any one of claims 6 or 7, wherein the electric motor (7) is designed as a dry rotor and is sealed from the pump chamber (53) by means of a shaft seal (29) arranged on the drive shaft (21), or wherein the electric motor (7) is designed as a wet rotor and is cooled by the coolant conveyed by the coolant pump (5).
  9. The coolant pump (5) according to any one of claims 6 to 8, wherein the control slide valve (31) is displaceable along the drive shaft (21) by means of at least one actuator arranged in the coolant pump (5), wherein the actuator is designed as a pneumatically, magnetically and/or hydraulically actuated slide valve or as an electric servomotor, or
    the control slide valve (31) comprises a section (33) enclosing the drive shaft (21) and facing towards the inlet (9), with a threaded section formed on its inner circumference.
  10. The coolant pump (5) according to any one of claims 6 to 9, wherein a threaded section complementary to the threaded section (33) of the control slide valve (31) is formed on a section (23) of the drive shaft (21) facing away from the electric motor (7), and the control slide valve (31) is displaceable along the drive shaft (21) by mutual engagement of the threaded sections (23, 33).
  11. The coolant pump (5) according to any one of claims 6 to 10, wherein the control slide valve is designed to follow the contour of the front side of the impeller (25) and has arranged at its outer end a radially continuous closure member (35), wherein a first sealing member (43), arranged radially outside the control slide valve (31), is disposed at an end of the closure member (35) facing away from the electric motor (7), wherein
    a receptacle (37) into which the closure member (35) of the control slide valve (31) can be introduced in the open position thereof is preferably formed in the pump chamber (53).
  12. The coolant pump (5) according to any one of claims 6 to 11, wherein a second sealing member (45), arranged radially inside the control slide valve (31), is disposed at a radially outer end of the impeller (25) facing towards the electric motor (7).
  13. The coolant pump (5) according to any one of claims 11 or 12, wherein the diameter of the first sealing member (43) is larger than the diameter of the second sealing member (45).
  14. The coolant pump (5) according to any one of claims 11 to 13, wherein the outlet (11) can be tightly closed, via the closure member (35), the first sealing member (43) and the second sealing member (45), by the control slide valve (21) in the closed position thereof.
  15. The coolant pump (5) according to any one of claims 6 to 14, wherein a braking member (27) is further provided, by means of which the impeller (25) can be secured to an inner wall (49) of the pump casing (51),
    wherein the braking member (27) is preferably formed on the impeller (25) and preferably consists of a pretensioned braking spring or plate-like brake disc which preferably comprises at its radially outer ends, in a radially inward direction, substantially wedge-tapered thickenings (41), wherein the braking member (27) can be brought into frictional engagement with the inner wall (49) of the pump casing (51) adjoining the electric motor (7), preferably by means of the thickenings (41), to secure the impeller (25) to the pump casing (51) and wherein the braking member (27), including, in particular, the thickenings (41) thereof, is preferably designed to disconnect from the inner wall (49) of the pump casing (51) as the speed of rotation of the impeller (25) caused by the drive shaft (21) of the electric motor (7) increases, so as to disengage the impeller (25).
  16. An impeller (25) for use in a coolant pump (5) according to any one of claims 6 to 15 for a cooling system (1) according to any one of claims 1 to 5, said impeller comprising:
    a plurality of blades (39) that are preferably typical of radial flow pumps and formed on the impeller surface facing towards a coolant inlet (9);
    a recess (55) for receiving a drive shaft (21);
    a control slide valve (31) connected to the impeller (25); and
    a braking member (27) arranged on the impeller (25).
  17. The impeller (25) according to claim 16, wherein the control slide valve (31) comprises at its front end a first sealing member (43) arranged radially outside thereof and the impeller (25) comprises at its radially outer end a second sealing member (45) arranged radially inside the control slide valve (31).
  18. The impeller (25) according to claim 16 or 17, wherein the control slide valve (31) is integrally formed with the impeller (25) such that the blades (39) of the impeller (25) penetrate the control slide valve (31) in an axial direction.
  19. The impeller (25) according to claim 16, wherein the braking member (27) is formed on a back side surface of the impeller (25),
    wherein the braking member (27) preferably consists of a pretensioned braking spring or plate-like brake disc capable of being brought into frictional engagement with a surface opposite the back side surface of the impeller (25), to secure the impeller (25) to this surface, and
    wherein the braking member (27) is preferably designed such that its braking effect decreases as the speed of rotation of the impeller (25) increases, whereby it approaches the back side surface of the impeller (25) to disengage the impeller (25).
  20. The impeller according to any one of claims 16 to 18, wherein the control slide valve (31) is designed to follow the contour of the impeller (25) and comprises at its outer end a radially continuous closure member (35).
  21. The impeller according to any one of claims 16 to 18 and 20, wherein the control slide valve (31) comprises in its frontal area a hollow, compartment-like section (33) with a threaded section formed on the inner circumferential wall thereof.
  22. A method for controlling a coolant flow in a cooling system (1) of a motor vehicle according to any one of claims 1 to 5, wherein the cooling system (1) comprises a controllable main coolant pump (3) mechanically operated by the driving force of an internal combustion engine arranged in the vehicle and a controllable secondary coolant pump (5) electrically operated by a separately arranged electric motor, said method comprising the steps of:
    detecting a current operating condition of an internal combustion engine of the vehicle;
    detecting a coolant temperature of a coolant circulating in a coolant circuit of the vehicle;
    reading out control parameters from a cooling circuit map;
    controlling the main coolant pump (3) and the secondary coolant pump (5) based upon the control parameters read out from the cooling circuit map; and
    controlling the coolant flow by selectively switching the main coolant pump (3) and/or the secondary coolant pump (5).
  23. The method according to claim 22, wherein the current operating condition of the internal combustion engine includes a start-stop condition, a warm-up condition, a low-load condition, a normal-load condition, an eco condition, a high-rpm condition, and a residual heat storing condition.
  24. The method according to claim 22 or 23, wherein the control parameters in the cooling circuit map include at least a desired coolant temperature, and/or a desired motor temperature, and/or a desired coolant flow rate, and/or the like.
  25. The method according to claim 22, wherein,
    when the current operating condition of the internal combustion engine is the warm-up condition, the secondary coolant pump (5) is switched to an OFF-mode condition and a coolant flow through the main coolant pump (3) is interrupted by means of a control slide valve (31) arranged in the main coolant pump (3), such that circulation of the coolant is interrupted,
    when the current operating condition of the internal combustion engine is the start-stop condition in which the main coolant pump (3) is temporarily unpowered during a stop phase of the internal combustion engine, the secondary coolant pump (5) is switched to an ON-mode condition, by means of which the coolant is circulated through the secondary coolant pump (5),
    when the current operating condition of the internal combustion engine is the low-load condition, a coolant flow through the main coolant pump (3) is interrupted by means of a control slide valve arranged in the main coolant pump (3) and the secondary coolant pump (5) is switched to an ON-mode condition, by means of which the coolant is circulated through the secondary coolant pump (5),
    when the current operating condition of the internal combustion engine is the normal-load condition, the secondary coolant pump (5) is switched to an OFF-mode condition and the control slide valve (31) thereof is closed, by means of which the coolant in the coolant circuit is circulated through the main coolant pump (3),
    when the current operating condition of the internal combustion engine is the eco condition, operation of the main coolant pump (3) is selectively interrupted by means of an overrunning clutch provided on the belt drive system of the main coolant pump (3), or a control slide valve arranged in the main coolant pump (3) is controlled such that the coolant flow in the main coolant pump (3) is interrupted and the coolant is circulated through the secondary coolant pump (5) in order for a desired elevated motor temperature to be obtained,
    when the current operating condition of the internal combustion engine is the high-rpm condition, the coolant flow of the main coolant pump (3) is routed, at least in part, in the bypass mode via the secondary coolant pump (5) to the intake side of the main coolant pump (5), or
    when the current operating state of the internal combustion engine is the residual heat storing condition with the internal combustion engine at a standstill, both the control slide valve of the main coolant pump (3) and the control slide valve (31) of the secondary coolant pump (5) are closed in order to prevent circulation of the coolant in the cooling circuit.
EP11793659.1A 2011-03-04 2011-11-29 Controllable cooling system for a motor vehicle, coolant pump therefor, impeller for use in the coolant pump, and method for controlling a coolant flow in such a cooling system Active EP2681425B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102011001090A DE102011001090A1 (en) 2011-03-04 2011-03-04 Controllable cooling system for a motor vehicle, coolant pump therefor, usable in the coolant pump impeller and method for controlling a flow of coolant in such a cooling system
PCT/EP2011/005982 WO2012119622A2 (en) 2011-03-04 2011-11-29 Controllable cooling system for a motor vehicle, coolant pump therefor, impeller for use in the coolant pump, and method for controlling a coolant flow in such a cooling system

Publications (2)

Publication Number Publication Date
EP2681425A2 EP2681425A2 (en) 2014-01-08
EP2681425B1 true EP2681425B1 (en) 2016-07-06

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EP11793659.1A Active EP2681425B1 (en) 2011-03-04 2011-11-29 Controllable cooling system for a motor vehicle, coolant pump therefor, impeller for use in the coolant pump, and method for controlling a coolant flow in such a cooling system

Country Status (6)

Country Link
US (1) US20130333863A1 (en)
EP (1) EP2681425B1 (en)
CN (1) CN103459798B (en)
DE (1) DE102011001090A1 (en)
ES (1) ES2587598T3 (en)
WO (1) WO2012119622A2 (en)

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Also Published As

Publication number Publication date
DE102011001090A1 (en) 2012-09-06
WO2012119622A3 (en) 2012-10-26
CN103459798B (en) 2016-03-16
EP2681425A2 (en) 2014-01-08
CN103459798A (en) 2013-12-18
WO2012119622A2 (en) 2012-09-13
ES2587598T3 (en) 2016-10-25
US20130333863A1 (en) 2013-12-19

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