EP3172446B1 - Kühlmittelpumpe mit integrierter regelung - Google Patents

Kühlmittelpumpe mit integrierter regelung Download PDF

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Publication number
EP3172446B1
EP3172446B1 EP15739275.4A EP15739275A EP3172446B1 EP 3172446 B1 EP3172446 B1 EP 3172446B1 EP 15739275 A EP15739275 A EP 15739275A EP 3172446 B1 EP3172446 B1 EP 3172446B1
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EP
European Patent Office
Prior art keywords
pump
coolant
control
volume flow
pumped
Prior art date
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Active
Application number
EP15739275.4A
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German (de)
English (en)
French (fr)
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EP3172446A1 (de
Inventor
Jens Hoffmann
Franz Pawellek
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Nidec GPM GmbH
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Nidec GPM GmbH
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Publication date
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Publication of EP3172446A1 publication Critical patent/EP3172446A1/de
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D13/00—Pumping installations or systems
    • F04D13/12—Combinations of 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
    • F01P5/00—Pumping cooling-air or liquid coolants
    • F01P5/10—Pumping liquid coolant; Arrangements of coolant pumps
    • F01P5/12—Pump-driving arrangements
    • 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
    • F04B23/00—Pumping installations or systems
    • F04B23/04—Combinations of two or more pumps
    • F04B23/08—Combinations of two or more pumps the pumps being of different types
    • F04B23/14—Combinations of two or more pumps the pumps being of different types at least one pump being of the non-positive-displacement type
    • 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
    • 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
    • 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
    • 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
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/14—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F04B1/141—Details or component parts
    • F04B1/146—Swash plates; Actuating elements
    • 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
    • F04B23/00—Pumping installations or systems
    • F04B23/04—Combinations of two or more pumps
    • F04B23/08—Combinations of two or more pumps the pumps being of different types
    • F04B23/10—Combinations of two or more pumps the pumps being of different types at least one pump being of the reciprocating positive-displacement type
    • 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
    • F04B23/00—Pumping installations or systems
    • F04B23/04—Combinations of two or more pumps
    • F04B23/08—Combinations of two or more pumps the pumps being of different types
    • F04B23/10—Combinations of two or more pumps the pumps being of different types at least one pump being of the reciprocating positive-displacement type
    • F04B23/106—Combinations of two or more pumps the pumps being of different types at least one pump being of the reciprocating positive-displacement type being an axial piston pump
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D15/00—Control, e.g. regulation, of pumps, pumping installations or systems
    • F04D15/0027—Varying behaviour or the very pump
    • F04D15/0038—Varying behaviour or the very pump by varying the effective cross-sectional area of flow through the rotor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • 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
    • 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
    • F01P2025/04—Pressure
    • F01P2025/06—Pressure for determining flow
    • 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
    • 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
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/128—Driving means
    • 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
    • F04D13/02—Units comprising pumps and their driving means
    • F04D13/021—Units comprising pumps and their driving means containing a coupling
    • 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.
  • the invention thus provides for the first time in the construction of a coolant pump a dedicated control circuit for regulating the position of a control slide by means of a hydraulic actuator.
  • 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.
  • either a centralized motor controller with lower processing power can be used at a correspondingly lower cost, or the added 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 pump control and the sensor are designed as a common electronic component.
  • the integration in an electronic component makes it possible to dispense with external wiring to different areas of the pump structure.
  • 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.
  • the sensor is 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 setpoint signal only a value corresponding to a volume flow, ie corresponds to a dissipated amount of heat.
  • the required heat output can be calculated by the central engine controller from the operating parameters of the internal combustion engine.
  • the pump controller may limit a path 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, which 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 have a pressure in the Detecting the pump chamber, which is in proportion to the delivered volume flow of the coolant pump.
  • the pump controller can compare a detected pressure of the sensor with a threshold value.
  • the pump control of the alternative Auslanderungsform with a pressure sensor can perform an autonomous function monitoring to ensure sufficient filling of the cooling system with coolant very 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 with the common electronic component.
  • the senor may have its own housing integrated with the common electronic component 20. This structure also makes it possible to effectively shield electromagnetic interference radiation from the control circuit relative to the sensor.
  • 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 electronic component according to the invention for use in a mechanically driven coolant pump according to one of claims 1 to 7 comprises a pump control and a sensor for detecting a position of a control slide in a pump chamber which limits the delivered volume flow.
  • the electronics required for control can be integrated with a component on the coolant pump, replaced or retrofitted.
  • a portion of the electronic component in which the pump controller is housed and a portion of the electronic component in which the sensor is housed may form an L-shaped arrangement with each other.
  • the parameter indicative of the volume flow of the delivered coolant may be a pressure in a pump chamber of the coolant pump, which corresponds to the volume flow of the delivered coolant.
  • the control method can be applied to an alternative embodiment of the coolant pump according to the invention.
  • 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 disposed, which is incorporated within a pump chamber 2 in a flow region of a cooling circuit of the internal combustion engine to cause a volume flow of the coolant.
  • 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 pushes the Coolant under pressure in 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, i. away from the impeller 5.
  • the annular piston 15 communicates with the control slide 7 in conjunction and moves 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 pumped 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.
  • the cylindrical portion 7a of the control slide 7 is 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 workload of the internal combustion engine, a fuel supply, a temperature, a vehicle speed or the like, a demanded volume flow of the coolant, which corresponds to a required heat output of the internal combustion engine.
  • various operating parameters e.g. a speed and workload of the internal combustion engine, a fuel supply, a temperature, a vehicle speed or the like, a demanded volume flow of the coolant, 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 for connection to a vehicle-side data bus for be provided 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 sensor 19 as a common electronic component 20.
  • a control circuit of the pump controller 21 and a sensor circuit may be molded in an encapsulated component.
  • an upgrade of a known ECF pump without modifications to the pump assembly can also take place.
  • the structure shown can 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 that the pump controller 21 receives from the central engine control ZMS includes a predetermined position of the control slide 7.
  • the central engine control ZMS calculates based on a required heat output of the internal combustion engine to be promoted by the coolant pump flow rate of the 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 the annular piston 15th or 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 carries out 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 off periods of the electromagnetic proportional valve 13 and the resulting change in position of the annular piston 15 or 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 control 21 performs a control in that the control slide 7 is moved to a new position for setting the flow rate 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 value. Signal from the central engine control is given.
  • 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, which in turn can initiate a limited emergency operation or shutdown of the internal combustion engine.
  • the electromagnetic proportional valve 13 may in a modified embodiment as well as an electric motor actuated Proportional valve 13 can be used.
  • the control signal for a servomotor does not have to contain pulse width modulation.
  • a CAN interface can be provided between the pump controller 21 and the central engine control ZMS.

Landscapes

  • 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)
  • Control Of Positive-Displacement Pumps (AREA)
EP15739275.4A 2014-07-21 2015-07-17 Kühlmittelpumpe mit integrierter regelung Active EP3172446B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102014110231.2A DE102014110231B3 (de) 2014-07-21 2014-07-21 Kühlmittelpumpe mit integrierter Regelung
PCT/EP2015/066472 WO2016012378A1 (de) 2014-07-21 2015-07-17 Kühlmittelpumpe mit integrierter regelung

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EP3172446A1 (de) 2017-05-31
CN106536888A (zh) 2017-03-22
CN106536888B (zh) 2019-10-18
US20170370274A1 (en) 2017-12-28
KR101912801B1 (ko) 2018-10-29
WO2016012378A1 (de) 2016-01-28
DE102014110231B3 (de) 2015-09-10
KR20170018025A (ko) 2017-02-15

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