EP1943423A1 - Pump arrangement - Google Patents

Pump arrangement

Info

Publication number
EP1943423A1
EP1943423A1 EP06805431A EP06805431A EP1943423A1 EP 1943423 A1 EP1943423 A1 EP 1943423A1 EP 06805431 A EP06805431 A EP 06805431A EP 06805431 A EP06805431 A EP 06805431A EP 1943423 A1 EP1943423 A1 EP 1943423A1
Authority
EP
European Patent Office
Prior art keywords
shaft
pump
actuator
arrangement according
rotor hub
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP06805431A
Other languages
German (de)
French (fr)
Other versions
EP1943423B1 (en
Inventor
Heiko Schulz-Andres
Dirk Kamarys
Olaf Rische
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Magna Powertrain Hueckeswagen GmbH
Original Assignee
Ixetic Hueckeswagen GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Ixetic Hueckeswagen GmbH filed Critical Ixetic Hueckeswagen GmbH
Publication of EP1943423A1 publication Critical patent/EP1943423A1/en
Application granted granted Critical
Publication of EP1943423B1 publication Critical patent/EP1943423B1/en
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0057—Driving elements, brakes, couplings, transmission specially adapted for machines or pumps
    • F04C15/0061—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
    • F04C15/0073—Couplings between rotors and input or output shafts acting by interengaging or mating parts, i.e. positive coupling of rotor and shaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C11/00—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations
    • F04C11/001—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations of similar working principle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/02—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations specially adapted for several machines or pumps connected in series or in parallel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/06—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations specially adapted for stopping, starting, idling or no-load operation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M1/00—Pressure lubrication
    • F01M1/02—Pressure lubrication using lubricating pumps
    • F01M2001/0207—Pressure lubrication using lubricating pumps characterised by the type of pump
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M1/00—Pressure lubrication
    • F01M1/02—Pressure lubrication using lubricating pumps
    • F01M2001/0207—Pressure lubrication using lubricating pumps characterised by the type of pump
    • F01M2001/0238—Rotary pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M1/00—Pressure lubrication
    • F01M1/02—Pressure lubrication using lubricating pumps
    • F01M2001/0253—Pressure lubrication using lubricating pumps characterised by the pump driving means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/12—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C2/14—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F04C2/18—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with similar tooth forms
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2270/00—Control; Monitoring or safety arrangements
    • F04C2270/19—Temperature
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2270/00—Control; Monitoring or safety arrangements
    • F04C2270/56—Number of pump/machine units in operation

Definitions

  • the invention relates to a pump arrangement, in particular for lubricating oil pumps for internal combustion engines, with at least two pump devices, wherein the pump devices can promote each other independently.
  • two-stage pressure-controlled pumps are known, with two internal gear pumps operate in parallel, the second stage from a certain oil pressure (of about 3 bar) back into the intake of the pump.
  • a certain oil pressure of about 3 bar
  • a pump arrangement in particular for lubricating oil pumps for internal combustion engines, with at least two pump devices, which are arranged on a common drive shaft, but can independently convey, and wherein the first pump is always rotationally connected to the drive shaft, wherein the at least second pump via a temperature-dependent actuated rotary drive connection to the shaft or the rotor of the first pump is connectable.
  • the inventive idea is to present an at least two-stage pump in which one stage delivers continuously and the other depending on the temperature is switched on or off to save power.
  • Two fixed displacement pumps eg gerotor or external gear pumps
  • the two pumps are separated.
  • the idea is to connect one pump firmly to the drive shaft and the other with the help of a temperature-dependent shaft-hub connection to switch. Once the required switching temperature has been reached, the second pump stage becomes active and both volumetric flows are available to the consumer.
  • An inventive pump arrangement is characterized in that the at least second pump is connected by a temperature-dependent variable actuator, in particular by a volume expansion of an actuator body at a temperature rise.
  • a pump arrangement in which the actuator produces a shaft-hub connection in a force-locking manner. Furthermore, a pump arrangement is preferred in which the actuator produces a positive shaft-hub connection.
  • the shaft-hub connection can thus be executed positively or non-positively. When a certain temperature is exceeded, the connection is established and released when falling below.
  • Another inventive pump arrangement is characterized in that within the second pump, a first cone is arranged on the shaft and a second cone in the pump rotor hub is arranged, wherein the actuator expands axially when the temperature increases and the second cone in the axial direction against presses the first cone.
  • a pump is preferred in which between the shaft and the rotor hub within the rotor hub, a cylindrical recess is arranged with two conical clamping sleeves, which move with axial expansion of the actuator against each other and cause a radial contact between the shaft and rotor hub.
  • a pump arrangement is preferred in which in the second pump, the shaft has a radial recess for receiving a radially expandable actuator, which is surrounded by a slotted sleeve, so that when radially expanding the actuator, the slotted sleeve expands in its circumference and a Press connection between actuator and rotor hub manufactures.
  • a pump arrangement is preferred in which on the shaft, a cylindrical annular body is arranged as an expansion element within a slotted sleeve, so that upon radial expansion of the annular body, the slotted sleeve expands in its circumference and produces a press connection between the actuator and rotor hub.
  • a further pump arrangement according to the invention is characterized in that an actuator is arranged in the rotor hub, which presses a ball against a return spring in a tapered seat in the rotor hub with temperature increase, so that the ball is pressed over the conical seat against the shaft and thus a Clamping force generated between rotor hub and shaft.
  • a pump arrangement is preferred in which within the second pump in a recess of the shaft radially extendable pins or elements with conical / conical ends are arranged, which are radially retractable by spring forces in the shaft, wherein by an axially within the recess of the shaft extendable actuator, which also has a tapered end which presses against the tapered ends of the pins, the elements can extend radially when deflecting the actuator by deflecting the forces at the tapered ends and engage in radial openings of the hub of the pump rotor.
  • a pump arrangement in which in the second pump in an axial recess of the shaft, a cup-shaped expansion body is arranged with a conical shape with radially deflectable Spreizarmen in a conical shape, wherein the radially deflectable spreader arms through slots in the shaft in recesses of the Rotomabe can engage when an axially disposed within the recess of the shaft extendable actuator having a tapered or a spherical end, so that the radially deflectable spreader presses through the slots in the shaft in the rotor hub.
  • the spreading arms move back into the shaft by their springback force.
  • FIG. 1 shows a second pump with an axially acting cone connection.
  • FIG. 2 shows a second pump with a radially acting conical connection.
  • FIG. 3 shows a second pump with a radially acting expansion element.
  • FIG. 4 shows a second pump with an annular expansion element.
  • FIG. 5 shows a second pump with an expansion element in the hub.
  • FIG. 6 shows a second pump with an expansion element in the shaft and radially acting pins.
  • FIG. 7 shows a second pump with an expansion element in the shaft and a pot-shaped expansion body.
  • FIG. 8 shows two pumps with a displaceable intermediate plate.
  • the so-called second pump which is temperature-dependent connectable to the shaft, shown as a gear pump with a gear 1.
  • the gear 1 is mounted on a shaft 2, which has a cone 4 at its end.
  • the hub of the gear 1 has a conical end portion 6, which rests on the conical end portion 4 of the shaft 2.
  • a support cap 8 is further arranged.
  • a sleeve 10 is arranged, which partially surrounds an annular expansion element 12. When the temperature increases, this element 12 expands and thus frictionally jammed the gear 1 with the shaft 2.
  • FIG. 2 shows a further clamping cone connection by means of an expansion element.
  • a cup-shaped recess 16 is arranged within a gear 14.
  • the pot-shaped recess 16 includes two conically shaped, mutually displaceable rings 18.
  • a stretchable element 22 is arranged, which expands upon temperature increase and the two conical rings 18 moves against each other.
  • a radial clamping force By the conical clamping rings 18 so there is a force deflection between the axially expanding expansion element 22 and the radially to be clamped parts of the gear 14 and the shaft 24 instead.
  • a radially extendable expansion element 30 is arranged in a radial bore 26 of a shaft 28.
  • the shaft 28 is further surrounded by a slotted sleeve 32 in the region of the expansion element 30.
  • the slotted sleeve 32 is pressed against the hub of the gear 34 and thus produces a frictional connection between the expansion element 30 and thus the shaft 28 and the gear 34.
  • an annular expansion element 36 is arranged in an annular recess 38 of the shaft 40.
  • the expansion element 36 is in turn surrounded by a slotted clamping sleeve 42.
  • the expansion element 36 arranged on the shaft 40 expands substantially radially when the temperature increases. During this expansion, it spreads the slotted sleeve 42. Again, the torque is transmitted to the gear 44 in turn by the resulting frictional force.
  • a temperature-dependent actuator 46 is arranged in a recess in the hub 48 of a toothed wheel 50.
  • the actuator 46 when expanded by increasing the temperature, presses a ball 52 into a conical seat 54 such that the ball 52 is pressed more firmly against the surface of the shaft 56, thus producing an increasing frictional force.
  • the ball within the conical seat 54 is pushed back by a spring 58 and repealed the frictional force. Again, the actuator force is deflected by the ball and the conical seat 54.
  • FIG. 6 shows a form-fitting connection with a temperature-dependent adjustable actuator.
  • a temperature-controlled actuator 62 is arranged, which acts on a conical element 64 in axial expansion.
  • a return spring 66 presses on cooling the conical member 64 and thus the actuator 62 back to its original position.
  • the conical element 64 in turn presses on tapered ends 70 of cylindrical pins 68, which thus extend radially from the shaft 60 and retract into radial openings 74 of a gear 76 at temperature elevation.
  • a positive connection between the shaft 60 and the gear 76 is produced.
  • the cylindrical pins 68 are returned by return springs 72 back into the shaft.
  • the springs 72 also prevent the extension of the cylindrical pins 68 by centrifugal force.
  • the torque between the shaft 60 and the gear 76 is thus transmitted in this arrangement by positive engagement.
  • a corresponding positive connection is produced by a so-called expansion element 78.
  • a temperature-dependent expansion element 82 is arranged in a recess of a shaft 80.
  • the expansion element 82 here has a spherical segment-shaped actuating body 84 which presses against spreading arms 86 of the expansion body 78 when the temperature-dependent element 82 extends under an increase in temperature.
  • the spreader arms 86 are pressed through openings 88 in the shaft in recesses 90 of a gear 92 and thus take the gear 92 in the rotary motion positively.
  • a return spring 94 ensures the retraction of the actuator 82 and the actuator body 84 in the cooled state, wherein the spreader arms 86 in turn spring back from the recesses 90 of the gear 92 in the shaft 80 and the frictional connection is released again due to their return spring force.
  • a further possibility of coupling the second pump to the shaft could consist of a combination of a shaft-hub connection and a valve 95, as indicated in FIG.
  • the separation of the two pumps 96 and 98 takes place via a loosely inserted intermediate plate 100.
  • the advantage of a loosely inserted plate 100 is the improvement in volumetric efficiency due to the reduction of the gap. Due to the temperature-dependent switching of the valve 95, the disc 100 is axially displaced against the pump 98 due to the pressurization of the pressure plate 100, the suction and pressure surfaces on the side of the pump 96 are now completely under system pressure. This displacement minimizes the column of the fixed stage 98, while the overall stage 96 rotates under pressure with large gaps, without promoting and thus absorbs only minimal power.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Eye Examination Apparatus (AREA)
  • Details Of Reciprocating Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)

Abstract

The invention relates to a pump arrangement, in particular for lubricating oil pumps for internal combustion engines, having at least two pump devices which are arranged on a common driveshaft but can feed independently of one another, wherein the first pump is always connected to the driveshaft so as to be driven in rotation, and wherein the second pump (1) can be connected to the shaft (2) or to the rotor of the first pump by means of a rotary drive connection (12) which can be actuated as a function of temperature.

Description

Pumpenanordnung pump assembly
Die Erfindung betrifft eine Pumpenanordnung, insbesondere für Schmierölpumpen für Verbrennungsmotoren, mit mindestens zwei Pumpenvorrichtungen, wobei die Pumpenvorrichtungen voneinander unabhängig fördern können. So sind im Stand der Technik zweistufige druckgeregelte Pumpen bekannt, wobei zwei Innenzahnradpumpen parallel arbeiten, wobei die zweite Stufe ab einem bestimmten Öldruck (von ca. 3 bar) in den Ansaugbereich der Pumpe zurückfördert. Bei diesen Konzepten treten volumetrische Verluste auf, die durch das Umfördern des nicht benötigten Volumenstroms anfallen. Hinzu kommen mechanische Verluste in Folge der relativ großen Reibradien der verwendeten Innenzahnradpumpen.The invention relates to a pump arrangement, in particular for lubricating oil pumps for internal combustion engines, with at least two pump devices, wherein the pump devices can promote each other independently. Thus, in the prior art two-stage pressure-controlled pumps are known, with two internal gear pumps operate in parallel, the second stage from a certain oil pressure (of about 3 bar) back into the intake of the pump. In these concepts occur volumetric losses incurred by the Umzufördern the unused volume flow. In addition, there are mechanical losses as a result of the relatively large friction radii of the internal gear pumps used.
Es ist Aufgabe der Erfindung, eine Pumpenanordnung darzustellen, die diese Nachteile nicht aufweist.It is an object of the invention to present a pump assembly which does not have these disadvantages.
Die Aufgabe wird gelöst durch eine Pumpenanordnung, insbesondere für Schmierölpumpen für Verbrennungsmotoren, mit mindestens zwei Pumpenvorrichtungen, welche auf einer gemeinsamen Antriebswelle angeordnet sind, aber von einander unabhängig fördern können, und wobei die erste Pumpe immer drehangetrieben mit der Antriebswelle verbunden ist, wobei die mindestens zweite Pumpe über eine temperaturabhängig betätigbare Drehantriebsverbindung mit der Welle oder dem Rotor der ersten Pumpe verbindbar ist.The object is achieved by a pump arrangement, in particular for lubricating oil pumps for internal combustion engines, with at least two pump devices, which are arranged on a common drive shaft, but can independently convey, and wherein the first pump is always rotationally connected to the drive shaft, wherein the at least second pump via a temperature-dependent actuated rotary drive connection to the shaft or the rotor of the first pump is connectable.
Die erfinderische Idee ist dabei, eine mindestens zweitstufige Pumpe darzustellen, bei der eine Stufe kontinuierlich fördert und die andere je nach Temperatur zu- oder abgeschaltet wird, um Leistung einzusparen. Es werden zwei Konstantpumpen (z. B. Gerotor- oder Außenzahnrad- pumpen) verwendet. Die beiden Teilpumpen sind voneinander getrennt.The inventive idea is to present an at least two-stage pump in which one stage delivers continuously and the other depending on the temperature is switched on or off to save power. Two fixed displacement pumps (eg gerotor or external gear pumps) are used. The two pumps are separated.
Bevorzugt wird eine Pumpenanordnung, bei welcher die temperaturabhängig betätigbare Drehantriebsverbindung zwischen der Welle und einer Rotornabe der zweiten Pumpe angeordnet ist. Die Idee ist also, die eine Pumpe fest mit der Antriebswelle zu verbinden und die andere mit Hilfe einer temperaturabhängigen Wellen-Naben-Verbindung dazu zu schalten. Ist die notwendige Schalttemperatur erreicht, wird die zweite Pumpenstufe aktiv, und beide Volumenströme stehen dem Verbraucher zur Verfügung. Eine erfinderische Pumpenanordnung zeichnet sich dadurch aus, dass die mindestens zweite Pumpe durch einen temperaturabhängig veränderbaren Aktor, insbesondere durch eine Volumenausdehnung eines Aktorkörpers bei einem Temperaturanstieg, hinzugeschaltet wird.Preference is given to a pump arrangement in which the temperature-dependent actuated rotary drive connection between the shaft and a rotor hub of the second pump is arranged. The idea is to connect one pump firmly to the drive shaft and the other with the help of a temperature-dependent shaft-hub connection to switch. Once the required switching temperature has been reached, the second pump stage becomes active and both volumetric flows are available to the consumer. An inventive pump arrangement is characterized in that the at least second pump is connected by a temperature-dependent variable actuator, in particular by a volume expansion of an actuator body at a temperature rise.
Bevorzugt wird auch eine Pumpenanordnung, bei welcher der Aktor eine Wellen-Naben-Verbindung kraftschlüssig herstellt. Weiterhin wird eine Pumpenanordnung bevorzugt, bei welcher der Aktor eine formschlüssige Wellen-Naben-Verbindung herstellt. Die Wellen-Nabenverbindung kann also formschlüssig oder kraftschlüssig ausgeführt werden. Beim Überschreiten einer bestimmten Temperatur wird die Verbindung hergestellt und beim Unterschreiten wieder gelöst.Also preferred is a pump arrangement in which the actuator produces a shaft-hub connection in a force-locking manner. Furthermore, a pump arrangement is preferred in which the actuator produces a positive shaft-hub connection. The shaft-hub connection can thus be executed positively or non-positively. When a certain temperature is exceeded, the connection is established and released when falling below.
Eine weitere erfinderische Pumpenanordnung zeichnet sich dadurch aus, dass innerhalb der zweiten Pumpe ein erster Konus auf der Welle angeordnet ist und ein zweiter Konus in der Pum- penrotornabe angeordnet ist, wobei der Aktor sich bei Temperaturerhöhung axial ausdehnt und den zweiten Konus in axialer Richtung gegen den ersten Konus presst.Another inventive pump arrangement is characterized in that within the second pump, a first cone is arranged on the shaft and a second cone in the pump rotor hub is arranged, wherein the actuator expands axially when the temperature increases and the second cone in the axial direction against presses the first cone.
Weiterhin wird eine Pumpe bevorzugt, bei welcher zwischen der Welle und der Rotornabe innerhalb der Rotornabe eine zylindrische Ausnehmung mit zwei konischen Spannhülsen angeordnet ist, welche bei axialer Ausdehnung des Aktors sich gegeneinander verschieben und eine radiale Anpressung zwischen Welle und Rotornabe bewirken.Furthermore, a pump is preferred in which between the shaft and the rotor hub within the rotor hub, a cylindrical recess is arranged with two conical clamping sleeves, which move with axial expansion of the actuator against each other and cause a radial contact between the shaft and rotor hub.
Auch wird eine Pumpenanordnung bevorzugt, bei welcher in der zweiten Pumpe die Welle eine radiale Ausnehmung zur Aufnahme eines radial ausdehnbaren Aktors aufweist, welcher von einer geschlitzten Hülse umgeben ist, so dass bei radialer Ausdehnung des Aktors die geschlitzte Hülse sich in ihrem Umfang ausdehnt und eine Pressverbindung zwischen Aktor und Rotornabe herstellt. Ebenso wird eine Pumpenanordnung bevorzugt, bei welcher auf der Welle ein zylindrischer Ringkörper als Dehnelement innerhalb einer geschlitzten Hülse angeordnet ist, so dass bei radialer Ausdehnung des Ringkörpers die geschlitzte Hülse sich in ihrem Umfang ausdehnt und eine Pressverbindung zwischen Aktor und Rotornabe herstellt.Also, a pump arrangement is preferred in which in the second pump, the shaft has a radial recess for receiving a radially expandable actuator, which is surrounded by a slotted sleeve, so that when radially expanding the actuator, the slotted sleeve expands in its circumference and a Press connection between actuator and rotor hub manufactures. Likewise, a pump arrangement is preferred in which on the shaft, a cylindrical annular body is arranged as an expansion element within a slotted sleeve, so that upon radial expansion of the annular body, the slotted sleeve expands in its circumference and produces a press connection between the actuator and rotor hub.
Eine weitere erfindungsgemäße Pumpenanordnung zeichnet sich dadurch aus, dass in der Rotornabe ein Aktor angeordnet ist, welcher bei Temperaturerhöhung eine Kugel gegen eine Rückstellfeder in einen kegeligen Sitz in der Rotornabe presst, so dass die Kugel über den Kegelsitz gegen die Welle gepresst wird und somit eine Klemmkraft zwischen Rotornabe und Welle erzeugt. Weiterhin wird eine Pumpenanordnung bevorzugt, bei welcher innerhalb der zweiten Pumpe in einer Ausnehmung der Welle radial ausfahrbare Stifte bzw. Elemente mit kegeligen/konischen Enden angeordnet sind, welche durch Federkräfte radial in die Welle einfahrbar sind, wobei durch einen axial innerhalb der Ausnehmung der Welle ausfahrbaren Aktor, der ebenfalls ein kegeliges Ende aufweist, welches gegen die kegeligen Enden der Stifte drückt, die Elemente beim Ausfahren des Aktors durch Umlenkung der Kräfte an den kegeligen Enden radial ausfahren können und in radiale Öffnungen der Nabe des Pumpenrotors eingreifen.A further pump arrangement according to the invention is characterized in that an actuator is arranged in the rotor hub, which presses a ball against a return spring in a tapered seat in the rotor hub with temperature increase, so that the ball is pressed over the conical seat against the shaft and thus a Clamping force generated between rotor hub and shaft. Furthermore, a pump arrangement is preferred in which within the second pump in a recess of the shaft radially extendable pins or elements with conical / conical ends are arranged, which are radially retractable by spring forces in the shaft, wherein by an axially within the recess of the shaft extendable actuator, which also has a tapered end which presses against the tapered ends of the pins, the elements can extend radially when deflecting the actuator by deflecting the forces at the tapered ends and engage in radial openings of the hub of the pump rotor.
Ebenso wird eine Pumpenanordnung bevorzugt, bei welcher in der zweiten Pumpe in einer axialen Ausnehmung der Welle ein topfförmiger Spreizkörper mit einer konischen Ausformung mit radial auslenkbaren Spreizarmen in einer konischen Ausformung angeordnet ist, wobei die radial auslenkbaren Spreizarme durch Schlitze in der Welle in Ausnehmungen der Rotomabe eingreifen können, wenn ein axial innerhalb der Ausnehmung der Welle ausfahrbar angeordneter Aktor, der ein kegeliges oder ein kugeliges Ende aufweist, damit die radial auslenkbaren Spreizarme durch die Schlitze in der Welle in die Rotornabe drückt. Beim Einfahren des Aktors bewegen sich die Spreizarme durch ihre Rückfederkraft zurück in die Welle.Similarly, a pump arrangement is preferred in which in the second pump in an axial recess of the shaft, a cup-shaped expansion body is arranged with a conical shape with radially deflectable Spreizarmen in a conical shape, wherein the radially deflectable spreader arms through slots in the shaft in recesses of the Rotomabe can engage when an axially disposed within the recess of the shaft extendable actuator having a tapered or a spherical end, so that the radially deflectable spreader presses through the slots in the shaft in the rotor hub. When retracting the actuator, the spreading arms move back into the shaft by their springback force.
Die Erfindung wird nun anhand der Figuren beschrieben.The invention will now be described with reference to the figures.
Figur 1 zeigt eine zweite Pumpe mit einer axial wirkenden Konusverbindung.FIG. 1 shows a second pump with an axially acting cone connection.
Figur 2 zeigt eine zweite Pumpe mit einer radial wirkenden Konusverbindung.FIG. 2 shows a second pump with a radially acting conical connection.
Figur 3 zeigt eine zweite Pumpe mit einem radial wirkenden Dehnelement.FIG. 3 shows a second pump with a radially acting expansion element.
Figur 4 zeigt eine zweite Pumpe mit einem ringförmigen Dehnelement.FIG. 4 shows a second pump with an annular expansion element.
Figur 5 zeigt eine zweite Pumpe mit einem Dehnelement in der Nabe.FIG. 5 shows a second pump with an expansion element in the hub.
Figur 6 zeigt eine zweite Pumpe mit einem Dehnelement in der Welle und radial wirkenden Stiften.FIG. 6 shows a second pump with an expansion element in the shaft and radially acting pins.
Figur 7 zeigt eine zweite Pumpe mit einem Dehnelement in der Welle und einen topf- förmigen Spreizkörper. Figur 8 zeigt zwei Pumpen mit einer verschiebbaren Zwischenplatte.FIG. 7 shows a second pump with an expansion element in the shaft and a pot-shaped expansion body. FIG. 8 shows two pumps with a displaceable intermediate plate.
In Figur 1 ist die so genannte zweite Pumpe, welche temperaturabhängig mit der Welle verbindbar ist, als Zahnradpumpe mit einem Zahnrad 1 dargestellt. Das Zahnrad 1 ist auf einer Welle 2 gelagert, welche an ihrem Ende einen Konus 4 aufweist. Ebenso weist die Nabe des Zahnrades 1 einen konischen Endteil 6 auf, welcher auf dem konischen Endteil 4 der Welle 2 aufliegt. Am Wellenende ist weiterhin eine Abstützkappe 8 angeordnet. Innerhalb der Abstützkappe 8 ist eine Hülse 10 angeordnet, die teilweise ein ringförmiges Dehnelement 12 umgibt. Bei Temperaturerhöhung dehnt sich dieses Element 12 aus und verklemmt damit kraftschlüssig das Zahnrad 1 mit der Welle 2.In Figure 1, the so-called second pump, which is temperature-dependent connectable to the shaft, shown as a gear pump with a gear 1. The gear 1 is mounted on a shaft 2, which has a cone 4 at its end. Likewise, the hub of the gear 1 has a conical end portion 6, which rests on the conical end portion 4 of the shaft 2. At the end of the shaft, a support cap 8 is further arranged. Within the support cap 8, a sleeve 10 is arranged, which partially surrounds an annular expansion element 12. When the temperature increases, this element 12 expands and thus frictionally jammed the gear 1 with the shaft 2.
In Figur 2 ist eine weitere Klemmkonusverbindung mittels eines Dehnelements dargestellt. Innerhalb eines Zahnrades 14 ist eine topfförmige Ausnehmung 16 angeordnet. Die topfförmige Ausnehmung 16 enthält zwei konisch geformte, gegeneinander verschiebbare Ringe 18. Innerhalb einer Führungshülse 20 ist wiederum ein dehnbares Element 22 angeordnet, welches sich bei Temperaturerhöhung ausdehnt und die beiden konischen Ringe 18 gegeneinander verschiebt. Dadurch wirkt zwischen dem Zahnrad 14 und der Welle 24 eine radiale Klemmkraft. Durch die konischen Spannringe 18 findet also eine Kraftumlenkung zwischen dem sich axial ausdehnenden Dehnelement 22 und den radial zu verspannenden Teilen des Zahnrades 14 und der Welle 24 statt.FIG. 2 shows a further clamping cone connection by means of an expansion element. Within a gear 14, a cup-shaped recess 16 is arranged. The pot-shaped recess 16 includes two conically shaped, mutually displaceable rings 18. Within a guide sleeve 20, in turn, a stretchable element 22 is arranged, which expands upon temperature increase and the two conical rings 18 moves against each other. As a result, between the gear 14 and the shaft 24 acts a radial clamping force. By the conical clamping rings 18 so there is a force deflection between the axially expanding expansion element 22 and the radially to be clamped parts of the gear 14 and the shaft 24 instead.
In Figur 3 ist in einer radialen Bohrung 26 einer Welle 28 ein radial ausfahrbares Dehnelement 30 angeordnet. Die Welle 28 wird weiterhin im Bereich des Dehnelements 30 von einer geschlitzten Hülse 32 umgeben. Bei Ausdehnung des Dehnelements 30 durch Temperaturerhöhung wird die geschlitzte Hülse 32 gegen die Nabe des Zahnrades 34 gepresst und somit eine kraftschlüssige Verbindung zwischen dem Dehnelement 30 und damit der Welle 28 und dem Zahnrad 34 hergestellt.In FIG. 3, a radially extendable expansion element 30 is arranged in a radial bore 26 of a shaft 28. The shaft 28 is further surrounded by a slotted sleeve 32 in the region of the expansion element 30. Upon expansion of the expansion element 30 by increasing the temperature, the slotted sleeve 32 is pressed against the hub of the gear 34 and thus produces a frictional connection between the expansion element 30 and thus the shaft 28 and the gear 34.
In Figur 4 wird ein ringförmiges Dehnelement 36 in einer ringförmigen Ausnehmung 38 der Welle 40 angeordnet. Das Dehnelement 36 ist wiederum von einer geschlitzten Spannhülse 42 umgeben. Das auf der Welle 40 angeordnete Dehnelement 36 dehnt sich bei Temperaturerhöhung im Wesentlichen radial aus. Während dieser Ausdehnung spreizt es die geschlitzte Hülse 42 auf. Auch hier wird das Drehmoment auf das Zahnrad 44 wiederum durch die so entstehende Reibkraft übertragen. In Figur 5 ist ein temperaturabhängig wirkender Aktor 46 in einer Ausnehmung in der Nabe 48 eines Zahnrades 50 angeordnet. Der Aktor 46 presst bei Ausdehnung durch Temperaturerhöhung eine Kugel 52 in einen konischen Sitz 54 dergestalt, dass die Kugel 52 fester gegen die Oberfläche der Welle 56 gepresst wird und somit eine ansteigende Reibungskraft erzeugt. Im abgekühlten Zustand des Aktors 46 wird durch eine Feder 58 die Kugel innerhalb des kegeligen Sitzes 54 wieder zurückgedrückt und die Reibkraft aufgehoben. Auch hier wird die Aktorkraft durch die Kugel und den kegeligen Sitz 54 umgelenkt.In FIG. 4, an annular expansion element 36 is arranged in an annular recess 38 of the shaft 40. The expansion element 36 is in turn surrounded by a slotted clamping sleeve 42. The expansion element 36 arranged on the shaft 40 expands substantially radially when the temperature increases. During this expansion, it spreads the slotted sleeve 42. Again, the torque is transmitted to the gear 44 in turn by the resulting frictional force. In FIG. 5, a temperature-dependent actuator 46 is arranged in a recess in the hub 48 of a toothed wheel 50. The actuator 46, when expanded by increasing the temperature, presses a ball 52 into a conical seat 54 such that the ball 52 is pressed more firmly against the surface of the shaft 56, thus producing an increasing frictional force. In the cooled state of the actuator 46, the ball within the conical seat 54 is pushed back by a spring 58 and repealed the frictional force. Again, the actuator force is deflected by the ball and the conical seat 54.
In Figur 6 ist eine formschlüssig wirkende Verbindung mit einem temperaturabhängig verstellbaren Aktor dargestellt. Innerhalb einer Ausnehmung der Welle 60 ist ein temperaturgeregelter Aktor 62 angeordnet, welcher bei axialer Ausdehnung auf ein kegeliges Element 64 wirkt. Eine Rückstellfeder 66 drückt bei Abkühlung das kegelige Element 64 und damit den Aktor 62 in seine Ausgangsposition zurück. Das kegelige Element 64 drückt wiederum auf kegelige Enden 70 von zylindrischen Stiften 68, welche bei Temperaturerhöhung somit aus der Welle 60 radial ausfahren und in radiale Öffnungen 74 eines Zahnrades 76 einfahren. Somit wird eine formschlüssige Verbindung zwischen der Welle 60 und dem Zahnrad 76 hergestellt. Bei abgekühltem Aktor und zurückgefahrenem Kegelelement 64 werden die zylindrischen Stifte 68 durch Rückstellfedern 72 wieder in die Welle zurückgefahren. Die Federn 72 verhindern auch das Ausfahren der zylindrischen Stifte 68 durch Fliehkraft. Das Moment zwischen der Welle 60 und dem Zahnrad 76 wird also in dieser Anordnung durch Formschluss übertragen.FIG. 6 shows a form-fitting connection with a temperature-dependent adjustable actuator. Within a recess of the shaft 60, a temperature-controlled actuator 62 is arranged, which acts on a conical element 64 in axial expansion. A return spring 66 presses on cooling the conical member 64 and thus the actuator 62 back to its original position. The conical element 64 in turn presses on tapered ends 70 of cylindrical pins 68, which thus extend radially from the shaft 60 and retract into radial openings 74 of a gear 76 at temperature elevation. Thus, a positive connection between the shaft 60 and the gear 76 is produced. When cooled actuator and retracted cone element 64, the cylindrical pins 68 are returned by return springs 72 back into the shaft. The springs 72 also prevent the extension of the cylindrical pins 68 by centrifugal force. The torque between the shaft 60 and the gear 76 is thus transmitted in this arrangement by positive engagement.
In Figur 7 wird ein entsprechender Formschluss durch ein so genanntes Spreizelement 78 hergestellt. In einer Ausnehmung einer Welle 80 ist wiederum ein temperaturabhängig reagierendes Dehnelement 82 angeordnet. Das Dehnelement 82 besitzt hier einen kugelabschnittsförmigen Betätigungskörper 84, der gegen Spreizarme 86 des Spreizkörpers 78 drückt, wenn das temperaturabhängige Element 82 unter Temperaturerhöhung ausfährt. Dabei werden die Spreizarme 86 durch Öffnungen 88 in der Welle in Ausnehmungen 90 eines Zahnrades 92 gedrückt und nehmen somit das Zahnrad 92 in der Drehbewegung formschlüssig mit. Eine Rückstellfeder 94 sorgt für das Zurückfahren des Aktors 82 und des Betätigungskörpers 84 im abgekühlten Zustand, wobei die Spreizarme 86 aufgrund ihrer Rückfederkraft wiederum aus den Ausnehmungen 90 des Zahnrades 92 in die Welle 80 zurückfedern und die kraftschlüssige Verbindung wieder gelöst wird.In FIG. 7, a corresponding positive connection is produced by a so-called expansion element 78. In a recess of a shaft 80, in turn, a temperature-dependent expansion element 82 is arranged. The expansion element 82 here has a spherical segment-shaped actuating body 84 which presses against spreading arms 86 of the expansion body 78 when the temperature-dependent element 82 extends under an increase in temperature. In this case, the spreader arms 86 are pressed through openings 88 in the shaft in recesses 90 of a gear 92 and thus take the gear 92 in the rotary motion positively. A return spring 94 ensures the retraction of the actuator 82 and the actuator body 84 in the cooled state, wherein the spreader arms 86 in turn spring back from the recesses 90 of the gear 92 in the shaft 80 and the frictional connection is released again due to their return spring force.
Eine weiter Möglichkeit der Ankopplung der zweiten Pumpe an die Welle könnte über eine Kombination aus einer Wellen-Naben-Verbindung und einem Ventil 95 bestehen, wie in Figur 8 angedeutet. Die Trennung der beiden Pumpen 96 und 98 erfolgt über eine lose eingelegte Zwischen- platte 100. Der Vorteil einer lose eingelegten Platte 100 ist die Verbesserung des volumetrischen Wirkungsgrades durch die Verkleinerung der Spalte. Durch die temperaturabhängig erfolgende Schaltung des Ventils 95 wird die Scheibe 100 axial in Folge der Druckbeaufschlagung der Druckplatte 100, deren Saug- und Druckflächen auf der Seite der Pumpe 96 jetzt komplett unter Systemdruck stehen, gegen die Pumpe 98 verschoben. Diese Verschiebung minimiert die Spalte der festen Stufe 98, während die Stufe 96 insgesamt unter Druck mit großen Spalten umläuft, ohne zu fördern und damit nur minimale Leistung aufnimmt. A further possibility of coupling the second pump to the shaft could consist of a combination of a shaft-hub connection and a valve 95, as indicated in FIG. The separation of the two pumps 96 and 98 takes place via a loosely inserted intermediate plate 100. The advantage of a loosely inserted plate 100 is the improvement in volumetric efficiency due to the reduction of the gap. Due to the temperature-dependent switching of the valve 95, the disc 100 is axially displaced against the pump 98 due to the pressurization of the pressure plate 100, the suction and pressure surfaces on the side of the pump 96 are now completely under system pressure. This displacement minimizes the column of the fixed stage 98, while the overall stage 96 rotates under pressure with large gaps, without promoting and thus absorbs only minimal power.
BezuqszeichenlisteLIST OF REFERENCES
Zahnrad der zweiten PumpeGear of the second pump
Wellewave
Konus konischer Endteil der Nabe des Zahnrades 1Cone conical end part of the hub of the gear 1
Abstützkappesupport spoiler
Hülse ringförmiges DehnelementSleeve annular expansion element
Zahnrad topfförmige Ausnehmung konische, verschiebbare RingeGear cup-shaped recess conical, sliding rings
Führungshülse dehnbares ElementGuide sleeve expandable element
Welle radiale BohrungShaft radial bore
Welle radial ausfahrbares Dehnelement geschlitzte HülseShaft radially extendable expansion element slotted sleeve
Zahnrad ringförmiges Dehnelement ringförmige AusnehmungGear annular expansion element annular recess
Welle geschlitzte SpannhülseShaft slotted clamping sleeve
Zahnradgear
Nabehub
Zahnradgear
Kugel konischer SitzBall conical seat
Wellewave
Welle temperaturgeregelter Aktor kegeliges Element zylindrische Stifte kegelige Enden der zylindrischen Stifte 68 72 RückstellfedernShaft temperature controlled actuator tapered element cylindrical pins tapered ends of the cylindrical pins 68 72 return springs
74 radiale Öffnungen74 radial openings
76 Zahnrad76 gear
78 Spreizelement78 expansion element
80 Welle80 wave
82 temperaturabhängig reagierendes Dehnelement82 temperature-dependent reacting expansion element
84 kugelabschnittsförmiger Betätigungskörper84 spherical segment-shaped actuating body
86 Spreizarme86 spreading arms
88 Öffnungen in der Welle88 openings in the shaft
90 Ausnehmungen90 recesses
92 Zahnrad92 gear
94 Rückstellfeder94 return spring
95 Ventil95 valve
96 erste Pumpe96 first pump
98 zweite Pumpe98 second pump
100 lose eingelegte Zwischenplatte 100 loosely inserted intermediate plate

Claims

Patentansprüche claims
1. Pumpenanordnung, insbesondere für Schmierölpumpen für Verbrennungsmotoren, mit mindestens zwei Pumpenvorrichtungen, welche auf einer gemeinsamen Antriebswelle (2, 24, 28, 40, 56, 60, 80) angeordnet sind, aber voneinander unabhängig fördern können, und wobei die erste Pumpe immer drehangetrieben mit der Antriebswelle (2, 24, 28, 40, 56, 60, 80, 98) verbunden ist, dadurch gekennzeichnet, dass die mindestens zweite Pumpe über eine temperaturabhängig betätigbare Drehantriebsverbindung mit der Welle (2, 24, 28, 40, 56, 60, 80) oder dem Rotor der ersten Pumpe (98) verbindbar ist.A pump assembly, in particular for lubricating oil pumps for internal combustion engines, having at least two pumping devices, which on a common drive shaft (2, 24, 28, 40, 56, 60, 80) are arranged, but can promote each other independently, and wherein the first pump always rotationally connected to the drive shaft (2, 24, 28, 40, 56, 60, 80, 98), characterized in that the at least second pump via a temperature-dependent actuated rotary drive connection with the shaft (2, 24, 28, 40, 56 , 60, 80) or the rotor of the first pump (98) is connectable.
2. Pumpenanordnung nach Anspruch 1 , dadurch gekennzeichnet, dass die temperaturabhängig betätigbare Drehantriebsverbindung zwischen der Welle (2, 24, 28, 40, 56, 60, 80) und einer Rotornabe der zweiten Pumpe angeordnet ist.2. Pump arrangement according to claim 1, characterized in that the temperature-dependent operable rotary drive connection between the shaft (2, 24, 28, 40, 56, 60, 80) and a rotor hub of the second pump is arranged.
3. Pumpenanordnung nach Anspruch 1 oder Anspruch 2, dadurch gekennzeichnet, dass die mindestens zweite Pumpe durch einen temperaturabhängig veränderbaren Aktor (12, 22, 30, 36, 46, 62, 82) , insbesondere durch eine Volumenausdehnung eines Aktorkörpers bei einem Temperaturanstieg, hinzugeschaltet wird.3. Pump arrangement according to claim 1 or claim 2, characterized in that the at least second pump by a temperature-dependent variable actuator (12, 22, 30, 36, 46, 62, 82), in particular by a volume expansion of an actuator body at a temperature rise, connected becomes.
4. Pumpenanordnung nach Anspruch 1 bis Anspruch 3, dadurch gekennzeichnet, dass der Aktor (12, 22, 30, 36, 46) eine kraftschlüssige Wellen-Naben-Verbindung herstellt.4. Pump arrangement according to claim 1 to claim 3, characterized in that the actuator (12, 22, 30, 36, 46) produces a frictional shaft-hub connection.
5. Pumpenanordnung nach Anspruch 1 bis Anspruch 3, dadurch gekennzeichnet, dass der Aktor (62, 82) eine formschlüssige Wellen Naben-Verbindung herstellt.5. Pump arrangement according to claim 1 to claim 3, characterized in that the actuator (62, 82) produces a positive waves hub connection.
6. Pumpenanordnung nach Anspruch 4, dadurch gekennzeichnet, dass ein erster Konus (4) auf der Welle (2) angeordnet ist und ein zweiter Konus (6) in der Pumpenrotornabe angeordnet ist, wobei der Aktor (12) sich bei Temperaturerhöhung axial ausdehnt und den zweiten Konus (6) in axialer Richtung gegen den ersten Konus (4) presst.6. Pump arrangement according to claim 4, characterized in that a first cone (4) on the shaft (2) is arranged and a second cone (6) is arranged in the pump rotor hub, wherein the actuator (12) expands axially upon temperature increase and presses the second cone (6) in the axial direction against the first cone (4).
7. Pumpenanordnung nach Anspruch 4, dadurch gekennzeichnet, dass zwischen der Welle (24) und der Rotornabe innerhalb der Rotornabe eine zylindrische Ausnehmung mit zwei konischen Spannhülsen (18) angeordnet ist, welche bei axialer Ausdehnung des Aktors (22) sich gegeneinander verschieben und eine radiale Anpressung zwischen Welle (24) und Rotornabe bewirken. 7. Pump arrangement according to claim 4, characterized in that between the shaft (24) and the rotor hub within the rotor hub, a cylindrical recess with two conical clamping sleeves (18) is arranged, which move with axial extension of the actuator (22) against each other and a cause radial contact between the shaft (24) and rotor hub.
8. Pumpenanordnung nach Anspruch 4, dadurch gekennzeichnet, dass die Welle (28) eine radiale Ausnehmung zur Aufnahme eines radial ausdehnbaren Aktors (30) aufweist, welcher von einer geschlitzten Hülse (32) umgeben ist, so dass bei radialer Ausdehnung des Aktors (30) die geschlitzte Hülse (32) sich in ihrem Umfang ausdehnt und eine Pressverbindung zwischen dem Aktor (30) und der Rotornabe herstellt.8. Pump arrangement according to claim 4, characterized in that the shaft (28) has a radial recess for receiving a radially expandable actuator (30), which is surrounded by a slotted sleeve (32), so that with radial expansion of the actuator (30 ) the slotted sleeve (32) expands in circumference and establishes a press fit between the actuator (30) and the rotor hub.
9. Pumpenanordnung nach Anspruch 4, dadurch gekennzeichnet, dass auf der Welle (40) ein zylindrischer Ringkörper (36) als Dehnelement innerhalb einer geschlitzten Hülse (42) angeordnet ist, so dass bei radialer Ausdehnung des Ringkörpers (36) die geschlitzte Hülse (42) sich in ihrem Umfang ausdehnt und eine Pressverbindung zwischen Aktor (36) und Rotornabe herstellt.9. Pump arrangement according to claim 4, characterized in that on the shaft (40) a cylindrical annular body (36) is arranged as an expansion element within a slotted sleeve (42), so that with radial expansion of the annular body (36), the slotted sleeve (42 ) expands in its circumference and produces a press connection between actuator (36) and rotor hub.
10. Pumpenanordnung nach Anspruch 4, dadurch gekennzeichnet, dass in der Rotornabe ein Aktor (46) angeordnet ist, welcher bei Temperaturerhöhung eine Kugel (52) gegen eine Rückstellfeder (58) in einen Kegelsitz (54) in der Rotornabe presst, so dass die Kugel (52) über den Kegelsitz (54) gegen die Welle (56) gepresst wird und somit eine Klemmkraft zwischen Rotornabe und Welle (56) erzeugt.10. Pump arrangement according to claim 4, characterized in that in the rotor hub, an actuator (46) is arranged, which presses a temperature increase (52) against a return spring (58) in a conical seat (54) in the rotor hub, so that the Ball (52) via the conical seat (54) against the shaft (56) is pressed and thus generates a clamping force between the rotor hub and shaft (56).
11. Pumpenanordnung nach Anspruch 5, dadurch gekennzeichnet, dass in einer Ausnehmung der Welle (60) radial ausfahrbare Stifte (68) bzw. Elemente mit kegeligen/konischen Enden (70) angeordnet sind, welche durch Federkräfte radial in die Welle (60) einfahrbar sind, wobei durch einen axial innerhalb der Ausnehmung der Welle (60) ausfahrbaren Aktor (62), der ebenfalls ein kegeliges Ende (64) aufweist, welches gegen die kegeligen Enden (70) der Stifte (68) drückt, die Elemente (68) beim Ausfahren des Aktors (62) durch Umlenkung der Kräfte an den kegeligen Enden (64, 70) radial ausfahren können und in radiale Öffnungen (74) der Nabe des Pumpenrotors (76) eingreifen.11. A pump assembly according to claim 5, characterized in that in a recess of the shaft (60) radially extendable pins (68) or elements with conical / conical ends (70) are arranged, which radially by spring forces in the shaft (60) retractable in which, by means of an actuator (62) which can be extended axially within the recess of the shaft (60) and which likewise has a conical end (64) which presses against the conical ends (70) of the pins (68), the elements (68) upon extension of the actuator (62) by deflection of the forces at the tapered ends (64, 70) can extend radially and engage in radial openings (74) of the hub of the pump rotor (76).
12. Pumpenanordnung nach Anspruch 5, dadurch gekennzeichnet, dass in einer axialen Ausnehmung der Welle (80) ein topfförmiger Spreizkörper (78) mit einer konischen Ausformung mit radial auslenkbaren Spreizarmen (86) angeordnet ist, und wobei die radial auslenkbaren Spreizarme (86) durch Schlitze in der Welle (80) in Ausnehmungen (90) der Rotornabe eingreifen können, wenn durch einen axial innerhalb der Ausnehmung der Welle (80) ausfahrbarer Aktor (82), der ebenfalls ein kegeliges oder ein kugeliges Ende (84) aufweist, die Spreizarme (86) durch Umlenkung an dem kegeligen Ende (84) des Aktors (82) radial ausfahren und in radiale Öffnungen (90) der Nabe des Pumpenrotors (92) eingreifen. 12. Pump arrangement according to claim 5, characterized in that in an axial recess of the shaft (80) a cup-shaped expansion body (78) is arranged with a conical shape with radially deflectable spreader arms (86), and wherein the radially deflectable spreader arms (86) Slits in the shaft (80) in recesses (90) of the rotor hub can engage, if by an axially within the recess of the shaft (80) extendable actuator (82), which also has a tapered or a spherical end (84), the spreader arms (86) extend radially by deflection at the tapered end (84) of the actuator (82) and engage in radial openings (90) of the hub of the pump rotor (92).
EP06805431A 2005-10-27 2006-10-17 Pump arrangement Not-in-force EP1943423B1 (en)

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Publication number Priority date Publication date Assignee Title
AT505644B1 (en) 2007-09-06 2011-09-15 Tcg Unitech Systemtechnik Gmbh WATER PUMP
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Also Published As

Publication number Publication date
ATE556223T1 (en) 2012-05-15
WO2007048380A1 (en) 2007-05-03
EP1943423B1 (en) 2012-05-02
DE112006002561A5 (en) 2008-07-03

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