EP3172445B1 - Coolant pump with integrated closed-loop control - Google Patents
Coolant pump with integrated closed-loop control Download PDFInfo
- Publication number
- EP3172445B1 EP3172445B1 EP15738683.0A EP15738683A EP3172445B1 EP 3172445 B1 EP3172445 B1 EP 3172445B1 EP 15738683 A EP15738683 A EP 15738683A EP 3172445 B1 EP3172445 B1 EP 3172445B1
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- EP
- European Patent Office
- Prior art keywords
- pump
- coolant
- control
- pumped
- volume flow
- 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.)
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
- F01P7/00—Controlling of coolant flow
- F01P7/14—Controlling of coolant flow the coolant being liquid
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
- F01P3/00—Liquid cooling
- F01P3/20—Cooling circuits not specific to a single part of engine or machine
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
- F01P5/00—Pumping cooling-air or liquid coolants
- F01P5/10—Pumping liquid coolant; Arrangements of coolant pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
- F01P5/00—Pumping cooling-air or liquid coolants
- F01P5/10—Pumping liquid coolant; Arrangements of coolant pumps
- F01P5/12—Pump-driving arrangements
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
- F01P7/00—Controlling of coolant flow
- F01P7/14—Controlling of coolant flow the coolant being liquid
- F01P7/16—Controlling of coolant flow the coolant being liquid by thermostatic control
- F01P7/164—Controlling of coolant flow the coolant being liquid by thermostatic control by varying pump speed
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B19/00—Machines or pumps having pertinent characteristics not provided for in, or of interest apart from, groups F04B1/00 - F04B17/00
- F04B19/20—Other positive-displacement pumps
- F04B19/22—Other positive-displacement pumps of reciprocating-piston type
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D1/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D13/00—Pumping installations or systems
- F04D13/12—Combinations of two or more pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D15/00—Control, e.g. regulation, of pumps, pumping installations or systems
- F04D15/0027—Varying behaviour or the very pump
- F04D15/0038—Varying behaviour or the very pump by varying the effective cross-sectional area of flow through the rotor
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
- F01P5/00—Pumping cooling-air or liquid coolants
- F01P5/10—Pumping liquid coolant; Arrangements of coolant pumps
- F01P2005/105—Using two or more pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
- F01P7/00—Controlling of coolant flow
- F01P7/14—Controlling of coolant flow the coolant being liquid
- F01P2007/146—Controlling of coolant flow the coolant being liquid using valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
- F01P2025/00—Measuring
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2270/00—Control
- F05D2270/60—Control system actuates means
- F05D2270/64—Hydraulic actuators
Definitions
- the present invention relates to a coolant pump for delivering a coolant for an internal combustion engine in a vehicle having the engine and a central engine controller.
- coolant pumps have been developed, which allow a reliable and stepless adjustment of the volume flow of the circulating coolant.
- the heat output of the cooling system is controlled in dependence on a current operating state. During a cold start phase, for example, the heat release is initially completely and subsequently partially prevented.
- coolant pumps with an electrohydraulically controlled control slide for adjusting the volume flow have proven to be particularly reliable in the course of this development.
- a pump of this type which has become known as ECF pumps (Electro-hydraulic Controlled Flow), is described, for example, in the German patent DE 10 2008 026 218 B4 the applicant discloses.
- a cylindrical control slide is displaced by a hydraulic actuator around a peripheral region of an impeller of the coolant pump.
- the hydraulic pressure of the actuator is not produced here by a closed circuit with a hydraulic oil, but applied via a side stream of the coolant. Pumps with such a coolant-based hydraulic system do not require additional dynamic sealing locations to the atmosphere and have proven themselves by a long service life and a reliable control.
- the volume flow of the coolant that is to be conveyed by a coolant pump is usually controlled by a central engine control ZMS of a vehicle.
- a position of the control slide is detected for this purpose and transmitted to the central engine control ZMS.
- the central engine control ZMS controls in dependence on further operating parameters, such as. a rotation speed of the internal combustion engine, a workload of the internal combustion engine, a fuel supply amount, a temperature, or the like, an electromagnetic valve in the hydraulic circuit.
- a correspondingly high number of electrical lines from the central engine control ZMS to the individual members of the control loop is required.
- an ECF pump At least two lines for power supply and signal communication are to be installed from the central engine control ZMS to the displacement sensor as well as from the central engine control ZMS to the electromagnetic valve.
- the invention has for its object to provide a coolant pump that requires little installation effort and ensures high reliability in a corrosive environment.
- this coolant pump is characterized in that it comprises a separate pump control, which controls a proportional valve in a hydraulic circuit based on the actual value signal from the sensor and a setpoint signal from the central engine control, and that the pump control and the proportional valve as a common electromechanical component are formed.
- the invention thus provides for the first time in the design of a coolant pump a dedicated control circuit for position control of a control slide, which is present with a hydraulic actuator as an integrated component.
- the coolant pump according to the invention has a reduced number of electrical lines to the central engine control compared to a conventional system.
- the susceptibility of the coolant pump can be improved because exposed in the engine compartment of the vehicle, the weather conditions and swirling grit, corrosion-sensitive connectors and / or outlet seals on the pump housing for the wiring can be saved.
- a program routine for regulating the position of the control slide is omitted in the central engine control.
- a processing load of the central engine control can be reduced.
- a central motor controller with lower processing power can be used at a correspondingly lower cost, or the additional processing power can be made available for control tasks of other peripheral devices, or in favor of an increased clocking of the calculation cycles.
- the senor may be a displacement sensor, in particular a Hall sensor, which detects a position of the control slide.
- the set value signal indicates a predetermined position of the control valve, or a predetermined volume flow and a rotational speed of the internal combustion engine or the coolant pump.
- the position control in the pump control can be implemented with a simple calculation routine.
- the computing capacity of the pump controller and the energy demand or the resulting waste heat in a sealed electronic component can be kept low.
- the setpoint signal from the central engine control indicates a predetermined volumetric flow and a rotational speed
- a calculation routine takes place between a volumetric flow and a position of the control spool to be regulated as a function of the pump rotational speed by the pump control.
- the central motor control transmits as a setpoint signal only a value corresponding to a volume flow, ie a quantity of heat to be dissipated.
- the required heat output is from the central Engine control calculable from the operating parameters of the internal combustion engine.
- the pump controller may limit a travel of the control spool in an upper range of the pump speed.
- the pump control thereby provides a protective function for components such as e.g. Seals in the cooling system to limit a maximum flow and the resulting pressure.
- the pump controller may compare a ratio between a driving duration of the proportional valve and a resultant positional change of the control spool to a threshold value. In this way, the pump control performs an autonomous function monitoring to ensure a sufficient charge of the cooling system with coolant.
- the existing hydraulic circuit is used here as a pressure-sensitive sensor, the function monitoring for the early detection of a leak without the provision of additional measuring elements, such as pressure gauges or other sensors, can be realized in the cooling system. As a result, the number of components and wiring and the cost and installation costs can be kept low.
- the senor may be a pressure sensor that detects a pressure of the delivered volume flow of the coolant.
- the setpoint signal indicates a predetermined volume flow or pressure indicative of the volume flow of the delivered coolant.
- the pressure sensor may preferably detect a pressure in the pump chamber, which is in relation to the delivered volume flow of the coolant pump.
- the pump controller may compare the sensed pressure of the sensor to a threshold.
- the pump control of the alternative embodiment with a pressure sensor can perform an autonomous function monitoring to ensure a sufficient filling amount of the cooling system with coolant particularly easy.
- the function monitoring for the early detection of a leak can also be realized in this embodiment without the provision of further measuring elements in the cooling system, whereby the number of components and wiring and the cost and installation costs can be kept low.
- the pump controller may include a transceiver for receiving data from the central engine controller and / or sending data thereto, a microcomputer for executing a control routine, a valve driver for driving the proportional valve, and a power supply manifold for supplying them respectively include electrical power.
- a control circuit of the pump controller can be realized with small dimensions and advantageous mounting options on the coolant pump.
- the pump controller may have its own housing integrated in the common electromechanical component.
- electromagnetic interference radiation for example, can be effectively shielded from the control circuit of the pump control, starting from the proportional valve arranged in the electromechanical component, in particular with a magnetically actuated valve.
- the proportional valve may have its own housing, which is integrated with the common electromechanical component 20.
- this structure can also be an electromagnetic interference radiation from a magnetic actuation of the Shield the proportional valve effectively against the control circuit of the pump control.
- the coolant to be conveyed can flow axially directed onto the impeller through a coolant inlet and out of the pump chamber via a radially directed coolant outlet, conveyed by the impeller.
- the invention is applied to the construction of a radial pump.
- the coolant to be conveyed can flow axially directed onto the impeller through a coolant inlet and out of the pump chamber via an axially or semi-axially directed coolant outlet on the opposite side of the impeller.
- the invention is applied to the structure of an axial pump or a Halbaxialpumpe.
- An inventive electronic component of the coolant pump is formed as a common electromechanical component of the pump control and the proportional valve of the coolant pump.
- a method according to the invention for controlling the mechanically driven coolant pump of a vehicle according to the invention with an internal combustion engine and a central engine control comprises, in a first alternative, the following steps: calculating a desired value of a parameter indicative of the volume flow of the delivered coolant as a function of operating parameters Internal combustion engine through the central engine control; Transmitting the setpoint from the central engine controller to a pump controller of the coolant pump; Detecting an actual value of the parameter by a sensor; Transferring the actual value from the sensor to the pump controller; and adjusting a position of a control slide, which limits the delivered volume flow of the coolant pump, as a function of the desired value and the actual value by the pump control, by means of control of a hydraulic actuator.
- the invention is applied to a coolant pump of said embodiments.
- the inventive method for controlling the mechanically driven coolant pump according to the invention of a vehicle with an internal combustion engine and a central engine control comprises in a second alternative the following steps: transferring operating parameters of the internal combustion engine from the central engine control to a pump control of the coolant pump; Calculating a setpoint value of a parameter indicative of the volume flow of the delivered coolant as a function of the operating parameters of the internal combustion engine by the pump controller; Detecting an actual value of the parameter by a sensor; Transferring the actual value from the sensor to the pump controller; and adjusting a position of a control slide, which limits the delivered volume flow of the coolant pump, as a function of the desired value and the actual value by the pump control, by means of control of a hydraulic actuator.
- the invention is applied to a coolant pump of said embodiments.
- the parameter indicative of the volume flow of the delivered coolant may be a position of the control spool.
- the control method can be applied to the structure of the coolant pump according to the invention mentioned above.
- the parameter indicative of the volume flow of the delivered coolant may be a pressure in a pump chamber of the coolant pump corresponding to the volume flow of the pumped Coolant corresponds.
- the coolant pump has a pump housing 1 and a pump shaft 4 rotatably mounted therein with a pulley 3, which is driven by a belt drive by an internal combustion engine (not shown).
- an impeller 5 is rotatably arranged, which is introduced within a pump chamber 2 in a flow region of a cooling circuit of the internal combustion engine to a volume flow of the coolant effect.
- the coolant is sucked through an axial inlet of the pump chamber 2, in the region of a middle radius of the impeller 5, and discharged, for example, through a radial outlet (not shown) of the pump chamber 2 facing a peripheral portion of the impeller 5.
- the flow region of the impeller 5 can be variably covered by a control slide 7 with a cylindrical section 7a arranged coaxially with the pump shaft and a rear wall section 7b along an adjustment path running parallel to the pump shaft 4. Between the inner peripheral wall of the cylindrical portion 7a of the control slide 7 and a rear wall of the pump chamber 2 extends a sealing lip 6. In Fig. 1 and 2 the control slide 7 is in an "open position", in which the flow region of the impeller 5 is not covered.
- an axial piston pump 9 is further arranged to the rear of the impeller 5 and parallel to the pump shaft 4, the piston is actuated via a sliding shoe which slides on a swash plate 8 on the rear side of the impeller 5 together with this rotatably to the pump shaft 4 is arranged.
- the axial piston pump 9 sucks in coolant from the flow area in the pump chamber 2 between the impeller 5 and the control slide 7 and discharges the refrigerant under pressure into a hydraulic circuit 11 which is formed in the pump housing 1.
- the hydraulic circuit 11 branches into two branches 11a and 11b.
- the one branch 11a of the hydraulic circuit 11 leads, on the one hand, to an electromagnetic proportional valve 13 and back again into the conveyed coolant flow.
- the other branch 11 b of the hydraulic circuit 11 leads to an annular piston 15, which is arranged coaxially with the pump shaft 4 and assumes the function of a hydraulic actuator along the displacement of the control slide 7.
- a return spring 17 acts on the annular piston 15 in the opposite direction to the pressure of the hydraulic circuit 11, ie away from the impeller 5.
- the annular piston 15 communicates with the control slide 7 and shifts it with increasing pressure of the hydraulic circuit 11 in the direction of the impeller. 5
- the electromagnetic proportional valve 13 is opened without supplying a drive current, so that the sucked by the axial piston pump 9 refrigerant flows back substantially unpressurized via the branch 11a of the hydraulic circuit 11 through the proportional valve 13 back into the funded coolant flow.
- the branch 11b of the hydraulic circuit 11 no pressure builds up and the annular piston 15 remains under the action of the return spring 17 in an unactuated basic position.
- the control slide 7, which is in communication with the annular piston 15 is held in the "open position", as in Fig. 1 and 2 is shown.
- the refrigerant discharged from the axial piston pump 9 can not flow back into the volume flow via the branch 11 a of the hydraulic circuit 11.
- the pressure exerted by the axial piston pump 9 in the hydraulic circuit 11 spreads from the backflow at the closed proportional valve 13 via the branch 11a in the branch 11b and acts on the annular piston 15.
- the annular piston 15 moves the control slide 7 against the force of the return spring 17 the impeller. It is the cylindrical portion 7a of the control slide 7 increasingly brought into axial overlap with the impeller 5, whereby an effective flow region of the impeller 5 is radially covered by the cylindrical portion 7a of the control slide 7.
- the central engine control ZMS calculates taking into account various operating parameters, e.g. a speed and work load of the internal combustion engine, a fuel supply, a temperature, a vehicle speed or the like, a volume flow of the coolant to be delivered, which corresponds to a required heat output of the internal combustion engine.
- various operating parameters e.g. a speed and work load of the internal combustion engine, a fuel supply, a temperature, a vehicle speed or the like, a volume flow of the coolant to be delivered, which corresponds to a required heat output of the internal combustion engine.
- a volume flow of the coolant conveyed by the coolant pump depends on the flow efficiency of the impeller 5, which increases with increasing axial displacement of the position of the control slide 7 (and the annular piston 15) in the direction of the "closed position" with an increasing degree the overlap by the cylindrical portion 7a of the control slide 7 to the impeller 5 decreases.
- the delivered volume flow of the coolant pump depends on the pump speed.
- the pump speed is forcibly determined by means of the belt drive by the speed of the internal combustion engine and includes the characteristic of vehicle operation fluctuations.
- the power supply manifold divides the voltage of a vehicle power source (not shown) of, for example, 12V into appropriate voltages the electronic components 23, 25, 27 of the pump controller 21 and supplies them with the required electrical power.
- the LIN transceiver 23 enables communication of data via a data bus, eg in the LIN protocol, between the pump controller 21 and the central engine control ZMS.
- a plug 22 may be provided for connection to a vehicle-side data bus to the central engine control ZMS.
- the microcomputer 25 executes a control routine with a control routine stored in a memory (not shown) of the microcomputer 25, and calculates a pulse width modulation as a drive signal of the valve driver 27.
- the valve driver 27 amplifies the drive signal from the microcomputer 25 by supplying a power for actuating the electromagnetic proportional valve 13 from the power supply manifold 29 in accordance with the pulse width modulation on and off.
- the pump controller 21 is formed together with a solenoid valve as a common electromechanical component 20.
- a control circuit of the pump control 21 and an electromagnetic control of the proportional valve 13 may be cast in an encapsulated component.
- the circuit board of the pump controller 21 may, for example, have a circular shape, so that it can be integrated in the region of the housing bottom with little space requirement.
- an upgrade of a known ECF pump can also be carried out without modifications to the pump structure.
- the pump controller 21 may be integrated with an outer portion of the housing of the proportional valve 13, as in FIG Fig. 3B is shown.
- the structure shown can preferably be realized with a Hall sensor as a displacement sensor 19.
- this embodiment is not limited to a Hall sensor, as will be described later in another embodiment.
- a displacement sensor 19 is used for detecting a position of the control slide 7 along a Verstellwegs. Through a Hall sensor and a magnetic encoder element, which is connected to the annular piston 15, a contactless and insensitive construction is produced. The displacement sensor 19 outputs as an actual value signal the detected position of the annular piston 15 or, accordingly, of the control slide 7 along the displacement path to the pump control 21.
- the setpoint signal which receives the pump controller 21 from the central engine control ZMS, contains a predetermined position of the control slide 7.
- the central engine control ZMS calculates a volume flow to be delivered by the coolant pump, based on the heat output of the internal combustion engine required coolant.
- the predetermined position of the control slide is then calculated in dependence on the volume flow and a current pump speed, which is in a fixed speed ratio to the engine, and transmitted to the pump controller 21.
- the setpoint signal received by the pump controller 21 from the central engine control ZMS includes only a setpoint value for a required volumetric flow of the coolant and further operating parameters, in particular a current speed of the internal combustion engine or the corresponding pump speed.
- the calculation of a setpoint value for the resulting position of the control slide 7 takes place in the pump controller 21 in this embodiment.
- the control routine executed in the microcomputer 25, for example, corresponds to the control function of a PID gate in which a control deviation is calculated between the predetermined set value and the actual value. From the control deviation is based on a system-specific function of the hydraulic circuit 11, i. a reaction behavior between an on and off duration of the electromagnetic proportional valve 13 and a resulting change in position of the annular piston 15 as a hydraulic actuator, a pulse width modulation for controlling the electromagnetic proportional valve 13 is calculated.
- the pressure in the hydraulic circuit 11 is controlled by the on and off periods for opening and closing the proportional valve 13 such that a balance between the hydraulic pressure and the pressure of the return spring 17 in a position of Ring piston 15 and the control slide 7 is achieved and maintained, which corresponds to the predetermined setpoint of the central engine control ZMS.
- the actual position of the control slide 7 is in turn detected by the displacement sensor 19 and transmitted as feedback to the control of the proportional valve 13 to the pump controller 21 and entered into the microcomputer 25.
- the pump controller 21 performs a function monitoring in order to independently detect a leak in the cooling system and to report it to the central engine control.
- the pump controller 21 can detect deviations in the reaction behavior of the hydraulic circuit with the required sensitivity, ie in particular without influences of other operating parameters such as permanent fluctuations of speed and temperature ,
- the pump controller 21 compares a deviation of the ratio between the on and Ausschaltdauem of the electromagnetic proportional valve 13 and the resulting change in position of the annular piston 15 and control slide 7 with a stored in the memory threshold.
- the threshold value as well as other specific parameters of the coolant pump are stored in a memory section of the pump control 21.
- the pump controller 21 In the case of fault detection, the pump controller 21 outputs an error message to the central engine control, which in turn can initiate a limited emergency operation or shutdown of the internal combustion engine.
- the coolant pump has a pressure sensor (not shown) instead of a displacement sensor 19, which is preferably arranged between the annular piston 15 and the control slide 7.
- the pump controller 21 performs a control in that the control slide 7 is moved to adjust the flow in a new position until the actual value signal of the detected pressure of the pressure sensor corresponds to a pressure of the predetermined volume flow, which is determined by the setpoint Signal from the central engine control ZMS is specified.
- a function monitoring of the cooling system can be easily perceived via the existing pressure sensor rather than via the reaction behavior of the hydraulic actuator.
- a threshold value is stored in a storage section of the pump controller. This threshold corresponds to a minimum operating pressure, which falls below in particular in the formation of trapped air in the cooling system.
- the pump controller 21 In the case of fault detection, the pump controller 21 outputs an error message to the central engine control ZMS, which in turn can initiate a limited emergency operation or shutdown of the internal combustion engine.
- a CAN interface can be provided between the pump controller 21 and the central engine control ZMS.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Control Of Non-Positive-Displacement Pumps (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Description
Die vorliegende Erfindung betrifft eine Kühlmittelpumpe zum Fördern eines Kühlmittels für einen Verbrennungsmotor in einem Fahrzeug, das den Verbrennungsmotor und eine zentrale Motorsteuerung aufweist.The present invention relates to a coolant pump for delivering a coolant for an internal combustion engine in a vehicle having the engine and a central engine controller.
Im Hinblick auf die Reduzierung von Kraftstoffverbrauch und Emissionen bei Fahrzeugen wurden Entwicklungen unternommen, um das Thermomanagement von Verbrennungsmotoren effizienter zu gestalten. Hierzu wurden Kühlmittelpumpen entwickelt, die eine zuverlässige und stufenlose Einstellung des Volumenstroms des zirkulierenden Kühlmittels ermöglichen. Um die Verbrennungsmaschine für eine effiziente Verbrennung und geringe Abgasemission in einem optimalen Temperaturbereich zu halten, wird der Wärmeaustrag des Kühlsystems in Abhängigkeit eines aktuellen Betriebszustands gesteuert. Während einer Kaltstartphase wird der Wärmeaustrag beispielsweise zunächst ganz und darauffolgend teilweise unterbunden.With a view to reducing fuel consumption and emissions from vehicles, developments have been made to make thermal management of internal combustion engines more efficient. For this purpose, coolant pumps have been developed, which allow a reliable and stepless adjustment of the volume flow of the circulating coolant. In order to keep the combustion engine in an optimal temperature range for efficient combustion and low exhaust emission, the heat output of the cooling system is controlled in dependence on a current operating state. During a cold start phase, for example, the heat release is initially completely and subsequently partially prevented.
Im Bereich der mechanisch angetriebenen Kühlmittelpumpen, bei denen eine Drehung der Verbrennungsmaschine über einen Riementrieb auf eine Pumpenwelle übertragen wird, haben sich im Zuge dieser Entwicklung Kühlmittelpumpen mit einem elektrohydraulisch gesteuerten Regelschieber zur Einstellung des Volumenstroms als besonders zuverlässig erwiesen. Eine Pumpe dieser Bauform, die sich unter dem Begriff ECF-Pumpen (Electro-hydraulic Controlled Flow) etabliert hat, wird beispielsweise in der deutschen Patentschrift
Bei einer solchen Kühlmittelpumpe wird ein zylindrischer Regelschieber mittels eines hydraulischen Stellgliedes um einen Umfangsbereich eines Flügelrads der Kühlmittelpumpe verschoben. Der hydraulische Druck des Stellglieds wird hierbei nicht durch einen geschlossenen Kreislauf mit einem Hydrauliköl hergestellt, sondern über einen Nebenstrom des Kühlmittels aufgebracht. Pumpen mit einem solchen Kühlmittelbasierten Hydrauliksystem erfordern keine zusätzlichen dynamischen Dichtungsstellen zur Atmosphäre und haben sich durch eine lange Lebensdauer sowie eine zuverlässige Regelung bewährt.In such a coolant pump, a cylindrical control slide is displaced by a hydraulic actuator around a peripheral region of an impeller of the coolant pump. The hydraulic pressure of the actuator is not produced here by a closed circuit with a hydraulic oil, but applied via a side stream of the coolant. Pumps with such a coolant-based hydraulic system do not require additional dynamic sealing locations to the atmosphere and have proven themselves by a long service life and a reliable control.
Der Volumenstrom des Kühlmittels, der von einer Kühlmittelpumpe gefördert werden soll, wird üblicherweise durch eine zentrale Motorsteuerung ZMS eines Fahrzeugs gesteuert. Bei einer bekannten Kühlmittelpumpe wird hierzu eine Position des Regelschiebers erfasst und an die zentrale Motorsteuerung ZMS übertragen. Die zentrale Motorsteuerung ZMS steuert in Abhängigkeit von weiteren Betriebsparametern, wie z.B. eine Drehzahl des Verbrennungsmotors, eine Arbeitslast des Verbrennungsmotors, eine Kraftstoffzufuhrmenge, eine Temperatur, oder dergleichen, ein elektromagnetisches Ventil im Hydraulikkreislauf an.The volume flow of the coolant that is to be conveyed by a coolant pump is usually controlled by a central engine control ZMS of a vehicle. In a known coolant pump, a position of the control slide is detected for this purpose and transmitted to the central engine control ZMS. The central engine control ZMS controls in dependence on further operating parameters, such as. a rotation speed of the internal combustion engine, a workload of the internal combustion engine, a fuel supply amount, a temperature, or the like, an electromagnetic valve in the hydraulic circuit.
Je nach Anzahl der zu erfassenden Parameter bzw. der hierfür erforderlichen Messglieder und der zu steuernden Stellglieder, ist eine entsprechend hohe Anzahl von elektrischen Leitungen von der zentralen Motorsteuerung ZMS zu den einzelnen Gliedern des Regelkreises erforderlich. Zum Einbau einer ECF-Pumpe sind wenigstens zwei Leitungen zur Leistungszufuhr und zur Signalkommunikation jeweils von der zentralen Motorsteuerung ZMS zu dem Wegsensor sowie von der zentralen Motorsteuerung ZMS zu dem elektromagnetischen Ventil zu installieren.Depending on the number of parameters to be detected or the required measuring elements and the actuators to be controlled, a correspondingly high number of electrical lines from the central engine control ZMS to the individual members of the control loop is required. To install an ECF pump, at least two lines for power supply and signal communication are to be installed from the central engine control ZMS to the displacement sensor as well as from the central engine control ZMS to the electromagnetic valve.
Der Erfindung liegt die Aufgabe zugrunde, eine Kühlmittelpumpe zu schaffen, die einen geringen Montageaufwand erfordert und eine hohe Betriebszuverlässigkeit in einer korrosiven Umgebung sicherstellt.The invention has for its object to provide a coolant pump that requires little installation effort and ensures high reliability in a corrosive environment.
Diese Aufgabe wird erfindungsgemäß durch eine Kühlmittelpumpe mit den Merkmalen des Anspruches 1 gelöst.This object is achieved by a coolant pump with the features of claim 1.
Diese Kühlmittelpumpe zeichnet sich insbesondere dadurch aus, dass sie eine eigene Pumpensteuerung umfasst, die ein Proportionalventil in einem hydraulischen Kreislauf basierend auf dem Istwert-Signal von dem Sensor und einem Sollwert-Signal von der zentralen Motorsteuerung ansteuert, und dass die Pumpensteuerung und das Proportionalventil als ein gemeinsames elektromechanisches Bauteil ausgebildet sind.In particular, this coolant pump is characterized in that it comprises a separate pump control, which controls a proportional valve in a hydraulic circuit based on the actual value signal from the sensor and a setpoint signal from the central engine control, and that the pump control and the proportional valve as a common electromechanical component are formed.
Die Erfindung sieht somit erstmals im Aufbau einer Kühlmittelpumpe eine dezidierte Steuerungsschaltung zur Positionsregelung eines Regelschiebers vor, die mit einem hydraulischen Stellglied als eine integrierte Komponente vorliegt.The invention thus provides for the first time in the design of a coolant pump a dedicated control circuit for position control of a control slide, which is present with a hydraulic actuator as an integrated component.
Dadurch weist die erfindungsgemäße Kühlmittelpumpe im Vergleich zu einem herkömmlichen System eine verringerte Anzahl von elektrischen Leitungen zu der zentralen Motorsteuerung auf. Insbesondere entfällt eine separate Leistungsversorgung und Kommunikationsschnittstelle jeweils zwischen der zentralen Motorsteuerung ZMS und dem elektromagnetischen Proportionalitätsventil, sowie der zentralen Motorsteuerung ZMS und einem Sensor zur Erfassung eines Parameters (z.B. Position des Regelschiebers), der für den Volumenstrom des geförderten Kühlmittels bezeichnend ist.As a result, the coolant pump according to the invention has a reduced number of electrical lines to the central engine control compared to a conventional system. In particular, a separate power supply and communication interface between the central engine control ZMS and the electromagnetic proportional valve, as well as the central engine control ZMS and a sensor for detecting a parameter (e.g., position of the control spool), which is indicative of the volume flow of the delivered coolant omitted.
An der erfindungsgemäßen Kühlmittelpumpe sind lediglich eine Leistungszufuhrleitung und eine Kommunikationsleitung zu der zentralen Motorsteuerung ZMS erforderlich. Die entfallenden Leitungen und Steckverbindungen vereinfachen den Aufbau und senken die Herstellungskosten der Kühlmittelpumpe sowie die Installationskosten beim Einbau in das Fahrzeug.At the coolant pump according to the invention only a power supply line and a communication line to the central engine control ZMS are required. The omitted lines and connectors simplify the construction and reduce the manufacturing cost of the coolant pump and installation costs when installed in the vehicle.
Darüber hinaus kann die Störanfälligkeit der Kühlmittelpumpe verbessert werden, da im Bereich des Motorraums des Fahrzeugs, der Witterungseinflüssen und aufgewirbeltem Streugut ausgesetzt ist, korrosionsempfindliche Steckverbindungen und/oder Austrittsdichtungen am Pumpengehäuse für die Verdrahtung eingespart werden.In addition, the susceptibility of the coolant pump can be improved because exposed in the engine compartment of the vehicle, the weather conditions and swirling grit, corrosion-sensitive connectors and / or outlet seals on the pump housing for the wiring can be saved.
Ferner entfällt in der zentralen Motorsteuerung eine Programmroutine zur Positionsregelung des Regelschiebers. Dadurch kann eine Verarbeitungsbelastung der zentralen Motorsteuerung verringert werden. Somit kann entweder eine zentrale Motorsteuerung mit geringerer Verarbeitungsleistung zu entsprechend geringeren Kosten eingesetzt werden, oder die entfallende Verarbeitungsleistung für Steuerungsaufgaben anderer Peripherievorrichtungen, oder zugunsten einer erhöhten Taktung der Berechnungszyklen zur Verfügung gestellt werden.Furthermore, a program routine for regulating the position of the control slide is omitted in the central engine control. Thereby, a processing load of the central engine control can be reduced. Thus, either a central motor controller with lower processing power can be used at a correspondingly lower cost, or the additional processing power can be made available for control tasks of other peripheral devices, or in favor of an increased clocking of the calculation cycles.
Durch die Integration einer Steuerschaltung der Pumpensteuerung in dem Proportionalventil als ein gemeinsames elektromechanisches Bauteil, kann auf eine externe Verdrahtung zu unterschiedlichen Bereichen des Pumpenaufbaus verzichtet werden. Hierdurch kann wiederum die Montage der Kühlmittelpumpe vereinfacht werden und es werden korrosionsempfindliche Steckverbindungen und/oder Austrittsdichtungen am Pumpengehäuse für die Verdrahtung eingespart.By integrating a control circuit of the pump control in the proportional valve as a common electromechanical component, can be dispensed with an external wiring to different areas of the pump structure. In this way, in turn, the assembly of the coolant pump can be simplified and it saves corrosion-sensitive connectors and / or outlet seals on the pump housing for the wiring.
Vorteilhafte Weiterbildungen der erfindungsgemäßen Kühlmittelpumpe sind Gegenstand der abhängigen Ansprüche.Advantageous developments of the coolant pump according to the invention are the subject of the dependent claims.
In einer weiteren Ausführungsform der vorliegenden Erfindung kann der Sensor ein Wegsensor, insbesondere ein Hall-Sensor, sein, der eine Position des Regelschiebers erfasst. In diesem Fall gibt das Sollwert-Signal eine vorbestimmte Position des Regelschiebers, oder einen vorbestimmten Volumenstrom und eine Drehzahl der Verbrennungsmaschine oder der Kühlmittelpumpe an.In a further embodiment of the present invention, the sensor may be a displacement sensor, in particular a Hall sensor, which detects a position of the control slide. In this case, the set value signal indicates a predetermined position of the control valve, or a predetermined volume flow and a rotational speed of the internal combustion engine or the coolant pump.
Falls das Sollwert-Signal von der zentralen Motorsteuerung und das Istwert-Signal des Wegsensors jeweils einen Positionswert des Regelschiebers angeben, lässt sich die Positionsregelung in der Pumpensteuerung mit einer einfachen Berechnungsroutine umsetzen. Dabei können die Rechenkapazitäten der Pumpensteuerung und der Energiebedarf bzw. die resultierende Abwärme in einem gekapselten elektronischen Bauteil niedrig gehalten werden.If the desired value signal from the central engine control and the actual value signal of the displacement sensor each indicate a position value of the control slide, the position control in the pump control can be implemented with a simple calculation routine. The computing capacity of the pump controller and the energy demand or the resulting waste heat in a sealed electronic component can be kept low.
Falls das Sollwert-Signal von der zentralen Motorsteuerung einen vorbestimmten Volumenstrom und eine Drehzahl angibt, erfolgt eine Berechnungsroutine zwischen einem Volumenstrom und einer in Abhängigkeit der Pumpendrehzahl zu regelnden Position des Regelschiebers seitens der Pumpensteuerung. Dadurch kann in der zentralen Motorsteuerung eine spezifische Berechnung anhand von individuellen Parametern der eingesetzten Kühlmittelpumpe entfallen. Die zentrale Motorsteuerung überträgt dann als Sollwert-Signal lediglich einen Wert, der einem Volumenstrom, d.h. einer abzuführenden Wärmemenge entspricht. Der erforderliche Wärmeaustrag ist von der zentralen Motorsteuerung aus den Betriebsparametern der Verbrennungsmaschine berechenbar. Somit kann eine gute Kompatibilität und Austauschbarkeit zwischen der erfindungsgemäßen Kühlmittelpumpe und unterschiedlichen zentralen Motorsteuerungen sichergestellt werden.If the setpoint signal from the central engine control indicates a predetermined volumetric flow and a rotational speed, a calculation routine takes place between a volumetric flow and a position of the control spool to be regulated as a function of the pump rotational speed by the pump control. As a result, a specific calculation based on individual parameters of the coolant pump used can be dispensed with in the central engine control. The central motor control then transmits as a setpoint signal only a value corresponding to a volume flow, ie a quantity of heat to be dissipated. The required heat output is from the central Engine control calculable from the operating parameters of the internal combustion engine. Thus, a good compatibility and interchangeability between the coolant pump of the invention and different central engine controls can be ensured.
Gemäß einer Ausführungsform der vorliegenden Erfindung kann die Pumpensteuerung in einem oberen Bereich der Pumpendrehzahl einen Weg des Regelschiebers begrenzen. Die Pumpensteuerung führt hierdurch eine Schutzfunktion für Bauteile wie z.B. Dichtungen im Kühlsystem aus, um einen maximalen Volumenstrom und den daraus resultierenden Druck zu begrenzen.According to an embodiment of the present invention, the pump controller may limit a travel of the control spool in an upper range of the pump speed. The pump control thereby provides a protective function for components such as e.g. Seals in the cooling system to limit a maximum flow and the resulting pressure.
Gemäß einer Ausfuhrungsform der vorliegenden Erfindung kann ferner die Pumpensteuerung ein Verhältnis zwischen einer Ansteuerungsdauer des Proportionalventils und einer resultierenden Positionsänderung des Regelschiebers mit einem Schwellwert vergleichen. Auf diese Weise führt die Pumpensteuerung eine autonome Funktionsüberwachung zur Sicherstellung einer ausreichenden Füllmenge des Kühlsystems mit Kühlmittel aus.Further, according to an embodiment of the present invention, the pump controller may compare a ratio between a driving duration of the proportional valve and a resultant positional change of the control spool to a threshold value. In this way, the pump control performs an autonomous function monitoring to ensure a sufficient charge of the cooling system with coolant.
Da hierbei der vorhandene hydraulische Kreislauf als druckempfindlicher Messgeber genutzt wird, kann die Funktionsüberwachung zur frühzeitigen Erkennung einer Leckage ohne die Bereitstellung weiterer Messglieder, wie Druckmesser oder sonstigen Sensoren, im Kühlsystem realisiert werden. Dadurch können die Anzahl der Bauteile und Verdrahtungen sowie die Kosten und der Installationsaufwand niedrig gehalten werden.Since the existing hydraulic circuit is used here as a pressure-sensitive sensor, the function monitoring for the early detection of a leak without the provision of additional measuring elements, such as pressure gauges or other sensors, can be realized in the cooling system. As a result, the number of components and wiring and the cost and installation costs can be kept low.
In einer alternativen Ausführungsform der vorliegenden Erfindung kann der Sensor ein Drucksensor sein, der einen Druck des geförderten Volumenstroms des Kühlmittels erfasst. In diesem Fall gibt das Sollwert-Signal einen vorbestimmten Volumenstrom oder einen Druck an, der für den Volumenstrom des geförderten Kühlmittels bezeichnend ist. Der Drucksensor kann vorzugsweise einen Druck in der Pumpenkammer erfassen, der im Verhältnis zu dem geförderten Volumenstrom der Kühlmittelpumpe steht.In an alternative embodiment of the present invention, the sensor may be a pressure sensor that detects a pressure of the delivered volume flow of the coolant. In this case, the setpoint signal indicates a predetermined volume flow or pressure indicative of the volume flow of the delivered coolant. The pressure sensor may preferably detect a pressure in the pump chamber, which is in relation to the delivered volume flow of the coolant pump.
Gemäß einer Ausführungsform der vorliegenden Erfindung kann die Pumpensteuerung den erfassten Druck des Sensors mit einem Schwellwert vergleichen. Auf diese Weise kann die Pumpensteuerung der alternativen Ausführungsform mit einem Drucksensor eine autonome Funktionsüberwachung zur Sicherstellung einer ausreichenden Füllmenge des Kühlsystems mit Kühlmittel besonders einfach ausführen.According to an embodiment of the present invention, the pump controller may compare the sensed pressure of the sensor to a threshold. In this way, the pump control of the alternative embodiment with a pressure sensor can perform an autonomous function monitoring to ensure a sufficient filling amount of the cooling system with coolant particularly easy.
Die Funktionsüberwachung zur frühzeitigen Erkennung einer Leckage kann auch bei dieser Ausführungsform ohne die Bereitstellung weiterer Messglieder im Kühlsystem realisiert werden, wodurch die Anzahl der Bauteile und Verdrahtungen sowie die Kosten und der Installationsaufwand niedrig gehalten werden können.The function monitoring for the early detection of a leak can also be realized in this embodiment without the provision of further measuring elements in the cooling system, whereby the number of components and wiring and the cost and installation costs can be kept low.
Gemäß einer Ausführungsform der vorliegenden Erfindung kann die Pumpensteuerung einen Sendeempfänger zum Empfangen von Daten aus der zentralen Motorsteuerung und / oder Senden von Daten an dieselbe, einen Mikrocomputer zum Ausführen einer Regelungsroutine, einen Ventiltreiber zum Ansteuern des Proportionalventils und einen Leistungszufuhrverteiler zu deren jeweiliger Versorgung mit einer elektrischer Leistung umfassen. Mit diesem Aufbau lässt sich eine Steuerungsschaltung der Pumpensteuerung mit kleinen Abmessungen und vorteilhafter Montagemöglichkeiten an der Kühlmittelpumpe realisieren.According to an embodiment of the present invention, the pump controller may include a transceiver for receiving data from the central engine controller and / or sending data thereto, a microcomputer for executing a control routine, a valve driver for driving the proportional valve, and a power supply manifold for supplying them respectively include electrical power. With this structure, a control circuit of the pump controller can be realized with small dimensions and advantageous mounting options on the coolant pump.
Gemäß einer Ausführungsform der vorliegenden Erfindung kann die Pumpensteuerung ein eigenes Gehäuse aufweisen, das in dem gemeinsamen elektromechanischen Bauteil integriert ist. Durch diesen Aufbau lässt sich beispielsweise elektromagnetische Störstrahlung ausgehend von dem im elektromechanischen Bauteil angeordneten Proportionalventil, insbesondere mit einem magnetisch betätigten Ventil, gegenüber der Steuerschaltung der Pumpensteuerung wirksam abschirmen.According to an embodiment of the present invention, the pump controller may have its own housing integrated in the common electromechanical component. By virtue of this structure, electromagnetic interference radiation, for example, can be effectively shielded from the control circuit of the pump control, starting from the proportional valve arranged in the electromechanical component, in particular with a magnetically actuated valve.
Gemäß einer Ausführungsform der vorliegenden Erfindung kann das Proportionalventil ein eigenes Gehäuse aufweisen, das mit dem gemeinsamen elektromechanischen Bauteil 20 integriert ist. Durch diesen Aufbau lässt sich ebenfalls eine elektromagnetische Störstrahlung ausgehend von einer magnetischen Betätigung des Proportionalventils gegenüber der Steuerschaltung der Pumpensteuerung wirksam abschirmen.According to one embodiment of the present invention, the proportional valve may have its own housing, which is integrated with the common
Gemäß einer Ausführungsform der vorliegenden Erfindung kann das zu fördernde Kühlmittel durch einen Kühlmitteleinlass axial gerichtet auf das Flügelrad anströmen und vom Flügelrad gefördert über einen radial gerichteten Kühlmittelauslass die Pumpenkammer verlassen. Somit wird die Erfindung an dem Aufbau einer Radialpumpe angewendet.According to one embodiment of the present invention, the coolant to be conveyed can flow axially directed onto the impeller through a coolant inlet and out of the pump chamber via a radially directed coolant outlet, conveyed by the impeller. Thus, the invention is applied to the construction of a radial pump.
Gemäß einer Ausführungsform der vorliegenden Erfindung kann das zu fördernde Kühlmittel durch einen Kühlmitteleinlass axial gerichtet auf das Flügelrad anströmen und vom Flügelrad gefördert über einen axial oder halbaxial gerichteten Kühlmittelauslass auf der gegenüberliegenden Seite des Flügelrads die Pumpenkammer verlassen. Somit wird die Erfindung an dem Aufbau einer Axialpumpe oder einer Halbaxialpumpe angewendet.According to an embodiment of the present invention, the coolant to be conveyed can flow axially directed onto the impeller through a coolant inlet and out of the pump chamber via an axially or semi-axially directed coolant outlet on the opposite side of the impeller. Thus, the invention is applied to the structure of an axial pump or a Halbaxialpumpe.
Ein erfindungsgemäßes elektronisches Bauteil der Kühlmittelpumpe wird als gemeinsames elektromechanisches Bauteil aus der Pumpensteuerung und dem Proportionalventil der Kühlmittelpumpe gebildet.An inventive electronic component of the coolant pump is formed as a common electromechanical component of the pump control and the proportional valve of the coolant pump.
Ein erfindungsgemäßes Verfahren zum Steuern der erfindungsgemäßen mechanisch angetriebenen Kühlmittelpumpe eines Fahrzeugs mit einem Verbrennungsmotor und einer zentralen Motorsteuerung weist in einer ersten Alternative die folgenden Schritte auf: Berechnen eines Sollwerts eines Parameters, der für den Volumenstrom des geförderten Kühlmittels bezeichnend ist, in Abhängigkeit von Betriebsparametern des Verbrennungsmotors durch die zentrale Motorsteuerung; Übertragen des Sollwerts von der zentralen Motorsteuerung zu einer Pumpensteuerung der Kühlmittelpumpe; Erfassen eines Istwerts des Parameters durch einen Sensor; Übertragen des Istwerts von dem Sensor zu der Pumpensteuerung; und Einregeln einer Position eines Regelschiebers, der den geförderten Volumenstrom der Kühlmittelpumpe begrenzt, in Abhängigkeit von dem Sollwert und dem Istwert durch die Pumpensteuerung, mittels Ansteuerung eines hydraulischen Stellglieds. Auf diese Weise wird die Erfindung an einer Kühlmittelpumpe der genannten Ausführungsformen angewendet.A method according to the invention for controlling the mechanically driven coolant pump of a vehicle according to the invention with an internal combustion engine and a central engine control comprises, in a first alternative, the following steps: calculating a desired value of a parameter indicative of the volume flow of the delivered coolant as a function of operating parameters Internal combustion engine through the central engine control; Transmitting the setpoint from the central engine controller to a pump controller of the coolant pump; Detecting an actual value of the parameter by a sensor; Transferring the actual value from the sensor to the pump controller; and adjusting a position of a control slide, which limits the delivered volume flow of the coolant pump, as a function of the desired value and the actual value by the pump control, by means of control of a hydraulic actuator. In this way the invention is applied to a coolant pump of said embodiments.
Das erfindungsgemäße Verfahren zum Steuern der erfindungsgemäßen mechanisch angetriebenen Kühlmittelpumpe eines Fahrzeugs mit einem Verbrennungsmotor und einer zentralen Motorsteuerung weist in einer zweiten Alternative die folgenden Schritte auf: Übertragen von Betriebsparametern des Verbrennungsmotors von der zentralen Motorsteuerung zu einer Pumpensteuerung der Kühlmittelpumpe; Berechnen eines Sollwerts eines Parameters, der für den Volumenstrom des geförderten Kühlmittels bezeichnend ist, in Abhängigkeit von den Betriebsparametern des Verbrennungsmotors durch die Pumpensteuerung; Erfassen eines Istwerts des Parameters durch einen Sensor; Übertragen des Istwerts von dem Sensor zu der Pumpensteuerung; und Einregeln einer Position eines Regelschiebers, der den geförderten Volumenstrom der Kühlmittelpumpe begrenzt, in Abhängigkeit von dem Sollwert und dem Istwert durch die Pumpensteuerung, mittels Ansteuerung eines hydraulischen Stellglieds. Auf diese alternative Weise wird die Erfindung an einer Kühlmittelpumpe der genannten Ausführungsformen angewendet.The inventive method for controlling the mechanically driven coolant pump according to the invention of a vehicle with an internal combustion engine and a central engine control comprises in a second alternative the following steps: transferring operating parameters of the internal combustion engine from the central engine control to a pump control of the coolant pump; Calculating a setpoint value of a parameter indicative of the volume flow of the delivered coolant as a function of the operating parameters of the internal combustion engine by the pump controller; Detecting an actual value of the parameter by a sensor; Transferring the actual value from the sensor to the pump controller; and adjusting a position of a control slide, which limits the delivered volume flow of the coolant pump, as a function of the desired value and the actual value by the pump control, by means of control of a hydraulic actuator. In this alternative manner, the invention is applied to a coolant pump of said embodiments.
Gemäß einer Ausführungsform der vorliegenden Erfindung kann der Parameter, der für den Volumenstrom des geförderten Kühlmittels bezeichnend ist, eine Position des Regelschiebers sein. Hierdurch kann das Steuerungsverfahren an dem eingangs genannten Aufbau der erfindungsgemäßen Kühlmittelpumpe angewendet werden.According to an embodiment of the present invention, the parameter indicative of the volume flow of the delivered coolant may be a position of the control spool. As a result, the control method can be applied to the structure of the coolant pump according to the invention mentioned above.
Gemäß einer Ausführungsform der vorliegenden Erfindung kann der Parameter, der für den Volumenstrom des geförderten Kühlmittels bezeichnend ist, ein Druck in einer Pumpenkammer der Kühlmittelpumpe sein, der dem Volumenstrom des geförderten Kühlmittels entspricht. Hierdurch kann das Steuerungsverfahren an einer alternativen Ausfuhrungsform der erfindungsgemäßen Kühlmittelpumpe angewendet werden.According to an embodiment of the present invention, the parameter indicative of the volume flow of the delivered coolant may be a pressure in a pump chamber of the coolant pump corresponding to the volume flow of the pumped Coolant corresponds. As a result, the control method can be applied to an alternative embodiment of the coolant pump according to the invention.
Die Erfindung wird nachfolgend in einem Ausfuhrungsbeispiel anhand der Figuren näher erläutert. Es zeigt:
- Fig.1
- eine schematische Schnittansicht eines inneren Bereichs der Kühlmittelpumpe und einer Verdrahtung der Pumpensteuerung gemäß der vorliegenden Erfindung;
- Fig. 2
- eine Schnittansicht eines Aufbaus einer Kühlmittelpumpe mit einer Pumpensteuerung gemäß der vorliegenden Erfindung, die mit einem Stecker zur Verbindung mit einem Datenbus ausgestattet ist;
- Fig. 3A
- eine Schnittansicht eines elektromechanischen Bauteils aus
Fig. 1 , bei dem eine Pumpensteuerung in einem Proportionalventil integriert ist; - Fig. 3B
- eine Schnittansicht eines elektromechanischen Bauteils aus
Fig. 2 , bei dem eine Pumpensteuerung und ein Proportionalventil miteinander integriert sind; - Fig. 4
- ein schematisches Blockdiagramm der Pumpensteuerung gemäß der vorliegenden Erfindung.
- Fig.1
- a schematic sectional view of an inner portion of the coolant pump and a wiring of the pump controller according to the present invention;
- Fig. 2
- a sectional view of a structure of a coolant pump with a pump controller according to the present invention, which is equipped with a plug for connection to a data bus;
- Fig. 3A
- a sectional view of an electromechanical component
Fig. 1 in which a pump control is integrated in a proportional valve; - Fig. 3B
- a sectional view of an electromechanical component
Fig. 2 in which a pump control and a proportional valve are integrated with each other; - Fig. 4
- a schematic block diagram of the pump control according to the present invention.
Nachfolgend wird ein beispielhafter Aufbau der Kühlmittelpumpe mit Bezug auf
Die Kühlmittelpumpe weist ein Pumpengehäuse 1 und eine darin drehbar gelagerte Pumpenwelle 4 mit einer Riemenscheibe 3 auf, die mittels eines Riementriebs von einem Verbrennungsmotor (nicht dargestellt) angetrieben wird. An einem freien Ende der Pumpenwelle 4 ist ein Flügelrad 5 drehfest angeordnet, das innerhalb einer Pumpenkammer 2 in einem Strömungsbereich eines Kühlkreislaufs des Verbrennungsmotors eingebracht ist, um einen Volumenstrom des Kühlmittels zu bewirken. Das Kühlmittel wird durch einen axialen Einlass der Pumpenkammer 2, im Bereich eines mittleren Radius des Flügelrads 5, angesaugt und beispielsweise durch einen radialen Auslass (nicht dargestellt) der Pumpenkammer 2, der einem Umfangsbereich des Flügelrads 5 gegenüberliegt, ausgestoßen.The coolant pump has a pump housing 1 and a pump shaft 4 rotatably mounted therein with a pulley 3, which is driven by a belt drive by an internal combustion engine (not shown). At a free end of the pump shaft 4, an
Der Strömungsbereich des Flügelrads 5 kann von einem Regelschieber 7 mit einem koaxial zur Pumpenwelle angeordneten zylindrischen Abschnitt 7a und einem Rückwandabschnitt 7b entlang eines parallel zur Pumpenwelle 4 verlaufenden Verstellwegs variabel überdeckt werden. Zwischen der inneren Umfangswand des zylindrischen Abschnitt 7a des Regelschiebers 7 und einer rückwärtigen Wand der Pumpenkammer 2 verläuft eine Dichtungslippe 6. In
In der Pumpenkammer 2 ist ferner zur Rückseite des Flügelrads 5 und parallel zur Pumpenwelle 4 eine Axialkolbenpumpe 9 angeordnet, deren Kolben über einen Gleitschuh betätigt wird, der auf einer Taumelscheibe 8 gleitet, die auf der rückwärtigen Seite des Flügelrads 5 gemeinsam mit diesem drehfest zur Pumpenwelle 4 angeordnet ist.In the
Die Axialkolbenpumpe 9 saugt Kühlmittel aus dem Strömungsbereich in der Pumpenkammer 2 zwischen dem Flügelrad 5 und dem Regelschieber 7 an und stößt das Kühlmittel unter Druck in einen hydraulischen Kreislauf 11 aus, der in dem Pumpengehäuse 1 ausgebildet ist. Der hydraulische Kreislauf 11 verzweigt sich in zwei Zweige 11a und 11b. Der eine Zweig 11a des hydraulischen Kreislaufs 11 führt einerseits zu einem elektromagnetischen Proportionalventil 13 und wieder zurück in den geförderten Kühlmittelstrom. Der andere Zweig 11b des hydraulischen Kreislaufs 11 führt zu einem Ringkolben 15, der koaxial zu der Pumpenwelle 4 angeordnet ist und die Funktion eines hydraulischen Stellglieds entlang des Verstellwegs des Regelschiebers 7 übernimmt.The
Eine Rückstellfeder 17 beaufschlagt den Ringkolben 15 in entgegengesetzter Richtung zu dem Druck des hydraulischen Kreislaufs 11, d.h. hinweg von dem Flügelrad 5. Der Ringkolben 15 steht mit dem Regelschieber 7 in Verbindung und verschiebt diesen mit zunehmendem Druck des hydraulischen Kreislaufs 11 in Richtung des Flügelrads 5.A
Nachfolgend wird eine beispielhafte Funktionsweise zur Einstellung des Volumenstroms der Kühlmittelpumpe beschrieben.An exemplary mode of operation for adjusting the volume flow of the coolant pump will be described below.
Das elektromagnetische Proportionalventil 13 ist ohne Zuführung eines Ansteuerstroms geöffnet, sodass das von der Axialkolbenpumpe 9 angesaugte Kühlmittel im Wesentlichen drucklos über den Zweig 11a des hydraulischen Kreislaufs 11 durch das Proportionalventil 13 hindurch zurück in den geförderten Kühlmittelstrom zurückfließt. Somit baut sich in dem Zweig 11b des hydraulischen Kreislaufs 11 kein Druck auf und der Ringkolben 15 verbleibt unter Beaufschlagung der Rückstellfeder 17 in einer unbetätigten Grundstellung. Der Regelschieber 7, der mit dem Ringkolben 15 in Verbindung steht, wird dabei in der "offenen Position" gehalten, wie in
In der "offenen Position" des Regelschiebers wird, ohne Berücksichtigung der Pumpendrehzahl, ein maximal geförderter Volumenstrom ohne Abschirmung eines strömungswirksamen Bereichs des Flügelrads 5 durch den Regelschieber 7 hergestellt. Dieser Zustand stellt zugleich einen Fail-Safe Modus dar, sodass im Falle eines Ausfalls einer Stromzufuhr oder eines Defekts der Ansteuerung, d.h. eines stromlosen elektromagnetischen Proportionalventils 13, automatisch ein maximaler Volumenstrom und ein größtmöglicher Wärmeaustrag am Verbrennungsmotor sichergestellt sind.In the "open position" of the control slide, without taking into account the pump speed, a maximum delivered volume flow without shielding a flow-effective area of the
Wenn das elektromagnetische Proportionalventil 13 durch eine zeitlich geregelte Zuführung eines Ansteuerstroms zeitweise geschlossen wird, kann das von der Axialkolbenpumpe 9 ausgestoßene Kühlmittel nicht über den Zweig 11a des hydraulischen Kreislaufs 11 in den Volumenstrom zurückfließen. Der von der Axialkolbenpumpe 9 aufgewendete Druck im hydraulischen Kreislauf 11 breitet sich von dem Rückstau am geschlossenen Proportionalventil 13 über den Zweig 11a in den Zweig 11b aus und wirkt auf den Ringkolben 15. Der Ringkolben 15 verschiebt den Regelschieber 7 gegen die Kraft der Rückstellfeder 17 zu dem Flügelrad. Dabei wird der zylindrische Abschnitt 7a des Regelschiebers 7 zunehmend in axiale Überschneidung mit dem Flügelrad 5 gebracht, wodurch ein wirksamer Strömungsbereich des Flügelrads 5 durch den zylindrischen Abschnitt 7a des Regelschiebers 7 radial überdeckt wird.When the electromagnetic
In einer "geschlossenen Position" des Regelschiebers 7 überdeckt der zylindrische Abschnitt 7a das Flügelrad 5 vollständig, sodass, ohne Berücksichtigung der Pumpendrehzahl, ein minimaler geförderter Volumenstrom durch volle Abschirmung eines strömungswirksamen Bereichs des Flügelrads 5 durch den Regelschieber 7 hergestellt wird.In a "closed position" of the control slide 7, the
Durch die Steuerung der Ein- und Ausschaltdauern des elektromagnetischen Proportionalventils 13 wird ein kontrollierter Rückstau im Zweig 11a und somit ein kontrollierter Druck im Zweig 11b des hydraulischen Kreislaufs 11 aufgebaut, der auf den Ringkolben 15 und entgegen der Rückstellfeder 17 wirkt. Der Ringkolben 15 verschiebt den Regelschieber 7 zur Einstellung des geförderten Volumenstroms der Kühlmittelpumpe zwischen der obenstehend beschriebenen "offenen Position" und "geschlossenen Position".By controlling the on and off periods of the electromagnetic proportional valve 13 a controlled back pressure in the
Die zentrale Motorsteuerung ZMS berechnet unter Berücksichtigung verschiedener Betriebsparameter, wie z.B. einer Drehzahl und Arbeitsbelastung des Verbrennungsmotors, einer Kraftstoffzufuhr, einer Temperatur, einer Fahrzeuggeschwindigkeit oder dergleichen, einen zu fördernden Volumenstrom des Kühlmittels, der einem erforderlichen Wärmeaustrag des Verbrennungsmotors entspricht.The central engine control ZMS calculates taking into account various operating parameters, e.g. a speed and work load of the internal combustion engine, a fuel supply, a temperature, a vehicle speed or the like, a volume flow of the coolant to be delivered, which corresponds to a required heat output of the internal combustion engine.
Wie obenstehend beschrieben ist, hängt ein von der Kühlmittelpumpe geförderter Volumenstrom des Kühlmittels einerseits von der Strömungswirksamkeit des Flügelrads 5 ab, die bei zunehmender axialer Verschiebung der Position des Regelschiebers 7 (und des Ringskolbens 15) in Richtung der "geschlossenen Position" mit einem steigenden Grad der Überdeckung durch den zylindrischen Abschnitt 7a des Regelschiebers 7 um das Flügelrad 5 abnimmt.As described above, on the one hand, a volume flow of the coolant conveyed by the coolant pump depends on the flow efficiency of the
Andererseits hängt der geförderte Volumenstrom der Kühlmittelpumpe von der Pumpendrehzahl ab. Die Pumpendrehzahl ist mittels des Riementriebs durch die Drehzahl der Verbrennungsmaschine zwangsweise vorgegeben und umfasst die für den Fahrzeugbetrieb charakteristischen Schwankungen.On the other hand, the delivered volume flow of the coolant pump depends on the pump speed. The pump speed is forcibly determined by means of the belt drive by the speed of the internal combustion engine and includes the characteristic of vehicle operation fluctuations.
Nachfolgend wird ein beispielhafter Aufbau der Pumpensteuerung 21 mit Bezug auf
Die Pumpensteuerung 21 umfasst in einer beispielgebenden Ausführungsform einen Sendeempfänger 23, wie z.B. einen LIN-Transceiver, einen Mikrocomputer 25, einen Ventiltreiber 27 und einen Leistungszufuhrverteiler 29. Der Leistungszufuhrverteiler teilt die Spannung einer Leistungsquelle des Fahrzeug (nicht dargestellt) von beispielsweise 12V in geeignete Spannungen der elektronischen Komponenten 23, 25, 27 der Pumpensteuerung 21 auf und versorgt diese mit der erforderlichen elektrischen Leistung. Der LIN-Transceiver 23 ermöglicht eine Kommunikation von Daten über einen Datenbus, z.B. im LIN-Protokoll, zwischen der Pumpensteuerung 21 und der zentralen Motorsteuerung ZMS. Wie in
Bei einer in
Wenn das Gehäuse des Proportionalventils, wie in
Anderenfalls kann die Pumpensteuerung 21 an einem äußeren Bereich des Gehäuses des Proportionalventils 13 integriert sein, wie in
Unterschiedliche Formen und Anordnungen zur Integration der Pumpensteuerung 21 und des Proportionalventils 13 ergeben sich ferner durch die Ausführung des verwendeten Ventiltyps. Anstelle des elektromagnetischen Proportionalventils 13 kann ebenso ein elektromotorisch betätigtes Proportionalventil 13 verwendet werden, das mit der Pumpensteuerung 21 ein gemeinsames elektromechanisches Bauteil bildet. In diesem Fall muss das Ansteuersignal für einen Stellmotor keine Pulsweitenmodulation enthalten.Various forms and arrangements for the integration of the
Der gezeigte Aufbau lässt sich vorzugsweise mit einem Hall-Sensor als Wegsensor 19 realisieren. Allerdings ist diese Ausführungsform nicht auf einen Hall-Sensor beschränkt, wie in einer weiteren Ausführungsform später beschrieben wird.The structure shown can preferably be realized with a Hall sensor as a
Bei einer Ausführungsform der in
In einer beispielhaften Ausführungsform enthält das Sollwert-Signal, das die Pumpensteuerung 21 von der zentralen Motorsteuerung ZMS empfängt, eine vorbestimmte Position des Regelschiebers 7. Hierzu berechnet die zentrale Motorsteuerung ZMS basierend auf einem dem erforderlichen Wärmeaustrag des Verbrennungsmotors einen von der Kühlmittelpumpe zu fördernden Volumenstrom des Kühlmittels. Die vorgebestimmte Position des Regelschiebers wird anschließend in Abhängigkeit des Volumenstroms und einer derzeitigen Pumpendrehzahl, die in einem festen Drehzahlverhältnis zu dem Verbrennungsmotor steht, berechnet und an die Pumpensteuerung 21 übertragen.In an exemplary embodiment, the setpoint signal, which receives the
In einer weiteren beispielhaften Ausführungsform enthält das Sollwertsignal, das die Pumpensteuerung 21 von der zentralen Motorsteuerung ZMS empfängt, lediglich einen Sollwert für einen erforderlichen Volumenstrom des Kühlmittels und weitere Betriebsparameter, wie insbesondere eine derzeitige Drehzahl der Verbrennungsmaschine oder die entsprechende Pumpendrehzahl. Die Berechnung eines Sollwerts für die resultierende Position des Regelschiebers 7 erfolgt bei dieser Ausführungsform in der Pumpensteuerung 21.In another exemplary embodiment, the setpoint signal received by the
Die Regelungsroutine, die in dem Mikrocomputer 25 ausgeführt wird, entspricht beispielsweise der Regelungsfunktion eines PID-Glieds, bei der zwischen dem vorgegebenen Sollwert und dem Istwert eine Regelabweichung berechnet wird. Aus der Regelabweichung wird basierend auf einer systemspezifischen Funktion des hydraulischen Kreislaufs 11, d.h. einem Reaktionsverhalten zwischen einer Ein- und Ausschaltdauer des elektromagnetischen Proportionalventil 13 und einer resultierenden Positionsänderung des Ringkolbens 15 als hydraulisches Stellglied, eine Pulsweitenmodulation zur Ansteuerung des elektromagnetischen Proportionalventils 13 berechnet.The control routine executed in the
Zum Einhalten einer Position des Regelschiebers 7 wird der Druck im hydraulischen Kreislauf 11 durch die Ein- und Ausschaltdauern zum Öffnen- und Schließen des Proportionalventils 13 derart gesteuert, dass ein Gleichgewicht zwischen dem hydraulischen Druck und dem Druck der Rückstellfeder 17 in einer Position des Ringkolbens 15 bzw. des Regelschiebers 7 erzielt und gehalten wird, die dem vorgegebenen Sollwert der zentralen Motorsteuerung ZMS entspricht. Die tatsächliche Position des Regelschiebers 7 wird wiederum von dem Wegsensor 19 erfasst und als Rückkopplung zur Ansteuerung des Proportionalventils 13 an die Pumpensteuerung 21 übertragen bzw. in den Mikrocomputer 25 eingegeben.To maintain a position of the control slide 7, the pressure in the
Gemäß einer weiteren beispielhaften Ausfuhrungsform führt die Pumpensteuerung 21 eine Funktionsüberwachung durch, um eine Leckage im Kühlsystem selbstständig zu erkennen und an die zentrale Motorsteuerung zu melden.According to a further exemplary embodiment, the
Wenn sich durch eine Leckage Lufteinschlüsse im Kühlmittelkreislauf gebildet haben, gelangen diese auch in den hydraulischen Kreislauf 11 der Kühlmittelpumpe und mindern den Druck in dem hydraulischen Stellglied. Die Kennlinie der Rückstellfeder 17, die dem Ringkolben 15 entgegenwirkt, bleibt unverändert. Das Ungleichgewicht zwischen dem verminderten hydraulischen Druck und der unveränderten Kennlinie der Rückstellfeder 17 muss in diesem Fall dahingehend kompensiert werden, dass das Verhältnis der Einschaltzeit zur Ausschaltzeiten des elektromagnetischen Proportionalventils 13 erhöht wird, um den hydraulischen Druck für die gewünschte Position des Ringkolbens 15 zu erzeugen.If air pockets in the coolant circuit have formed due to leakage, they also enter the
Aufgrund der einfachen Regelungsschleife zwischen dem Wegsensor 19 des Regelschiebers 7 und dem elektromagnetischen Proportionalitätsventil 13 im hydraulischen Kreislauf 11 kann die erfindungsgemäße Pumpensteuerung 21 Abweichungen im Reaktionsverhalten des hydraulischen Kreislaufs mit der erforderlichen Sensibilität, d.h. insbesondere ohne Einflüsse weiterer Betriebsparameter wie permanente Schwankungen von Drehzahl und Temperatur erfassen. Die Pumpensteuerung 21 vergleicht eine Abweichung des Verhältnisses zwischen den Ein- und Ausschaltdauem des elektromagnetischen Proportionalventils 13 und der resultierenden Positionsänderung des Ringkolbens 15 bzw. Regelschiebers 7 mit einem in dem Speicher hinterlegten Schwellwert. Der Schwellwert ist ebenso wie übrige spezifische Parameter der Kühlmittelpumpe in einem Speicherabschnitt der Pumpensteuerung 21 hinterlegt.Due to the simple control loop between the
Im Falle einer Fehlererkennung gibt die Pumpensteuerung 21 eine Fehlermeldung an die zentrale Motorsteuerung aus, die wiederum einen eingeschränkten Notbetrieb oder eine Abschaltung der Verbrennungsmaschine einleiten kann.In the case of fault detection, the
In einer alternativen beispielhaften Ausführungsform weist die Kühlmittelpumpe anstelle eines Wegsensors 19 einen Drucksensor (nicht dargestellt) auf, der vorzugsweise zwischen dem Ringkolben 15 und dem Regelschieber 7 angeordnet ist.In an alternative exemplary embodiment, the coolant pump has a pressure sensor (not shown) instead of a
Bei dieser alternativen Ausführungsform führt die Pumpensteuerung 21 eine Regelung dahingehend durch, dass der Regelschieber 7 zur Einstellung des Volumenstroms in eine neue Position verschoben wird, bis das Istwert-Signal des erfassten Drucks des Drucksensors einem Druck des vorbestimmten Volumenstroms entspricht, der durch das Sollwert-Signal von der zentralen Motorsteuerung ZMS vorgegeben ist.In this alternative embodiment, the
Bei dieser Ausführungsform kann eine Funktionsüberwachung des Kühlsystems einfach über den vorhandenen Drucksensor anstatt über das Reaktionsverhalten des hydraulischen Stellglieds wahrgenommen werden. Wie zu der vorhergehenden Ausführungsform beschrieben wurde, ist ein Schwellwert in einem Speicherabschnitt der Pumpensteuerung hinterlegt. Dieser Schwellwert entspricht einem minimalen Betriebsdruck, der insbesondere bei der Bildung von Lufteinschlüssen im Kühlsystem unterschritten wird. Nach einem Vergleich des Sollwerts mit dem erfassten Druck des Drucksensors beurteilt die Pumpensteuerung 21, ob eine Leckage im Kühlsystem vorliegt.In this embodiment, a function monitoring of the cooling system can be easily perceived via the existing pressure sensor rather than via the reaction behavior of the hydraulic actuator. As described in the previous embodiment, a threshold value is stored in a storage section of the pump controller. This threshold corresponds to a minimum operating pressure, which falls below in particular in the formation of trapped air in the cooling system. After a comparison of the desired value with the detected pressure of the pressure sensor, the
Im Falle einer Fehlererkennung gibt die Pumpensteuerung 21 eine Fehlermeldung an die zentrale Motorsteuerung ZMS aus, die wiederum einen eingeschränkten Notbetrieb oder eine Abschaltung der Verbrennungsmaschine einleiten kann.In the case of fault detection, the
Ferner kann anstelle einer LIN-Schnittstelle eine CAN-Schnittstelle zwischen der Pumpensteuerung 21 und der zentralen Motorsteuerung ZMS vorgesehen sein.Furthermore, instead of a LIN interface, a CAN interface can be provided between the
Claims (15)
- A coolant pump configured to pump a coolant for an internal combustion engine in a vehicle comprising the internal combustion engine and a central engine control unit, said coolant pump comprising:a pump shaft (4) which is rotatably mounted in a pump housing (1) and driven by the internal combustion engine via a belt drive (3),an impeller (5) which is arranged on the pump shaft (4) and accommodated in a pump chamber (2) of the pump housing (1), pumping the coolant,an axial piston pump (9) which is actuated via a wobble plate (8) on a rear side of the impeller (5) and which branches-off a fraction of the pumped coolant,a hydraulic circuit (11) which extends from the axial piston pump (9) via a proportional valve (13) back to the pumped coolant and which includes a branch (11b) between the axial piston pump (9) and the proportional valve (13) as a hydraulic actuator,a regulating slide valve (7) which adjusts the volume flow of the coolant pumped by the coolant pump and which is slidable depending on a pressure in the hydraulic circuit (11),a sensor (19) which detects a parameter indicative of the volume flow of the pumped coolant and which outputs an actual value signal of the parameter, andcharacterized bya dedicated pump control (21) which controls the proportional valve (13) in the hydraulic circuit (11) on the basis of the actual value signal from the sensor (19) and a desired value signal from the central engine control unit, andwherein the pump control (21) and the proportional valve (13) are formed as a mutual electromechanical component (20).
- The coolant pump according to claim 1, wherein the sensor (19) is a position sensor which detects a position of the regulating slide valve (7), and
the desired value signal indicates i) a predetermined position of the regulating slide valve (7) or ii) a predetermined volume flow and a speed of the internal combustion engine or coolant pump. - The coolant pump according to claim 1 or 2, wherein the pump control (21) limits a path of the regulating slide valve (7) in an upper speed range of the pump.
- The coolant pump according to any one of claims 1 to 3, wherein the pump control (21) compares a relationship between a control duration of the proportional valve (13) and a resulting position change of the regulating slide valve (7) with a threshold value.
- The coolant pump according to any one of claims 1,3 or 4, wherein the sensor (19) is a pressure sensor which detects the pressure of the pumped volume flow of the coolant, and
the desired value signal indicates i) a predetermined volume flow or ii) a pressure which is indicative of the volume flow of the pumped coolant. - The coolant pump according to claim 5, wherein the pump control (21) compares the pressure detected by the sensor (19) with a threshold value.
- The coolant pump according to any one of claims 1 to 6, wherein the pump control (21) comprises a transceiver (23) for receiving data from the central engine control unit and/or for sending data thereto, a microcomputer (25) for performing a control procedure, a valve driver (27) for driving the proportional valve (13), and a power supply distributor (29) for supplying each component with electric power.
- The coolant pump according to any one of claims 1 to 7, wherein the mutual electromechanical component (20) is configured such that the pump control (21) is integrated into a housing of the proportional valve (13).
- The coolant pump according to any one of claims 1 to 7, wherein the mutual electromechanical component (20) is configured such that the pump control (21) has a housing of its own which is integral with a housing of the proportional valve (13).
- The coolant pump according to any one of claims 1 to 9, wherein the coolant to be pumped flows through a coolant inlet axially directed towards the impeller (5) and is pumped by the impeller (5) so as to leave the pump chamber (2) via a radial coolant outlet.
- The coolant pump according to any one of claims 1 to 9, wherein the coolant to be pumped flows through a coolant inlet axially directed towards the impeller (5) and is pumped by the impeller (5) so as to leave the pump chamber (2) via an axial or semi-axial coolant outlet on the opposite side of the impeller (5).
- An electromechanical component (20) of the coolant pump according to any one of claims 1 to 11, formed as a mutual electromechanical component from the pump control (21) and the proportional valve (13) of the coolant pump.
- A method for controlling a mechanically driven coolant pump of a vehicle with an internal combustion engine and a central engine control unit according to any one of claims 1 to 11, said method comprising the steps of:a1) calculating by way of the central engine control unit, a desired value of a parameter, which is indicative of the volume flow of the pumped coolant, depending on operating parameters of the internal combustion engine; and
transmitting the desired value from the central engine control unit to a pump control (21) of the coolant pump;
ora2) transmitting operating parameters of the internal combustion engine from the central engine control unit to a pump control (21) of the coolant pump; and
calculating by way of the pump control (21) a desired value of a parameter, which is indicative of the volume flow of the pumped coolant, depending on the operating parameters of the internal combustion engine;b) detecting an actual value of the parameter by a sensor (19);c) transmitting the actual value from the sensor (19) to the pump control (21); andd) tuning by way of the pump control (21) the position of a regulating slide valve (7), which limits the pumped volume flow of the coolant pump, depending on the desired value and the actual value by controlling a hydraulic actuator (13). - The control method according to claim 13, wherein the parameter which is indicative of the volume flow of the pumped coolant is a position of the regulating slide valve (7).
- The control method according to claim 13, wherein the parameter which is indicative of the volume flow of the pumped coolant is a pressure in a pump chamber (2) of the coolant pump which corresponds to the volume flow of the pumped coolant.
Priority Applications (1)
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PL15738683T PL3172445T3 (en) | 2014-07-21 | 2015-07-17 | Coolant pump with integrated closed-loop control |
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DE102014110231.2A DE102014110231B3 (en) | 2014-07-21 | 2014-07-21 | Coolant pump with integrated control |
DE102015109966.7A DE102015109966B3 (en) | 2015-06-22 | 2015-06-22 | Coolant pump with integrated control |
PCT/EP2015/066473 WO2016012379A1 (en) | 2014-07-21 | 2015-07-17 | Coolant pump with integrated closed-loop control |
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EP3172445B1 true EP3172445B1 (en) | 2019-09-11 |
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EP (1) | EP3172445B1 (en) |
KR (1) | KR101912802B1 (en) |
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DE102011004172B3 (en) | 2011-02-15 | 2012-03-01 | Schwäbische Hüttenwerke Automotive GmbH | Coolant pump with adjustable delivery volume |
CN202117755U (en) | 2011-06-15 | 2012-01-18 | 中国汽车技术研究中心 | Electronic-control auxiliary cooling system of engine insusceptible to rotating speed of engine |
DE102011079310A1 (en) * | 2011-07-18 | 2013-01-24 | Schaeffler Technologies AG & Co. KG | Coolant pump for a coolant circuit of an internal combustion engine |
DE102011079311A1 (en) | 2011-07-18 | 2013-01-24 | Schaeffler Technologies AG & Co. KG | Coolant pump for coolant circulation circuit of internal combustion engine of motor car, has control pump integrated into pump and providing fluid for displacement of locking element, where control pump is designed as rotary pump |
DE102011113040B3 (en) | 2011-09-09 | 2012-04-26 | Geräte- und Pumpenbau GmbH Dr. Eugen Schmidt | Controllable coolant pump for supplying coolant to e.g. cylinder head of internal combustion engine, has outflow opening enclosed by ring seal, which is arranged in chamber rear wall and actively connected with disk in rear end position |
DE102012204044A1 (en) * | 2012-03-15 | 2013-09-19 | Schaeffler Technologies AG & Co. KG | Adjustable coolant pump with a multi-part modular design |
DE102012223069A1 (en) * | 2012-12-13 | 2014-06-18 | Bayerische Motoren Werke Aktiengesellschaft | Coolant circuit for an internal combustion engine |
DE102013011209B3 (en) * | 2013-07-04 | 2014-01-23 | Geräte- und Pumpenbau GmbH Dr. Eugen Schmidt | Controllable coolant pump for internal combustion engine mounted in e.g. truck, has piston rod that is connected with permanent magnet, and linearly moved with respect to solenoid coil |
-
2015
- 2015-07-17 PL PL15738683T patent/PL3172445T3/en unknown
- 2015-07-17 US US15/502,362 patent/US10400659B2/en not_active Expired - Fee Related
- 2015-07-17 WO PCT/EP2015/066473 patent/WO2016012379A1/en active Application Filing
- 2015-07-17 CN CN201580039869.XA patent/CN106536939B/en not_active Expired - Fee Related
- 2015-07-17 KR KR1020177000789A patent/KR101912802B1/en active IP Right Grant
- 2015-07-17 HU HUE15738683A patent/HUE047472T2/en unknown
- 2015-07-17 EP EP15738683.0A patent/EP3172445B1/en not_active Not-in-force
Non-Patent Citations (1)
Title |
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None * |
Also Published As
Publication number | Publication date |
---|---|
KR101912802B1 (en) | 2018-12-28 |
EP3172445A1 (en) | 2017-05-31 |
KR20170018026A (en) | 2017-02-15 |
US20180119596A9 (en) | 2018-05-03 |
US10400659B2 (en) | 2019-09-03 |
US20170254253A1 (en) | 2017-09-07 |
PL3172445T3 (en) | 2020-04-30 |
CN106536939A (en) | 2017-03-22 |
WO2016012379A1 (en) | 2016-01-28 |
HUE047472T2 (en) | 2020-04-28 |
CN106536939B (en) | 2019-09-06 |
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