EP3676498B1 - Controllable coolant pump for a main delivery circuit and a secondary delivery circuit - Google Patents

Controllable coolant pump for a main delivery circuit and a secondary delivery circuit Download PDF

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Publication number
EP3676498B1
EP3676498B1 EP18740810.9A EP18740810A EP3676498B1 EP 3676498 B1 EP3676498 B1 EP 3676498B1 EP 18740810 A EP18740810 A EP 18740810A EP 3676498 B1 EP3676498 B1 EP 3676498B1
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EP
European Patent Office
Prior art keywords
pump
valve
pressure
circuit
hydraulic control
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EP18740810.9A
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German (de)
French (fr)
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EP3676498A1 (en
Inventor
Franz Pawellek
Toni Steiner
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Nidec GPM GmbH
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Nidec GPM GmbH
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D15/00—Control, e.g. regulation, of pumps, pumping installations or systems
    • F04D15/0027—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
    • 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
    • F04D15/0005—Control, e.g. regulation, of pumps, pumping installations or systems by using valves
    • F04D15/0022—Control, e.g. regulation, of pumps, pumping installations or systems by using valves throttling valves or valves varying the pump inlet opening or the outlet opening
    • 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
    • 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
    • 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
    • F05D2250/00—Geometry
    • F05D2250/50—Inlet or outlet
    • F05D2250/52—Outlet
    • 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
    • F05D2270/50—Control logic embodiments
    • F05D2270/54—Control logic embodiments by electronic means, e.g. electronic tubes, transistors or IC's within an electronic circuit
    • 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 mechanically driven coolant pump with a controllable delivery rate for a main delivery circuit from a first outlet and for a secondary delivery circuit from a second outlet of the coolant pump.
  • auxiliary devices such as exhaust gas recirculation, a turbocharger, charge air cooling or the like, as well as so-called split cooling, i.e. separate cooling of the engine block and cylinder heads of the internal combustion engine, are used in vehicles.
  • split cooling i.e. separate cooling of the engine block and cylinder heads of the internal combustion engine.
  • both systems are known in the prior art that include one or more additional water pumps to enable independent promotion of individual circulations, as well as systems with water valves, which enable a needs-based distribution of a coolant flow delivered by a pump to different branches.
  • the provision of additional water pumps and water valves with actuators for valve adjustment in a branched pipeline network again requires the corresponding installation and susceptibility of cabling to interference for a power supply and control signal transmission between decentralized actuators or pump motors, a central control device and a battery.
  • a failure of a drive or a defect in a cable can have effects on other areas of the coolant circulation that do not comply with a uniform fail-safe mode to prevent consequential damage.
  • control slide In a closed state, the control slide covers the pump impeller to form a spiral housing, whereby the pump outlet is shut down. In this case, an opening to a bypass is released in a rear wall of the pump chamber behind the pump impeller, which allows coolant to be discharged from the pump chamber separately from the pump outlet.
  • an open position of the control slide in which a flow through the pump outlet is completely released, the opening of the bypass to the pump chamber is closed by a part of the control slide.
  • the disclosed coolant pump thus provides a function for switching a large delivery rate through the pump outlet or a small delivery rate through the bypass.
  • intermediate states of a dividing ratio of the delivery flow occur, the course of which cannot be controlled separately in the desired manner, but is established as a function of a pressure difference between the individual volume flows, which in turn results from a fixed flow geometry of the pump.
  • WO 2013/034126 A1 discloses a controllable coolant pump according to the preamble of claim 1.
  • one object of the present invention is to create a compact actuator for a coolant system with two delivery circuits.
  • Another aspect of the invention is also to create a constructive relationship for a fail-safe mode implemented jointly in the conveying circuits.
  • the controllable mechanical coolant pump with a first outlet for a main delivery circuit and a second outlet for a secondary delivery circuit has, inter alia, a hydraulic control circuit derived from the coolant with an inlet-side auxiliary pump, an outlet-side proportional valve and a control slide as a hydraulic actuator for limiting the flow of the main delivery circuit, and is characterized in particular in that a control valve is connected to the hydraulic control circuit as a hydraulic actuator for limiting the flow of the secondary delivery circuit, with actuations of the control slide and the control valve being assigned to respective pressure ranges in the hydraulic control circuit.
  • the invention thus provides for the first time a coolant pump with two hydraulic actuators, in particular for regulating two different pump outlets or delivery circuits.
  • the invention provides for the first time to connect two hydraulic actuators to a hydraulic control circuit, which is derived in particular from the coolant, i.e. to operate them with the same control pressure.
  • the actuators By designing the actuation of the actuators for different pressure ranges, they respond to a control of an assigned pressure in the hydraulic control circuit, at least in some areas, independently of one another, so that different valve positions can be made in the two conveying circuits.
  • two new basic states can be implemented in comparison to the state of the art of an ECF pump with bypass, i.e. the main conveyor circuit and secondary conveyor circuit are completely closed, or the main conveyor circuit and secondary conveyor circuit are fully open, as well as two adjustment ranges, in which For example, the main conveyor circuit remains closed and a flow rate of the secondary conveyor circuit can be set.
  • control valve can be connected to the hydraulic control circuit as a branched hydraulic actuator between the auxiliary pump and the proportional valve, and can be closed by means of the pressure in the hydraulic control circuit against an elastic bias.
  • This configuration of the hydraulic control means that the hydraulic actuators or the control slide and the control valve have the same control pressure at.
  • a fail-safe mode is achieved for the secondary conveyor circuit, as will be described later.
  • control valve can be designed as a seat valve valve which is acted upon by a spring in the opening direction.
  • the spring-loaded seat valve ensures smooth adjustment of the valve body in relation to the actuating force of the spring, even when the load is absorbed by the delivery pressure.
  • a piston area for receiving a hydraulic actuating force of the control valve in the hydraulic control circuit can be smaller than a piston area of the control slide in the hydraulic control circuit.
  • the piston area of the control valve to the piston area of the control slide can have an area ratio of approximately 1: 3.
  • This hydraulically effective area ratio between the two actuators in conjunction with the restoring forces of the respective spring preload, achieves a preferred spread of the two associated control pressure ranges, which is reflected in a defined response behavior between the two actuators.
  • control valve can be arranged in the second outlet on the pump housing.
  • a pressure valve can be provided between the main delivery flow and the secondary delivery flow which opens above a predetermined pressure difference between a higher pressure in the main delivery flow and a lower pressure in the secondary delivery flow.
  • the pressure valve thus counteracts the drying up of the small secondary conveying circuit during the transient pressure difference described, since part of the main conveying circuit flows into the secondary conveying circuit.
  • the pressure valve can be designed as a check valve which is acted upon by a spring in the closing direction.
  • a spring-loaded check valve forms the preferred means of providing a pressure valve which gradually opens for a flow from the main conveyor circuit to the secondary conveyor circuit as the pressure difference increases.
  • the pressure valve can open downstream from the control slide into the main delivery circuit and upstream from the control valve into the secondary delivery circuit.
  • This arrangement of the pressure valve achieves a preferred response behavior in the manner of operation described and enables a highly integrated, compact pump structure.
  • Fig. 1 shows a longitudinal section through the pump without complete outer contours of a pump housing 1.
  • a pump shaft 3 extends from a belt pulley 4, through a shaft bearing into a pump chamber 10 of the pump housing 1 and drives a pump impeller 2.
  • the pump impeller 2 and the pump chamber 10, which is not shown in full, are designed in the form of a radial pump assembly, in which a pump inlet 13 (not shown) flows axially towards the pump impeller 2, and a first pump outlet 11 for a main delivery circuit connected to the internal combustion engine a radially outer volute casing section leads out tangentially from the pump chamber 10.
  • the pump assembly of the coolant pump has a hydraulically adjustable control slide 8, which is known from a so-called ECF pump type.
  • a flow-effective radial area around the pump impeller 2 can be variably covered by the control slide 8 with a cylindrical section formed coaxially to the pump shaft 3 along an adjustment path running parallel to the pump shaft 3.
  • the control slide 8 is in a closed position, in which the flow area of the pump impeller 2 is completely covered and thus no delivery flow to the first pump outlet 11 is brought about.
  • an axial piston pump 6 (shown schematically) is also arranged within the radius of the pump impeller 2 and parallel to the pump shaft 3, the piston of which is actuated via a sliding shoe (not shown) which is mounted on a swash plate (not rotatably arranged with the pump shaft 3) shown) slides.
  • the axial piston pump 6 serves as an auxiliary pump of a coolant-operated hydraulic control circuit 5 (shown schematically) in which a control pressure independent of the flow rate is generated and set to control the control slide 8 and a control valve 9 described later.
  • the axial piston pump 6 sucks in coolant from the flow area between the pump impeller 2 and the control slide 9 and discharges the pressurized coolant into the hydraulic control circuit 5, which is formed in the pump housing 1.
  • the hydraulic control circuit 5 comprises an electromagnetically actuated proportional valve 7 (shown schematically), which limits a return of the coolant into the delivered coolant flow and thus sets a pressure of the hydraulic control circuit 5 in a path between the axial piston pump 6 and the proportional valve 7.
  • a hydraulic branch feeds the pressure of the hydraulic control circuit 5 to an annular piston 18, which is arranged coaxially with the pump shaft 3 and takes over the function of a hydraulic actuator along the displacement path of the control slide 8.
  • a return spring acts on the annular piston 18 in the opposite direction to the pressure of the hydraulic control circuit 5, ie away from the pump impeller 2.
  • the annular piston 18 is connected to the control slide 8 and moves it with increasing pressure of the hydraulic control circuit 5 in the direction of the pump impeller 2, whereby the cylindrical section of the control slide 6 is increasingly brought into axial overlap with the pump impeller 2.
  • the electromagnetic proportional valve 7 is opened without the supply of a control current, so that the coolant sucked in by the axial piston pump 6 flows back essentially without pressure via the hydraulic control circuit 5 through the proportional valve 7 and back into the pumped coolant.
  • the electromagnetic proportional valve 7 is closed temporarily or intermittently by supplying a control current controlled with pulse width modulation, the pressure generated by the axial piston pump 6 spreads via the hydraulic control circuit 5 to the annular piston 18. If the proportional valve 7 remains open by switching off the control current, no more pressure builds up in the hydraulic control circuit 5 and the annular piston 18 returns to the unactuated basic position under the action of the return spring.
  • a maximum delivery flow is brought about as a function of the pump speed without shielding a flow-effective region of the pump impeller 2 in the main delivery circuit.
  • This state also represents a fail-safe mode, since in the event of a power supply failure, ie a currentless electromagnetic proportional valve 7, a maximum volume flow and the greatest possible heat dissipation from the internal combustion engine through the main conveyor circuit are automatically ensured.
  • the pump housing 1 comprises a second pump outlet 12 for a secondary delivery circuit, to which a cooling system for an exhaust gas recirculation valve (EGR valve) is connected in the present exemplary embodiment.
  • the second pump outlet 12 opens into the pump chamber 10 on a rear side of the pump impeller 2.
  • the opening of the second pump outlet 12 is accessible through openings on the front of the control slide 8, regardless of its position, so that part of the flow from the pump chamber 10 always enters the second pump outlet 12 penetrates.
  • control valve 9 In the second pump outlet 12, the control valve 9 is arranged, which blocks, limits or opens a flow of the secondary delivery circuit.
  • the control valve 9 is also connected to the hydraulic control circuit 5 by a hydraulic branch.
  • a valve body of the control valve 9 is displaced by the pressure in the hydraulic control circuit 5 approximately perpendicular to the flow direction against the restoring force of a spring and gradually closes the flow in the second pump outlet 12.
  • the valve body of the control valve 9 is pushed back by the spring and the flow of the second pump outlet 12 is released.
  • the pressure in the hydraulic control circuit 5 is controlled by switching on and off times for opening and closing the proportional valve 7.
  • the pressure is controlled in such a way that a balance is achieved between the hydraulic pressure and a restoring force of the pretensioned spring in the regulating valve 9 and a position of the valve body in the regulating valve 9 is maintained.
  • the positions of the valve body of the control valve 9, like a position of the annular piston 18 of the control valve 8, can be detected by a displacement sensor (not shown) and used to control the proportional valve 7.
  • the main conveying circuit and the secondary conveying circuit are throttled in relation to a predetermined machine speed on the basis of a control current for opening and closing the electromagnetically actuated proportional valve 7.
  • the hydraulic configuration was selected in such a way that the control valve 9 for the secondary delivery circuit has a higher hydraulic value Pressure to close is required as the control slide 8 for the main conveyor circuit.
  • the assignment of the pressure ranges in which the hydraulic actuators respond is set on the basis of a hydraulically active piston area, which each actuator has for taking up pressure from the hydraulic control circuit 5, and the selected characteristic curve of the return springs.
  • the response behavior of the two hydraulic actuators is preferably selected such that an adjustment range of the control valve 9 can be controlled by a pressure that begins above a pressure at which the control slide 8 closes completely.
  • a suitable separation between the pressure for closing one hydraulic actuator and the lower pressure at the beginning of the adjustment range of the other actuator is set by a hydraulically effective area ratio.
  • the area ratio between the actuator closing at higher pressure and the actuator closing at lower pressure is 1: 3.
  • the in Fig. 1 The operating state of the controllable coolant pump shown is intended for a cold start situation of a vehicle in which the internal combustion engine or other devices are not yet required to cool.
  • the proportional valve 7 is controlled by a control unit (not shown) by a sampling ratio of a pulse width modulation with a high proportion of switch-on times in order to set a high pressure in the hydraulic control circuit 5.
  • the proportional valve 7 severely limits a return flow of the coolant behind the axial piston pump 6 and a backflow in front of the proportional valve 7 increases the pressure in the hydraulic control circuit 5 to the branched actuators until the control slide 8 and then the control valve 9 close.
  • both flows of the main conveying circuit and the secondary conveying circuit are consequently maximally limited or closed.
  • the in Fig. 2 The operating state of the controllable coolant pump shown is intended, for example, for a warm-up situation of a vehicle in which the internal combustion engine is not yet at operating temperature, but so-called hotspots have already formed on devices such as exhaust gas recirculation, so that there is already a need for cooling to protect components such as an EGR valve is present.
  • the proportional valve 7 is controlled by a sampling ratio of a pulse width modulation with a lower proportion of switch-on times in order to lower the pressure in the hydraulic control circuit 5.
  • a return flow from the hydraulic control circuit 5 through the proportional valve 7 increases and the pressure on the actuators decreases.
  • the control valve 9 initially moves back into the open position via gradual limiting positions, while the control slide 8 remains closed. If a pressure in the hydraulic control circuit 5 is maintained after this process, the flow of the main conveying circuit consequently remains closed and the flow in the secondary conveying circuit 5 remains open.
  • a gradual limitation of the secondary conveyor circuit can be set when the main conveyor circuit is closed.
  • the pressure valve 15 remains closed, since it is still exposed to a pressure of the secondary delivery circuit in the closing direction while the other side is not exposed to any delivery pressure.
  • the in Fig. 3 The operating state of the controllable coolant pump shown is intended for a load situation of a vehicle in which there is a need for cooling both for the internal combustion engine and for one or more other devices that are connected to the secondary delivery circuit.
  • Fig. 3 If the proportional valve 7 is not activated or is activated by a sampling ratio of a pulse width modulation with a small proportion of switch-on times, so that no pressure is generated in the hydraulic control circuit 5.
  • the control slide 8 then moves back into the open position via gradual limiting positions, while the control valve 9, which is already open, remains open.
  • both the flow of the main conveying circuit and the flow of the secondary conveying circuit 5 consequently remain open to the maximum.
  • a gradual limitation of the main conveying circuit can be set when the secondary conveying circuit is open.
  • the pressure valve 15 is opened by a pressure difference while the control slide 8 is opening or while the main conveying circuit is open to the maximum.
  • the pressure difference arises from a low pressure loss of the part of the conveying flow that flows into the main conveying circuit and a high pressure loss of the part of the conveying flow that flows into the secondary conveying circuit.
  • the pressure valve 15 opens and enables a flow of the large delivery rate in the main delivery circuit to compensate the insufficient delivery rate in the secondary delivery circuit. The flow behavior is thus improved during a transient state of the division or a relatively large division ratio between the delivery rates.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Control Of Positive-Displacement Pumps (AREA)

Description

Die vorliegende Erfindung betrifft eine mechanisch angetriebene Kühlmittelpumpe mit einer regelbaren Förderleistung für einen Hauptförderkreislauf aus einem ersten Auslass und für einen Nebenförderkreislauf aus einem zweiten Auslass der Kühlmittelpumpe.The present invention relates to a mechanically driven coolant pump with a controllable delivery rate for a main delivery circuit from a first outlet and for a secondary delivery circuit from a second outlet of the coolant pump.

Durch steigende Anforderungen an die Kraftstoffeffizienz und Emissionen von Verbrennungsmaschinen werden in Fahrzeugen Hilfseinrichtungen, wie eine Abgasrückführung, ein Turbolader, eine Ladeluftkühlung oder dergleichen, sowie ein sogenanntes Split Cooling, d.h. eine separate Kühlung von Motorblock und Zylinderköpfen der Verbrennungsmaschine eingesetzt. Die Einbindung eines jeweiligen thermischen Bedarfs zum Schutz der betreffenden Bauteile oder zur Funktionalität von Wärmeaustauschern stellt Herausforderungen an die Flexibilität moderner Thermomanagementsysteme.Due to increasing demands on fuel efficiency and emissions from internal combustion engines, auxiliary devices such as exhaust gas recirculation, a turbocharger, charge air cooling or the like, as well as so-called split cooling, i.e. separate cooling of the engine block and cylinder heads of the internal combustion engine, are used in vehicles. The integration of a respective thermal requirement for the protection of the relevant components or for the functionality of heat exchangers poses challenges to the flexibility of modern thermal management systems.

Um einen größeren Freiheitsgrad bei der Gestaltung des Thermomanagements, insbesondere hinsichtlich spezifischer Verzweigungen und Zirkulationen zu verschaffen, sind im Stand der Technik sowohl Systeme bekannt, die eine oder mehrere Zusatzwasserpumpen umfassen, um eine unabhängige Förderung individueller Zirkulationen zu ermöglichen, als auch Systeme mit Wasserventilen, die eine bedarfsgerechte Verteilung eines durch eine Pumpe geförderten Kühlmittelstroms auf verschiedene Zweige ermöglichen.In order to provide a greater degree of freedom in the design of the thermal management, in particular with regard to specific branches and circulations, both systems are known in the prior art that include one or more additional water pumps to enable independent promotion of individual circulations, as well as systems with water valves, which enable a needs-based distribution of a coolant flow delivered by a pump to different branches.

Die steigende Komplexität derartiger Systeme ist stets mit Problemstellungen der Kosten für Komponenten, der Installation, dem Packaging sowie der Ausfallsicherheit steuerungsrelevanter Komponenten konfrontiert.The increasing complexity of such systems is always confronted with problems relating to the costs of components, installation, packaging and the reliability of control-relevant components.

So geht beispielsweise die Bereitstellung von Zusatzwasserpumpen und Wasserventilen mit Stellgliedern zur Ventileinstellung in einem verzweigten Leitungsnetz wiederum mit einer entsprechenden Installation und Störempfindlichkeit von Verkabelungen für eine Leistungszufuhr und Steuersignalübertragung zwischen dezentralen Stellantrieben oder Pumpenmotoren, einer zentralen Steuereinrichtung und einer Batterie einher. Zudem kann durch die Anzahl und Unabhängigkeit der Komponenten, ein Ausfall eines Antriebs oder Defekt eines Kabels Auswirkungen auf andere Bereiche der Kühlmittelzirkulation nach sich ziehen, die nicht mit einem einheitlichen Fail Safe Modus zur Abwendung von Folgeschäden konform sind.Thus, for example, the provision of additional water pumps and water valves with actuators for valve adjustment in a branched pipeline network again requires the corresponding installation and susceptibility of cabling to interference for a power supply and control signal transmission between decentralized actuators or pump motors, a central control device and a battery. In addition, due to the number and independence of the components, a failure of a drive or a defect in a cable can have effects on other areas of the coolant circulation that do not comply with a uniform fail-safe mode to prevent consequential damage.

Aus der deutschen Patentanmeldung DE 10 2010 050 261 B3 derselben Anmelderin ist eine Kühlmittelpumpe vom sogenannten ECF (Electromagnetic Controlled Flow) Typ mit einem Bypass bekannt. Bei einer solchen ECF Pumpe kann trotz eines an die Maschinendrehzahl gebunden Riemenantriebs eine effektive Förderleistung gegenüber einer der Maschinendrehzahl entsprechenden Förderleistung gedrosselt eingestellt oder abgestellt werden. Somit sind selbst bei einem mechanisch abhängigen Pumpenantrieb Funktionen wie ein Kühlmittelstillstand während einer Kaltstartphase einer Verbrennungsmaschine oder dergleichen realisierbar. Die Regelung erfolgt über einen mittels Kühlmittel hydraulisch betätigten, zylindrischen Regelschieber, der einen strömungswirksamen radialen Bereich des Pumpenlaufrads überdeckt. In einem geschlossenen Zustand überdeckt der Regelschieber das Pumpenlaufrad zu einem Spiralgehäuse, wodurch der Pumpenauslass stillgelegt ist. Dabei wird eine Öffnung zu einem Bypass in einer Rückwand der Pumpenkammer hinter dem Pumpenlaufrad freigegeben, der eine zu dem Pumpenauslass separate Abfuhr von Kühlmittel aus der Pumpenkammer gewährt. Andererseits wird in einer offenen Position des Regelschiebers, in dem eine Strömung durch den Pumpenauslass vollständig freigegeben ist, die Öffnung des Bypasses zur Pumpenkammer durch einen Teil des Regelschiebers verschlossen.From the German patent application DE 10 2010 050 261 B3 by the same applicant is known a coolant pump of the so-called ECF (Electromagnetic Controlled Flow) type with a bypass. With such an ECF pump, despite a belt drive linked to the machine speed, an effective delivery rate can be set or switched off in a throttled manner compared to a delivery rate corresponding to the machine speed. Thus, even with a mechanically dependent pump drive, functions such as a coolant standstill during a cold start phase of an internal combustion engine or the like can be implemented. The regulation takes place via a cylindrical control slide hydraulically operated by means of coolant, which covers a flow-effective radial area of the pump impeller. In a closed state, the control slide covers the pump impeller to form a spiral housing, whereby the pump outlet is shut down. In this case, an opening to a bypass is released in a rear wall of the pump chamber behind the pump impeller, which allows coolant to be discharged from the pump chamber separately from the pump outlet. On the other hand, in an open position of the control slide, in which a flow through the pump outlet is completely released, the opening of the bypass to the pump chamber is closed by a part of the control slide.

Die offenbarte Kühlmittelpumpe stellt somit eine Funktion zum Umschalten einer großen Fördermenge durch den Pumpenauslass oder einer kleinen Fördermenge durch den Bypass zur Verfügung. Während der Drosselung der Förderleistung treten jedoch Zwischenzustände eines Teilungsverhältnisses des Förderstroms auf, deren Verlauf nicht in gewünschter Weise separat steuerbar ist, sondern sich in Abhängigkeit einer Druckdifferenz der einzelnen Volumenströme einstellt, die sich wiederum aus einer festen Strömungsgeometrie der Pumpe ergibt.The disclosed coolant pump thus provides a function for switching a large delivery rate through the pump outlet or a small delivery rate through the bypass. During the throttling of the delivery capacity, however, intermediate states of a dividing ratio of the delivery flow occur, the course of which cannot be controlled separately in the desired manner, but is established as a function of a pressure difference between the individual volume flows, which in turn results from a fixed flow geometry of the pump.

WO 2013/034126 A1 offenbart eine regelbare Kühlmittelpumpe nach dem Oberbegriff des Anspruchs 1. WO 2013/034126 A1 discloses a controllable coolant pump according to the preamble of claim 1.

Im Hinblick auf die Nachteile des zuvor genannten Stands der Technik besteht eine Aufgabe der vorliegenden Erfindung darin, eine kompakte Aktorik für ein Kühlmittelsystem mit zwei Förderkreisläufen zu schaffen.In view of the disadvantages of the aforementioned prior art, one object of the present invention is to create a compact actuator for a coolant system with two delivery circuits.

Ein weiterer Aspekt der Erfindung ist darüber hinaus, einen konstruktiven Zusammenhang für einen in den Förderkreisläufen gemeinsam umgesetzten Fail Safe Modus zu schaffen.Another aspect of the invention is also to create a constructive relationship for a fail-safe mode implemented jointly in the conveying circuits.

Die Aufgabe wird erfindungsgemäß durch eine Kühlmittelpumpe mit den Merkmalen des Anspruchs 1 gelöst.The object is achieved according to the invention by a coolant pump having the features of claim 1.

Die regelbare mechanische Kühlmittelpumpe mit einem ersten Auslass für einen Hauptförderkreislauf und einem zweiten Auslass für einen Nebenförderkreislauf weist u.a. einen aus dem Kühlmittel abgeleiteten hydraulischen Regelkreislauf mit einer eingangsseitigen Hilfspumpe, einem ausgangsseitigen Proportionalventil und einem Regelschieber als hydraulisches Stellglied zur Durchflussbegrenzung des Hauptförderkreislaufs auf, und zeichnet sich insbesondere dadurch aus, dass ein Regelventil als hydraulisches Stellglied zur Durchflussbegrenzung des Nebenförderkreislaufs mit dem hydraulischen Regelkreislauf verbunden ist, wobei Betätigungen des Regeschiebers und des Regelventils jeweiligen Druckbereichen im hydraulischen Regelkreislauf zugeordnet sind.The controllable mechanical coolant pump with a first outlet for a main delivery circuit and a second outlet for a secondary delivery circuit has, inter alia, a hydraulic control circuit derived from the coolant with an inlet-side auxiliary pump, an outlet-side proportional valve and a control slide as a hydraulic actuator for limiting the flow of the main delivery circuit, and is characterized in particular in that a control valve is connected to the hydraulic control circuit as a hydraulic actuator for limiting the flow of the secondary delivery circuit, with actuations of the control slide and the control valve being assigned to respective pressure ranges in the hydraulic control circuit.

Die Erfindung sieht somit erstmals eine Kühlmittelpumpe mit zwei hydraulischen Stellgliedern vor, insbesondere zur Regulierung von zwei unterschiedlichen Pumpenauslässen bzw. Förderkreisläufen.The invention thus provides for the first time a coolant pump with two hydraulic actuators, in particular for regulating two different pump outlets or delivery circuits.

Ferner sieht die Erfindung erstmals vor zwei hydraulische Stellglieder an einem hydraulischen Regelkreislauf, der insbesondere aus dem Kühlmittel abgeleitet wird, anzuschließen, d.h. mit demselben Regeldruck zu betreiben.Furthermore, the invention provides for the first time to connect two hydraulic actuators to a hydraulic control circuit, which is derived in particular from the coolant, i.e. to operate them with the same control pressure.

Als Leistungszufuhr bzw. Verstellkraft eines zusätzlichen Stellglieds wird eine bereits im Stand der Technik vorhandene Baugruppe genutzt und erweitert. Dadurch kann ein besonders kompakter Aufbau erzielt werden, in dem eine Aktorik zur Regelung der Förderkreise in der Pumpe integriert und Kosten eingespart werden. Insbesondere kann eine externe Verkabelung zu Stellgliedern oder Motoren im kühlmittelführenden Leitungsnetz entfallen.An assembly already available in the prior art is used and expanded as the power supply or adjusting force of an additional actuator. This can a particularly compact structure can be achieved in which actuators for regulating the delivery circuits are integrated in the pump and costs are saved. In particular, external cabling to actuators or motors in the coolant-carrying line network can be dispensed with.

Durch die Verknüpfung einer gemeinsamen hydraulischen Ansteuerung mittels desselben Regeldrucks, tritt auch im Falle eines Regelungsausfalls oder eines hydraulischen Defekts an beiden Stellgliedern dieselbe Ansteuerungsgröße auf, wodurch eine simultan ausgerichtete Reaktion der Stellglieder sichergestellt und zugunsten eines Fail Safe Modus in beiden Förderkreisläufen nutzbar ist.By linking a common hydraulic control by means of the same control pressure, the same control variable occurs even in the event of a control failure or a hydraulic defect on both actuators, which ensures a simultaneous reaction of the actuators and can be used in both conveyor circuits in favor of a fail-safe mode.

Durch die Auslegung der Betätigung der Stellglieder auf verschiedene Druckbereiche, sprechen diese auf eine Steuerung eines zugeordneten Drucks im hydraulischen Regelkreislauf zumindest bereichsweise unabhängig voneinander an, sodass verschiedene Ventilstellungen in den beiden Förderkreisläufen vorgenommen werden können. Durch die Ansteuerung beider hydraulischer Stellglieder aus dem hydraulischen Regelkreislauf lassen sich im Vergleich zum genannten Stand der Technik einer ECF Pumpe mit Bypass zwei neue Grundzustände, d.h. Hauptförderkreislauf und Nebenförderkreislauf vollständig geschlossen, oder Hauptförderkreislauf und Nebenförderkreislauf vollständig geöffnet, als auch zwei Verstellbereiche realisieren, in wobei z.B. der Hauptförderkreislauf geschlossen bleibt und ein Durchfluss des Nebenförderkreislaufs einstellbar ist.By designing the actuation of the actuators for different pressure ranges, they respond to a control of an assigned pressure in the hydraulic control circuit, at least in some areas, independently of one another, so that different valve positions can be made in the two conveying circuits. By activating both hydraulic actuators from the hydraulic control circuit, two new basic states can be implemented in comparison to the state of the art of an ECF pump with bypass, i.e. the main conveyor circuit and secondary conveyor circuit are completely closed, or the main conveyor circuit and secondary conveyor circuit are fully open, as well as two adjustment ranges, in which For example, the main conveyor circuit remains closed and a flow rate of the secondary conveyor circuit can be set.

Vorteilhafte Weiterbildungen der regelbaren Kühlmittelpumpe sind Gegenstand der abhängigen Ansprüche.Advantageous developments of the controllable coolant pump are the subject of the dependent claims.

Gemäß einem Aspekt der Erfindung kann das Regelventil als abgezweigtes hydraulisches Stellglied zwischen der Hilfspumpe und dem Proportionalventil mit dem hydraulischen Regelkreislauf verbunden sein, und mittels des Drucks im hydraulischen Regelkreislauf entgegen einer elastischen Vorspannung geschlossen werden.According to one aspect of the invention, the control valve can be connected to the hydraulic control circuit as a branched hydraulic actuator between the auxiliary pump and the proportional valve, and can be closed by means of the pressure in the hydraulic control circuit against an elastic bias.

Durch diese Konfiguration der hydraulischen Ansteuerung liegt an den hydraulischen Stellgliedern bzw. dem Regelschieber und dem Regelventil derselbe Regeldruck an. Durch die Auslegung als drucklos geöffnetes Ventil wird eine Fail Safe Modus für den Nebenförderkreislauf erzielt, wie später beschrieben wird.This configuration of the hydraulic control means that the hydraulic actuators or the control slide and the control valve have the same control pressure at. As a result of the design as a valve that is open without pressure, a fail-safe mode is achieved for the secondary conveyor circuit, as will be described later.

Gemäß einem Aspekt der Erfindung kann das Regelventil als Sitzventilventil ausgebildet sein, das durch eine Feder in Öffnungsrichtung beaufschlagt ist.According to one aspect of the invention, the control valve can be designed as a seat valve valve which is acted upon by a spring in the opening direction.

Das federbeaufschlagte Sitzventil stellt auch unter Lastaufnahme des Förderdrucks eine leichtgängig geführte Verstellung des Ventilkörpers in Bezug auf die Stellkraft der Feder sicher.The spring-loaded seat valve ensures smooth adjustment of the valve body in relation to the actuating force of the spring, even when the load is absorbed by the delivery pressure.

Gemäß einem Aspekt der Erfindung kann eine Kolbenfläche zur Aufnahme einer hydraulischen Stellkraft des Regelventils im hydraulischen Regelkreislauf kleiner als eine Kolbenfläche des Regelschiebers im hydraulischen Regelkreislauf sein.According to one aspect of the invention, a piston area for receiving a hydraulic actuating force of the control valve in the hydraulic control circuit can be smaller than a piston area of the control slide in the hydraulic control circuit.

Durch diese Auswahl der unterschiedlichen hydraulisch wirksamen Flächengrößen der Stellglieder wird eine anwendungsspezifische Präferenz in der hydraulischen Ansteuerung getroffen. Somit wird in einem mittleren Bereich des Regeldrucks, der zwischen den jeweiligen Drücken zum Schließen des Regelschiebers und des Regelventils liegt, derjenige Zustand umgesetzt, dass der Regelschieber für den Hauptförderkreislauf geschlossen bleibt und das Regelventil für den Nebenförderkreislauf einstellbar geöffnet wird. Dieser Zustand wird beispielsweise benötigt, wenn die Verbrennungsmaschine eine Betriebstemperatur schnell erreichen soll während an Hilfseinrichtungen, wie z.B. an einem Ventil der Abgasrückführung bereits Kühlungsbedarf besteht.Through this selection of the different hydraulically effective area sizes of the actuators, an application-specific preference is made in the hydraulic control. Thus, in a middle range of the regulating pressure, which lies between the respective pressures for closing the regulating slide and the regulating valve, that state is implemented that the regulating slide for the main conveying circuit remains closed and the regulating valve for the secondary conveying circuit is adjustably opened. This state is required, for example, if the internal combustion engine is to reach an operating temperature quickly while auxiliary equipment, such as an exhaust gas recirculation valve, already needs cooling.

Gemäß einem Aspekt der Erfindung kann die Kolbenfläche des Regelventils zu der Kolbenfläche des Regelschiebers ein Flächenverhältnis von etwa 1:3 betragen.According to one aspect of the invention, the piston area of the control valve to the piston area of the control slide can have an area ratio of approximately 1: 3.

Durch dieses hydraulisch wirksame Flächenverhältnis zwischen den beiden Stellgliedern wird im Zusammenhang mit den Rückstellkräften der jeweiligen Federvorspannung eine bevorzugte Spreizung der beiden zugeordneten Bereiche des Regeldrucks erzielt, was sich in einem definierten Ansprechverhalten zwischen den beiden Stellgliedern widerspiegelt.This hydraulically effective area ratio between the two actuators, in conjunction with the restoring forces of the respective spring preload, achieves a preferred spread of the two associated control pressure ranges, which is reflected in a defined response behavior between the two actuators.

Gemäß einem Aspekt der Erfindung kann das Regelventil in dem zweiten Auslass am Pumpengehäuse angeordnet sein.According to one aspect of the invention, the control valve can be arranged in the second outlet on the pump housing.

Somit werden ein hochintegrierter kompakter Pumpenaufbau und eine kurze hydraulische Anbindung des hydraulischen Regelkreises an das Regelventil ermöglicht.This enables a highly integrated, compact pump design and a short hydraulic connection between the hydraulic control circuit and the control valve.

Gemäß einem Aspekt der Erfindung kann zwischen dem Hauptförderstrom und dem Nebenförderstrom ein Druckventil bereitgestellt sein, das oberhalb einer vorbestimmten Druckdifferenz zwischen einem höheren Druck in dem Hauptförderstrom und einem niedrigeren Druck in dem Nebenförderstrom öffnet.According to one aspect of the invention, a pressure valve can be provided between the main delivery flow and the secondary delivery flow which opens above a predetermined pressure difference between a higher pressure in the main delivery flow and a lower pressure in the secondary delivery flow.

In einem Übergangszustand, in dem der Nebenförderkreislauf geöffnet ist und der Hauptförderkreislauf aus dem geschlossenen Zustand geöffnet wird, fällt aufgrund des großen Volumenstroms durch den ersten Pumpenauslass ein Förderdruck in dem zweiten Pumpenauslass stark ab, woraus eine entsprechende Abnahme des Volumenstroms im Nebenförderkreislauf trotz unveränderter Stellung der Regelventils resultiert.In a transitional state in which the secondary delivery circuit is open and the main delivery circuit is opened from the closed state, a delivery pressure in the second pump outlet drops sharply due to the large volume flow through the first pump outlet, resulting in a corresponding decrease in the volume flow in the secondary delivery circuit despite the unchanged position of the Control valve results.

Das Druckventil wirkt somit während der beschriebenen transienten Druckdifferenz einem Versiegen des kleinen Nebenförderkreislaufs entgegen, da ein Teil des Hauptförderkreislaufs in den Nebenförderkreislauf nachströmt.The pressure valve thus counteracts the drying up of the small secondary conveying circuit during the transient pressure difference described, since part of the main conveying circuit flows into the secondary conveying circuit.

Gemäß einem Aspekt der Erfindung kann das Druckventil als Rückschlagventil ausgebildet sein, das durch eine Feder in Schließrichtung beaufschlagt ist.According to one aspect of the invention, the pressure valve can be designed as a check valve which is acted upon by a spring in the closing direction.

Ein federbeaufschlagtes Rückschlagventil bildet das bevorzugte Mittel, um ein Druckventil bereitzustellen, das zu einem Nachströmen von dem Hauptförderkreislauf zu dem Nebenförderkreislaus bei zunehmender Druckdifferenz graduell öffnet.A spring-loaded check valve forms the preferred means of providing a pressure valve which gradually opens for a flow from the main conveyor circuit to the secondary conveyor circuit as the pressure difference increases.

Gemäß einem Aspekt der Erfindung kann das Druckventil strömungsabwärts vom Regelschieber in den Hauptförderkreislauf und strömungsaufwärts vom Regelventil in den Nebenförderkreislauf münden.According to one aspect of the invention, the pressure valve can open downstream from the control slide into the main delivery circuit and upstream from the control valve into the secondary delivery circuit.

Diese Anordnung des Druckventils erzielt in der beschriebenen Funktionsweise ein bevorzugtes Ansprechverhalten und ermöglicht einen hochintegrierten kompakten Pumpenaufbau.This arrangement of the pressure valve achieves a preferred response behavior in the manner of operation described and enables a highly integrated, compact pump structure.

Die Erfindung wird nachfolgend anhand eines Ausführungsbeispiels mit Bezug auf die Zeichnungen der Figuren 1 bis 3 beschrieben. In diesen zeigen:

Fig. 1
eine axiale Schnittansicht der Pumpe in einem Zustand, in dem sowohl der Hauptförderkreislauf als auch der Nebenförderkreislauf geschlossen sind;
Fig. 2
eine axiale Schnittansicht der Pumpe in einem Zustand, in dem der Hauptförderkreislauf geschlossen ist und der Nebenförderkreislauf geöffnet ist;
Fig. 3
eine axiale Schnittansicht der Pumpe in einem Zustand, in dem sowohl der Hauptförderkreislauf als auch der Nebenförderkreislauf geöffnet sind.
The invention is explained below using an exemplary embodiment with reference to the drawings of FIG Figures 1 to 3 described. In these show:
Fig. 1
an axial sectional view of the pump in a state in which both the main conveyor circuit and the secondary conveyor circuit are closed;
Fig. 2
an axial sectional view of the pump in a state in which the main conveyor circuit is closed and the secondary conveyor circuit is open;
Fig. 3
an axial sectional view of the pump in a state in which both the main conveyor circuit and the secondary conveyor circuit are open.

Fig. 1 zeigt einen Längsschnitt durch die Pumpe ohne vollständige Außenkonturen eines Pumpengehäuses 1. Eine Pumpenwelle 3 erstreckt sich von einer Riemenscheibe 4, durch ein Wellenlager in eine Pumpenkammer 10 des Pumpengehäuses 1 und treibt ein Pumpenlaufrad 2 an. Das Pumpenlaufrad 2 und die Pumpenkammer 10, die nicht vollständig dargestellt ist, sind in der Bauweise einer Radialpumpenbaugruppe ausgestaltet, bei der ein Pumpeneinlass 13 (nicht dargestellt) das Pumpenlaufrad 2 axial anströmt, und ein erster Pumpenauslass 11 für einen mit der Verbrennungsmaschine verbundenen Hauptförderkreislauf über einen radial äußeren Spiralgehäuseabschnitt tangential aus der Pumpenkammer 10 ausleitet. Fig. 1 shows a longitudinal section through the pump without complete outer contours of a pump housing 1. A pump shaft 3 extends from a belt pulley 4, through a shaft bearing into a pump chamber 10 of the pump housing 1 and drives a pump impeller 2. The pump impeller 2 and the pump chamber 10, which is not shown in full, are designed in the form of a radial pump assembly, in which a pump inlet 13 (not shown) flows axially towards the pump impeller 2, and a first pump outlet 11 for a main delivery circuit connected to the internal combustion engine a radially outer volute casing section leads out tangentially from the pump chamber 10.

Die Pumpenbaugruppe der Kühlmittelpumpe weist einen hydraulisch verstellbaren Regelschieber 8 auf, der aus einem sogenannten ECF Pumpentyp bekannt ist. Dabei kann ein strömungswirksamer radialer Bereich um das Pumpenlaufrad 2 von dem Regelschieber 8 mit einem koaxial zur Pumpenwelle 3 ausgebildeten zylindrischen Abschnitt entlang eines parallel zur Pumpenwelle 3 verlaufenden Stellwegs variabel überdeckt werden. In Fig. 1 befindet sich der Regelschieber 8 in einer geschlossenen Position, in welcher der Strömungsbereich des Pumpenlaufrads 2 vollständig überdeckt wird und somit kein Förderstrom zu dem ersten Pumpenauslass 11 bewirkt wird.The pump assembly of the coolant pump has a hydraulically adjustable control slide 8, which is known from a so-called ECF pump type. A flow-effective radial area around the pump impeller 2 can be variably covered by the control slide 8 with a cylindrical section formed coaxially to the pump shaft 3 along an adjustment path running parallel to the pump shaft 3. In Fig. 1 the control slide 8 is in a closed position, in which the flow area of the pump impeller 2 is completely covered and thus no delivery flow to the first pump outlet 11 is brought about.

In dem Pumpengehäuse 1 ist ferner innerhalb des Radius des Pumpenlaufrads 2 und parallel zur Pumpenwelle 3 eine Axialkolbenpumpe 6 (schematisch dargestellt) angeordnet, deren Kolben über einen Gleitschuh (nicht dargestellt) betätigt wird, der auf einer mit der Pumpenwelle 3 drehfest angeordneten Taumelscheibe (nicht dargestellt) gleitet. Die Axialkolbenpumpe 6 dient als eine Hilfspumpe eines mit Kühlmittel betriebenen hydraulischen Regelkreislaufs 5 (schematisch dargestellt), in dem ein zum Förderstrom unabhängiger Regeldruck zur Ansteuerung des Regelschiebers 8 und eines später beschriebenen Regelventils 9 erzeugt und eingestellt wird.In the pump housing 1, an axial piston pump 6 (shown schematically) is also arranged within the radius of the pump impeller 2 and parallel to the pump shaft 3, the piston of which is actuated via a sliding shoe (not shown) which is mounted on a swash plate (not rotatably arranged with the pump shaft 3) shown) slides. The axial piston pump 6 serves as an auxiliary pump of a coolant-operated hydraulic control circuit 5 (shown schematically) in which a control pressure independent of the flow rate is generated and set to control the control slide 8 and a control valve 9 described later.

Die Axialkolbenpumpe 6 saugt Kühlmittel aus dem Strömungsbereich zwischen dem Pumpenlaufrad 2 und dem Regelschieber 9 an und stößt das unter Druck gesetzte Kühlmittel in den hydraulischen Regekreislauf 5 aus, der in dem Pumpengehäuse 1 ausgebildet ist. Der hydraulische Regelkreislauf 5 umfasst ein elektromagnetisch betätigtes Proportionalventil 7 (schematisch dargestellt), das einen Rücklauf des Kühlmittels in den geförderten Kühlmittelstrom begrenzt und somit einen Druck des hydraulischen Regekreislaufs 5 in einer Strecke zwischen der Axialkolbenpumpe 6 und dem Proportionalventil 7 einstellt.The axial piston pump 6 sucks in coolant from the flow area between the pump impeller 2 and the control slide 9 and discharges the pressurized coolant into the hydraulic control circuit 5, which is formed in the pump housing 1. The hydraulic control circuit 5 comprises an electromagnetically actuated proportional valve 7 (shown schematically), which limits a return of the coolant into the delivered coolant flow and thus sets a pressure of the hydraulic control circuit 5 in a path between the axial piston pump 6 and the proportional valve 7.

Eine hydraulische Abzweigung führt den Druck des hydraulischen Regekreislaufs 5 einem Ringkolben 18 zu, der koaxial zu der Pumpenwelle 3 angeordnet ist und die Funktion eines hydraulischen Stellglieds entlang des Verschiebungswegs des Regelschiebers 8 übernimmt. Eine Rückstellfeder beaufschlagt den Ringkolben 18 in entgegengesetzter Richtung zu dem Druck des hydraulischen Regelkreislaufs 5, d.h. hinweg von dem Pumpenlaufrad 2. Der Ringkolben 18 steht mit dem Regelschieber 8 in Verbindung und verschiebt diesen mit zunehmendem Druck des hydraulischen Regelkreislaufs 5 in Richtung des Pumpenlaufrads 2, wodurch der zylindrische Abschnitt des Regelschiebers 6 zunehmend in axiale Überschneidung mit dem Pumpenlaufrad 2 gebracht wird.A hydraulic branch feeds the pressure of the hydraulic control circuit 5 to an annular piston 18, which is arranged coaxially with the pump shaft 3 and takes over the function of a hydraulic actuator along the displacement path of the control slide 8. A return spring acts on the annular piston 18 in the opposite direction to the pressure of the hydraulic control circuit 5, ie away from the pump impeller 2. The annular piston 18 is connected to the control slide 8 and moves it with increasing pressure of the hydraulic control circuit 5 in the direction of the pump impeller 2, whereby the cylindrical section of the control slide 6 is increasingly brought into axial overlap with the pump impeller 2.

Das elektromagnetische Proportionalventil 7 ist ohne Zuführung eines Ansteuerstroms geöffnet, sodass das von der Axialkolbenpumpe 6 angesaugte Kühlmittel im Wesentlichen drucklos über den hydraulischen Regelkreislauf 5 durch das Proportionalventil 7 hindurch zurück in das geförderte Kühlmittel zurück fließt. Wenn das elektromagnetische Proportionalventil 7 durch Zuführung eines unter Pulsweitenmodulation gesteuerten Ansteuerstroms zweitweise bzw. intermittierend geschlossen wird, breitet sich der von der Axialkolbenpumpe 6 erzeugte Druck über den hydraulischen Regelkreislauf 5 zu dem Ringkolben 18 aus. Wenn das Proportionalventil 7 durch Abschalten des Ansteuerstroms geöffnet bleibt, baut sich in dem hydraulischen Regelkreislauf 5 kein Druck mehr auf und der Ringkolben 18 kehrt unter Beaufschlagung der Rückstellfeder in die unbetätigte Grundstellung zurück.The electromagnetic proportional valve 7 is opened without the supply of a control current, so that the coolant sucked in by the axial piston pump 6 flows back essentially without pressure via the hydraulic control circuit 5 through the proportional valve 7 and back into the pumped coolant. When the electromagnetic proportional valve 7 is closed temporarily or intermittently by supplying a control current controlled with pulse width modulation, the pressure generated by the axial piston pump 6 spreads via the hydraulic control circuit 5 to the annular piston 18. If the proportional valve 7 remains open by switching off the control current, no more pressure builds up in the hydraulic control circuit 5 and the annular piston 18 returns to the unactuated basic position under the action of the return spring.

In der geschlossenen Position des Regelschiebers 8, die in den Figuren 1 und 2 dargestellt ist, überdeckt dessen zylindrischer Abschnitt das Pumpenlaufrad 2 vollständig, sodass unabhängig von der Pumpendrehzahl im Wesentlichen kein Volumenstrom in das Spiralgehäuse bewirkt wird.In the closed position of the control slide 8, which is in the Figures 1 and 2 is shown, the cylindrical portion of which completely covers the pump impeller 2, so that, regardless of the pump speed, essentially no volume flow is brought about into the spiral housing.

In der offenen Position des Regelschiebers 8, die in Fig. 3 dargestellt ist, wird in Abhängigkeit der Pumpendrehzahl ein maximaler Förderstrom ohne Abschirmung eines strömungswirksamen Bereichs des Pumpenlaufrads 2 in dem Hauptförderkreislauf bewirkt. Dieser Zustand stellt zugleich einen Fail-Safe Modus dar, da im Falle eines Ausfalls einer Stromzufuhr, d.h. einem stromlosen elektromagnetischen Proportionalventil 7, automatisch ein maximaler Volumenstrom und ein größtmöglicher Wärmeaustrag aus dem Verbrennungsmotor durch den Hauptförderkreislauf sichergestellt ist.In the open position of the control slide 8, which is shown in Fig. 3 is shown, a maximum delivery flow is brought about as a function of the pump speed without shielding a flow-effective region of the pump impeller 2 in the main delivery circuit. This state also represents a fail-safe mode, since in the event of a power supply failure, ie a currentless electromagnetic proportional valve 7, a maximum volume flow and the greatest possible heat dissipation from the internal combustion engine through the main conveyor circuit are automatically ensured.

Darüber hinaus umfasst das Pumpengehäuse 1 einen zweiten Pumpenauslass 12 für einen Nebenförderkreislauf, an den im vorliegenden Ausführungsbeispiel eine Kühlung für ein Abgasrückführungsventil (AGR-Ventil) angeschlossen ist. Der zweite Pumpenauslass 12 mündet an einer Rückseite des Pumpenlaufrads 2 in die Pumpenkammer 10. Die Mündung des zweiten Pumpenauslasses 12 ist durch stirnseitige Öffnungen des Regelschiebers 8 unabhängig von einer Position desselben zugänglich, sodass stets ein Teil des Förderstroms aus der Pumpenkammer 10 in den zweiten Pumpenauslass 12 dringt.In addition, the pump housing 1 comprises a second pump outlet 12 for a secondary delivery circuit, to which a cooling system for an exhaust gas recirculation valve (EGR valve) is connected in the present exemplary embodiment. The second pump outlet 12 opens into the pump chamber 10 on a rear side of the pump impeller 2. The opening of the second pump outlet 12 is accessible through openings on the front of the control slide 8, regardless of its position, so that part of the flow from the pump chamber 10 always enters the second pump outlet 12 penetrates.

In dem zweiten Pumpenauslass 12 ist das Regelventil 9 angeordnet, das einen Durchfluss des Nebenförderkreislaufs sperrt, begrenzt oder öffnet. Das Regelventil 9 ist ebenfalls durch eine hydraulische Abzweigung mit dem hydraulischen Regelkreislauf 5 verbunden. Ein Ventilkörper des Regelventils 9 wird durch den Druck im hydraulischen Regelkreislauf 5 in etwa senkrecht zur Flussrichtung gegen die Rückstellkraft einer Feder verschoben und verschließt dabei graduell den Durchfluss im zweiten Pumpenauslass 12. Bei geringerem hydraulischem Regeldruck wird der Ventilkörper des Regelventils 9 durch die Feder zurückgeschoben und der Durchfluss des zweiten Pumpenauslasses 12 freigegeben.In the second pump outlet 12, the control valve 9 is arranged, which blocks, limits or opens a flow of the secondary delivery circuit. The control valve 9 is also connected to the hydraulic control circuit 5 by a hydraulic branch. A valve body of the control valve 9 is displaced by the pressure in the hydraulic control circuit 5 approximately perpendicular to the flow direction against the restoring force of a spring and gradually closes the flow in the second pump outlet 12. At a lower hydraulic control pressure, the valve body of the control valve 9 is pushed back by the spring and the flow of the second pump outlet 12 is released.

Wie in Bezug auf die hydraulische Ansteuerung des Regeschiebers 8 erläutert, wird der Druck im hydraulischen Regelkreislauf 5 durch Ein- und Ausschaltdauern zum Öffnen- und Schließen des Proportionalventils 7 gesteuert. Zur Ansteuerung des Regelventils 9 in eine variable Stellung zur Durchflussbegrenzung wird der Druck derart gesteuert, dass ein Gleichgewicht zwischen dem hydraulischen Druck und einer Rückstellkraft der vorgespannten Feder im Regelventil 9 erzielt wird und eine Stellung des Ventilkörpers im Regelventil 9 gehalten wird.As explained in relation to the hydraulic control of the regulating slide 8, the pressure in the hydraulic control circuit 5 is controlled by switching on and off times for opening and closing the proportional valve 7. To control the regulating valve 9 in a variable position to limit the flow, the pressure is controlled in such a way that a balance is achieved between the hydraulic pressure and a restoring force of the pretensioned spring in the regulating valve 9 and a position of the valve body in the regulating valve 9 is maintained.

Die Stellungen des Ventilkörpers des Regelventils 9 können ebenso wie eine Stellung des Ringkolbens 18 des Regelventils 8 durch einen Wegsensor (nicht dargestellt) erfasst und zur Regelung des Proportionalventils 7 verwendet. Dadurch wird eine Drosselung des Hauptförderkreislaufs und des Nebenförderkreislaufs in Bezug zu einer vorgegebenen Maschinendrehzahl Anhand eines Ansteuerstroms zum Öffnen und Schließen des elektromagnetisch betätigten Proportionalventils 7 durchgeführt.The positions of the valve body of the control valve 9, like a position of the annular piston 18 of the control valve 8, can be detected by a displacement sensor (not shown) and used to control the proportional valve 7. As a result, the main conveying circuit and the secondary conveying circuit are throttled in relation to a predetermined machine speed on the basis of a control current for opening and closing the electromagnetically actuated proportional valve 7.

Nachstehend werden die Einstellung von zwei Grundzuständen und eines Verstellbereichs der Durchflussbegrenzung mit Bezug auf die Figuren 1 bis 3 erläutert.The following describes the setting of two basic states and an adjustment range of the flow restriction with reference to the Figures 1 to 3 explained.

In der dargestellten Ausführungsform wurde die hydraulische Ausgestaltung derart gewählt, dass das Regelventil 9 für den Nebenförderkreislauf einen höheren hydraulischen Druck zum Schließen benötigt als der Regelschieber 8 für den Hauptförderkreislauf. Die Zuordnung der Druckbereiche, in denen die hydraulischen Stellglieder ansprechen, wird anhand einer hydraulisch wirksamen Kolbenfläche, die jedes Stellglied zur Druckaufnahme aus dem hydraulischen Regelkreislauf 5 aufweist, und der gewählten Kennlinie der Rückstellfedern eingestellt. In der dargestellten Ausführungsform ist das Ansprechverhalten der beiden hydraulischen Stellglieder vorzugsweise derart gewählt, dass ein Verstellbereich des Regelventils 9 durch einen Druck ansteuerbar ist, der oberhalb eines Drucks beginnt, bei dem der Regelschieber 8 vollständig schließt. Bei entsprechender Auswahl der Rückstellfedern wird eine geeignete Trennung zwischen dem Druck zum Schließen des einen hydraulischen Stellglieds und dem unteren Druck zu Beginn des Verstellbereichs des anderen Stellglieds durch ein hydraulisch wirksames Flächenverhältnis eingestellt. Beispielsweise beträgt das Flächenverhältnis zwischen dem bei höheren Druck schließenden Stellglied und dem bei niedrigerem Druck schließenden Stellglied den Wert 1:3.In the embodiment shown, the hydraulic configuration was selected in such a way that the control valve 9 for the secondary delivery circuit has a higher hydraulic value Pressure to close is required as the control slide 8 for the main conveyor circuit. The assignment of the pressure ranges in which the hydraulic actuators respond is set on the basis of a hydraulically active piston area, which each actuator has for taking up pressure from the hydraulic control circuit 5, and the selected characteristic curve of the return springs. In the embodiment shown, the response behavior of the two hydraulic actuators is preferably selected such that an adjustment range of the control valve 9 can be controlled by a pressure that begins above a pressure at which the control slide 8 closes completely. With an appropriate selection of the return springs, a suitable separation between the pressure for closing one hydraulic actuator and the lower pressure at the beginning of the adjustment range of the other actuator is set by a hydraulically effective area ratio. For example, the area ratio between the actuator closing at higher pressure and the actuator closing at lower pressure is 1: 3.

Der in Fig. 1 gezeigte Betriebszustand der regelbaren Kühlmittelpumpe ist für eine Kaltstartsituation eines Fahrzeugs gedacht, in der noch kein Kühlungsbedarf der Verbrennungsmaschine oder von anderen Einrichtungen vorliegt.The in Fig. 1 The operating state of the controllable coolant pump shown is intended for a cold start situation of a vehicle in which the internal combustion engine or other devices are not yet required to cool.

In Fig. 1 wird das Proportionalventil 7 von einer Steuereinheit (nicht dargestellt) durch ein Abtastverhältnis einer Pulsweitenmodulation mit einem hohen Anteil von Einschaltzeiten angesteuert, um einen hohen Druck im hydraulischen Regelkreislauf 5 einzustellen. Das Proportionalventil 7 begrenzt einen Rückfluss des Kühlmittels hinter der Axialkolbenpumpe 6 stark und ein Rückstau vor dem Proportionalventil 7 lässt den Druck im hydraulischen Regelkreislauf 5 zu den verzweigten Stellgliedern ansteigen, bis zunächst der Regelschieber 8 und darauffolgend das Regelventil 9 schließen. Ab einem halten eines Drucks, bei dem das Regelventil 9 vollständig schließt, sind folglich beide Durchflüsse des Hauptförderkreislaufs und des Nebenförderkreislaufs maximal begrenzt bzw. geschlossen.In Fig. 1 the proportional valve 7 is controlled by a control unit (not shown) by a sampling ratio of a pulse width modulation with a high proportion of switch-on times in order to set a high pressure in the hydraulic control circuit 5. The proportional valve 7 severely limits a return flow of the coolant behind the axial piston pump 6 and a backflow in front of the proportional valve 7 increases the pressure in the hydraulic control circuit 5 to the branched actuators until the control slide 8 and then the control valve 9 close. As soon as a pressure is maintained at which the control valve 9 closes completely, both flows of the main conveying circuit and the secondary conveying circuit are consequently maximally limited or closed.

Ein Druckventil 15, das zwischen dem ersten Pumpenauslass 11 und dem zweiten Pumpenauslass 12 angeordnet ist, ist geschlossen, da es in Schließrichtung einem Druck des Nebenförderkreislaufs ausgesetzt ist, der sich vor dem geschlossenen Regelventil 9 staut, während die andere Seite in einem stillgelegten Abschnitt des ersten Pumpenauslasses 11 bzw. des Spiralgehäuses keinem Förderdruck ausgesetzt ist.A pressure valve 15, which is arranged between the first pump outlet 11 and the second pump outlet 12, is closed because there is a pressure in the closing direction of the secondary delivery circuit, which accumulates in front of the closed control valve 9, while the other side is not exposed to any delivery pressure in a disused section of the first pump outlet 11 or the spiral housing.

Der in Fig. 2 gezeigte Betriebszustand der regelbaren Kühlmittelpumpe ist beispielsweise für eine Warmlaufsituation eines Fahrzeugs gedacht, in der die Verbrennungsmaschine noch nicht auf Betriebstemperatur ist, sich an Einrichtungen wie einer Abgasrückführung jedoch bereits sogenannte Hotspots gebildet haben, sodass bereits ein Kühlungsbedarf zum Schutz von Bauteilen wie einem AGR-Ventil vorliegt.The in Fig. 2 The operating state of the controllable coolant pump shown is intended, for example, for a warm-up situation of a vehicle in which the internal combustion engine is not yet at operating temperature, but so-called hotspots have already formed on devices such as exhaust gas recirculation, so that there is already a need for cooling to protect components such as an EGR valve is present.

In Fig. 2 wird das Proportionalventil 7 durch ein Abtastverhältnis einer Pulsweitenmodulation mit einem niedrigeren Anteil von Einschaltzeiten angesteuert, um den Druck im hydraulischen Regelkreislauf 5 abzusenken. Ein Rückfluss aus dem hydraulischen Regelkreislauf 5 durch das Proportionalventil 7 nimmt zu und der Druck an den Stellgliedern nimmt ab. Dabei bewegt sich zunächst das Regelventil 9 über graduelle Begrenzungspositionen in die geöffnete Stellung zurück, während der Regelschieber 8 geschlossen bleibt. Wenn ein Druck im hydraulischen Regelkreislauf 5 nach diesem Vorgang gehalten wird, bleibt folglich der Durchfluss des Hauptförderkreislaufs geschlossen und der Durchfluss im Nebenförderkreislauf 5 geöffnet. Zudem ist bei Regelung eines höheren Drucks im Regelkreislauf 5 eine graduelle Begrenzung des Nebenförderkreislaufs bei geschlossenem Hauptförderkreislauf einstellbar.In Fig. 2 the proportional valve 7 is controlled by a sampling ratio of a pulse width modulation with a lower proportion of switch-on times in order to lower the pressure in the hydraulic control circuit 5. A return flow from the hydraulic control circuit 5 through the proportional valve 7 increases and the pressure on the actuators decreases. The control valve 9 initially moves back into the open position via gradual limiting positions, while the control slide 8 remains closed. If a pressure in the hydraulic control circuit 5 is maintained after this process, the flow of the main conveying circuit consequently remains closed and the flow in the secondary conveying circuit 5 remains open. In addition, when a higher pressure is regulated in the control circuit 5, a gradual limitation of the secondary conveyor circuit can be set when the main conveyor circuit is closed.

Das Druckventil 15 bleibt wiederum geschlossen, da es weiterhin in Schließrichtung einem Druck des Nebenförderkreislaufs ausgesetzt ist während die andere Seite keinem Förderdruck ausgesetzt ist.The pressure valve 15 remains closed, since it is still exposed to a pressure of the secondary delivery circuit in the closing direction while the other side is not exposed to any delivery pressure.

Der in Fig. 3 gezeigte Betriebszustand der regelbaren Kühlmittelpumpe ist für eine Lastsituation eines Fahrzeugs gedacht, in der sowohl für die Verbrennungsmaschine als auch für eine oder mehrere andere Einrichtungen, die mit dem Nebenförderkreislauf verbunden sind, ein Kühlungsbedarf vorliegt.The in Fig. 3 The operating state of the controllable coolant pump shown is intended for a load situation of a vehicle in which there is a need for cooling both for the internal combustion engine and for one or more other devices that are connected to the secondary delivery circuit.

In Fig. 3 wird das Proportionalventil 7 nicht oder durch ein Abtastverhältnis einer Pulsweitenmodulation mit einem geringen Anteil von Einschaltzeiten angesteuert, sodass im hydraulischen Regelkreislauf 5 kein Druck erzeugt wird. Daraufhin bewegt sich der Regelschieber 8 über graduelle Begrenzungspositionen in die geöffnete Stellung zurück, während das bereits geöffnete Regelventil 9 offen bleibt. Solange kein Druck im hydraulischen Regelkreislauf 5 erzeugt wird, bleiben folglich sowohl der Durchfluss des Hauptförderkreislaufs als auch der Durchfluss des Nebenförderkreislaufs 5 maximal geöffnet. Zudem ist bei Regelung eines niedrigen Drucks im Regelkreislauf 5 eine graduelle Begrenzung des Hauptförderkreislaufs bei geöffnetem Nebenförderkreislauf einstellbar.In Fig. 3 If the proportional valve 7 is not activated or is activated by a sampling ratio of a pulse width modulation with a small proportion of switch-on times, so that no pressure is generated in the hydraulic control circuit 5. The control slide 8 then moves back into the open position via gradual limiting positions, while the control valve 9, which is already open, remains open. As long as no pressure is generated in the hydraulic control circuit 5, both the flow of the main conveying circuit and the flow of the secondary conveying circuit 5 consequently remain open to the maximum. In addition, when regulating a low pressure in the control circuit 5, a gradual limitation of the main conveying circuit can be set when the secondary conveying circuit is open.

Das Druckventil 15 wird während des Öffnens des Regelschiebers 8 bzw. während eines maximal geöffneten Hauptförderkreislaufs durch eine Druckdifferenz geöffnet. Die Druckdifferenz entsteht durch einen geringen Druckverlust des Teils des Förderstroms, der in den Hauptförderkreislauf fließt, und einen hohen Druckverlust des Teils des Förderstroms, der in den Nebenförderkreislauf fließt. Infolgedessen würde ohne das Druckventil 15, je nach Strömungsgeometrie bzw. - verhältnis der Pumpenauslässe 11, 12, kein ausreichender Volumenstrom in den Nebenförderkreislauf abfließen. Sobald der Volumenstrom des Nebenförderkreislaufs einbricht erhöht ein entsprechender Druckabfall in dem zweiten Pumpenauslass 12 die Druckdifferenz am Druckventil 15. Wenn die Druckdifferenz einen voreingestellten Schwellwert des Druckventils 15 überschreitet, öffnet sich das Druckventil 15 und ermöglicht ein Nachströmen aus der großen Fördermenge in dem Hauptförderkreislauf zum Ausgleich der unzureichenden Fördermenge in dem Nebenförderkreislauf. Somit wird das Strömungsverhalten während eines transienten Zustands der Aufteilung oder eines relativ großen Teilungsverhältnisses zwischen den Fördermengen verbessert.The pressure valve 15 is opened by a pressure difference while the control slide 8 is opening or while the main conveying circuit is open to the maximum. The pressure difference arises from a low pressure loss of the part of the conveying flow that flows into the main conveying circuit and a high pressure loss of the part of the conveying flow that flows into the secondary conveying circuit. As a result, without the pressure valve 15, depending on the flow geometry or flow ratio of the pump outlets 11, 12, there would be insufficient volume flow into the secondary delivery circuit. As soon as the volume flow of the secondary delivery circuit collapses, a corresponding pressure drop in the second pump outlet 12 increases the pressure difference at the pressure valve 15.If the pressure difference exceeds a pre-set threshold value of the pressure valve 15, the pressure valve 15 opens and enables a flow of the large delivery rate in the main delivery circuit to compensate the insufficient delivery rate in the secondary delivery circuit. The flow behavior is thus improved during a transient state of the division or a relatively large division ratio between the delivery rates.

Claims (9)

  1. A controllable coolant pump which is driven mechanically by an internal combustion engine, comprising:
    a pump housing (1) with an axially supplying inlet (13) and a radially discharging first outlet (11) for a main conveying circuit which are connected to a pump chamber (10) of the pump housing (1),
    a pump impeller (2) for conveying coolant, which is rotatably accommodated on a pump shaft (3) in the pump chamber (10) and is driven via a belt drive (4),
    a hydraulic control circuit (5) derived from the coolant, with an auxiliary pump (6) on the input side, a proportional valve (7) on the output side and a regulating slide (8) as a hydraulic actuator for limiting the flow of the main conveying circuit, wherein, in order to radially shield the pump impeller (2), a cylindrical section of the regulating slide (8) is axially displaceable in the pump chamber (10) against a reset force by means of a pressure in the hydraulic control circuit (5); and
    a second outlet (12) for a secondary conveying circuit which is connected to the pump chamber (10);
    characterized in that
    a regulating valve (9), as a hydraulic actuator for limiting the flow of the secondary conveying circuit, is connected to the hydraulic control circuit (5), wherein actuations of the regulating slide (8) and of the regulating valve (9) are assigned or associated to respective pressure ranges within the hydraulic control circuit (5).
  2. The controllable coolant pump according to Claim 1, wherein
    the regulating valve (9), as a branched-off hydraulic actuator between the auxiliary pump (6) and the proportional valve (7), is connected to the hydraulic control circuit (5) and is closed against a reset force by means of the pressure in the hydraulic control circuit (5).
  3. The controllable coolant pump according to Claim 1 or 2, wherein
    the regulating valve (9) is configured as a seat valve which is biased by a spring in the opening direction.
  4. The controllable coolant pump according to any of Claims 1 to 3, wherein
    a piston surface for receiving a hydraulic positioning force of the regulating valve (9) in the hydraulic control circuit (5) is smaller than a piston surface of the regulating slide (8) in the hydraulic control circuit (5).
  5. The controllable coolant pump according to Claim 4, wherein
    the surface ratio of the piston surface of the regulating valve (9) to the piston surface of the regulating slide (8) is approximately 1:3.
  6. The controllable coolant pump according to any of Claims 1 to 5, wherein
    the regulating valve (9) is disposed in the second outlet (12) on the pump housing (1).
  7. The controllable coolant pump according to any of Claims 1 to 6, wherein
    a pressure valve (15) is provided between the main conveying flow and the secondary conveying flow, which opens from a predetermined pressure difference between a higher pressure in the main conveying flow and a lower pressure in the secondary conveying flow.
  8. The controllable coolant pump according to Claim 7, wherein
    the pressure valve (15) is configured as a check valve which is biased by a spring in the closing direction.
  9. The controllable coolant pump according to Claim 7 or 8, wherein
    the pressure valve (15) opens out downstream of the regulating slide (8) into the main conveying circuit and upstream of the regulating valve (9) into the secondary conveying circuit.
EP18740810.9A 2017-09-01 2018-07-12 Controllable coolant pump for a main delivery circuit and a secondary delivery circuit Active EP3676498B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102017120191.2A DE102017120191B3 (en) 2017-09-01 2017-09-01 Controllable coolant pump for main and secondary conveying circuit
PCT/EP2018/068958 WO2019042644A1 (en) 2017-09-01 2018-07-12 Controllable coolant pump for a main delivery circuit and a secondary delivery circuit

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EP3676498A1 EP3676498A1 (en) 2020-07-08
EP3676498B1 true EP3676498B1 (en) 2021-06-09

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EP18740810.9A Active EP3676498B1 (en) 2017-09-01 2018-07-12 Controllable coolant pump for a main delivery circuit and a secondary delivery circuit

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US (1) US11002281B2 (en)
EP (1) EP3676498B1 (en)
CN (1) CN111051702B (en)
BR (1) BR112019028100A2 (en)
DE (1) DE102017120191B3 (en)
WO (1) WO2019042644A1 (en)

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US11002281B2 (en) 2021-05-11
US20200340482A1 (en) 2020-10-29
WO2019042644A1 (en) 2019-03-07
CN111051702A (en) 2020-04-21
CN111051702B (en) 2021-09-14
BR112019028100A2 (en) 2020-07-28
EP3676498A1 (en) 2020-07-08
DE102017120191B3 (en) 2018-12-06

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