EP2698541A2 - Pompe rotative avec volume d'alimentation réglable, notamment pour le réglage d'une pompe de liquide de refroidissement - Google Patents

Pompe rotative avec volume d'alimentation réglable, notamment pour le réglage d'une pompe de liquide de refroidissement Download PDF

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Publication number
EP2698541A2
EP2698541A2 EP13180155.7A EP13180155A EP2698541A2 EP 2698541 A2 EP2698541 A2 EP 2698541A2 EP 13180155 A EP13180155 A EP 13180155A EP 2698541 A2 EP2698541 A2 EP 2698541A2
Authority
EP
European Patent Office
Prior art keywords
pump
housing structure
housing
fluid
pressure
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.)
Withdrawn
Application number
EP13180155.7A
Other languages
German (de)
English (en)
Other versions
EP2698541A3 (fr
Inventor
Claus Welte
Dr. Uwe Meinig
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.)
Schwaebische Huettenwerke Automotive GmbH
Original Assignee
Schwaebische Huettenwerke Automotive 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 Schwaebische Huettenwerke Automotive GmbH filed Critical Schwaebische Huettenwerke Automotive GmbH
Publication of EP2698541A2 publication Critical patent/EP2698541A2/fr
Publication of EP2698541A3 publication Critical patent/EP2698541A3/fr
Withdrawn legal-status Critical Current

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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
    • 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
    • F04C15/0042—Systems for the equilibration of forces acting on the machines or pump
    • 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
    • F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • 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
    • F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • F04C2/102—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member the two members rotating simultaneously around their respective axes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D13/00—Pumping installations or systems
    • F04D13/12—Combinations of two or more pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • 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
    • F04D5/00—Pumps with circumferential or transverse flow
    • F04D5/002—Regenerative pumps
    • 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 invention relates to an adjustable in relation to their delivery volume rotary pump.
  • the rotary pump may be part of a pump assembly and in particular serve as a servo pump for a work pump to supply fluid to the work pump, for example, serve as a precharge, or to adjust an operating parameter, such as the delivery volume of the working pump. It can form a coolant pump in combination with a working pump and serve for the fluidic adjustment of the delivery volume of the working pump.
  • a preferred field of application is vehicle construction.
  • the rotary pump or combination of rotary pump and working pump can be used in particular for supplying an aggregate, such as an internal combustion engine for driving a vehicle, with a fluid.
  • a pump impeller on the outer circumference encompassing annular slide to form an annular gap axially shifted and thereby varies on the outer circumference of the feed wheel of the flow cross-section.
  • the annular slide acts as an aperture in the discharge area of the delivery wheel.
  • the pumped by rotary pumps per unit time fluid volume changes with the speed of the pump.
  • the delivery volume of the pump speed is proportional, since such pumps have a constant specific delivery volume at least in the practically relevant speed range.
  • the specific delivery volume is the volume of fluid delivered per revolution.
  • turbomachines such as centrifugal pumps
  • the proportionality is not present, the delivery volume even grows disproportionately to the speed. If the rotary pump is rotationally driven by an internal combustion engine in fixed speed relation to an output shaft of the internal combustion engine, such as a crankshaft, as is the case in preferred applications, the proportionality or, in general, the dependence of the delivery volume on the rotational speed in certain engine speed ranges may be disturbing.
  • lubricating oil pumps require more lubricating oil to supply engine drive motors from an engine speed of about 2000 rpm than is necessary for lubricating the internal combustion engine.
  • coolant pumps which are designed as centrifugal pumps in most applications, the conditions are similar. If the pump pumps more fluid than it actually needs, energy is wasted driving the pump. Furthermore, undesirable side effects may occur. For example, in the case of Schinier oil pumps, too much lubricated oil can cause the crankshaft to splash in the lubricating oil, resulting in further losses. The fluid delivered beyond the requirement can, for example, be conveyed back into the fluid reservoir via a bypass, whereby, however, drive energy for the pump is unnecessarily consumed.
  • adjustable for example, only controllable or also controllable rotary pumps have been developed in the delivery volume.
  • EP 1 363 025 B1 adjustable gear pumps for example, describes the EP 1 363 025 B1 adjustable gear pumps.
  • An adjustable vane pump is for example from the DE 10 2010 009 839 A1 known.
  • the EP 2 489 881 A2 discloses a radial type radial centrifugal pump and its use as a coolant pump.
  • the centrifugal pump comprises a radial impeller for conveying the working fluid, which can serve in particular as a coolant for an internal combustion engine, and also a servo pump for the fluidic adjustment of a control structure, by the adjustment of the delivery volume of the centrifugal pump is changed.
  • the servo pump is designed as a rotary pump and cooperates with a control valve, via which the adjusting structure is acted upon by the fluid pumped by the servo pump.
  • the delivery volume of the servo pump is so high that the volume flow does not flow through the control valve in the open valve state quickly enough and therefore a backlog can arise, which acts undesirably on the actuator structure.
  • a pressure limiter is provided downstream of the outlet of the servo pump, through which fluid can flow back into the circuit. This corresponds to the bypass solution mentioned above.
  • the invention is based on a rotary pump with adjustable delivery volume, which comprises a housing having a first housing structure and a second housing structure, optionally one or more further housing structures, furthermore a delivery chamber and at least one pump wheel rotatable in the delivery chamber about an axis of rotation.
  • a rotary drive of the impeller this promotes alone or optionally with one or more other pumping wheels, a fluid from an inlet leading into the feed chamber to an outlet leading out of the feed chamber.
  • the inlet opens into a low-pressure region of the delivery chamber, and the outlet opens into a high-pressure region of the delivery chamber.
  • the housing structures form chamber walls of the delivery chamber, the first housing structure a first chamber wall and the second housing structure a second chamber wall.
  • the second housing structure is relative to the first housing structure from a first position against a restoring pressure force in a second position movable.
  • the rotary pump therefore also includes a pressing device for generating the pressing force.
  • the gap opens into an environment of the housing, so that in the second position, fluid can escape from the delivery chamber, bypassing the inlet and the outlet, and at least a portion of the fluid flowing through the inlet into the delivery chamber by means of the impeller only is not conveyed to the outlet, but can flow on the way between inlet and outlet through the gap.
  • the delivery chamber is an internal gap within the delivery chamber, so that fluid does not escape through the gap in the environment of the housing, but only in the delivery chamber circulates. For the only circulating in the delivery chamber portion of the fluid less flow than the part of the fluid must be applied, which flows through the delivery chamber and the outlet per unit time.
  • the internal gap in this sense thus causes a conveying capacity reducing fluid circulation within the delivery chamber.
  • the internal gap may in particular be formed on an end face of the impeller by increasing a gap existing between the impeller and the second chamber wall also in the first position of the second housing structure by the movement in the direction of the second position. If the second housing structure assumes the first position, the delivery chamber may advantageously be tightly sealed apart from the inlet and the outlet as well as unavoidable leaks, and the first position accordingly be a closed position of the second housing structure.
  • variable displacement pumps which supply fluid conveyed on demand downstream of the outlet via a bypass back into a reservoir
  • drive power for the pump is saved because the rotary pumps in the second position of the second housing structure only a comparatively lower volume flow against the at the outlet must prevail fluid pressure.
  • a bypass valve for the discharge of too much pumped fluid is not needed.
  • the adjusting mechanism formed by means of the second housing structure and the pressing device can build relatively compact with small dimensions, whereby the arrangement of the rotary pump facilitates in tight installation spaces or even made possible.
  • the second chamber wall formed by the second housing structure may be a peripheral wall or a portion of a peripheral wall of the delivery chamber.
  • the second chamber wall is an end wall or a partial region of an end wall of the delivery chamber.
  • the second housing structure may advantageously be a housing cover which closes off the delivery chamber at one end face.
  • the first housing structure may form a peripheral wall or a portion of a peripheral wall of the delivery chamber. Preferably, it forms a peripheral wall and one of the second chamber wall axially on the other side of the delivery chamber facing the bottom of the delivery chamber, so a further end wall.
  • a plurality of separately formed housing structures can be joined together, including the first housing structure.
  • the said housing cover can also be composed of a plurality of separately formed housing structures, including the second housing structure, thus forming the second housing structure only a portion of a housing cover.
  • the second housing structure can also be movable relative to at least one other of the housing structures forming the assembled housing cover in order to realize the mobility according to the invention.
  • the second chamber wall may extend in particular in the low-pressure region of the delivery chamber, for example only in a chamber region which extends from the inlet towards the outlet, but not to the outlet.
  • the second chamber wall does not have to extend to the inlet, but may each have a distance both to the outlet and to the inlet in the direction of rotation of the impeller or against the direction of rotation.
  • the inlet opens into the delivery chamber in the region of the second chamber wall.
  • the second housing structure may basically form the outlet of the delivery chamber, but more preferably it forms the inlet.
  • the second chamber wall may be an end wall of the delivery chamber and the inlet at this end wall in the delivery chamber lead.
  • the outlet can in particular open at an axially opposite other end wall in the delivery chamber, but in principle also on a peripheral wall of the delivery chamber.
  • the inlet can also be formed by another housing structure, for example the first housing structure, so that the second housing structure forms neither the inlet nor the outlet.
  • the second housing structure may be movably or rotationally movably supported or supported, preferably to or from the first housing structure.
  • translational mobility comes, for example, an axial mobility, d. H. a mobility at least substantially parallel to the axis of rotation of the impeller into consideration.
  • the second housing structure is tiltably or pivotally supported or stored. In comparison to a translational mobility, the risk of tilting and thereby jamming of the second housing structure is reduced.
  • a tilting or pivoting mobility can be effected simply and last but not least, for example, by pressing the second housing structure in a loose pressure contact against a supporting structure, such as against the first housing structure.
  • the pressing force for this purpose can be conveniently generated by the pressing device.
  • the second housing structure can be pressed in such embodiments, in particular in an axial pressure contact with the support structure, preferably the first housing structure.
  • the second housing structure is tilted or swung against the pressing force of the support structure, but here remains locally, on one side, in said pressure contact with the support structure.
  • the second housing structure of the pressure distribution in the delivery chamber is adapted to the pressing force applied. This can be achieved, for example, by applying the pressure force eccentrically in the region of the force acting on the second housing structure by the pressure in the delivery chamber.
  • the pressure force eccentrically in the region of the force acting on the second housing structure by the pressure in the delivery chamber.
  • the pressure distribution in the interior of the delivery chamber are at least basically not respected. Basically, this also applies in embodiments in which the second housing structure is mounted tiltably in a rotary bearing of shaft and bushing.
  • the lever is determined which the pressure force acting on the second housing structure in the delivery chamber has for pivotal mounting. If the second housing structure is tiltably or pivotably supported in a loose pressure contact, the tilting or pivoting axis does not have to be fixed at least in advance, at least not inevitably.
  • the pressure point, through which the tilting or pivoting axis extends, can adjust itself to the pressure conditions in the delivery chamber.
  • the location of the tilting axis or at least a narrow region in which the tilting or pivoting axis extends is more preferably dictated by design, for example by a guiding engagement in which the second housing structure is guided relative to the first housing structure within the scope of its mobility becomes.
  • the pressing device is preferably designed such that it presses the second housing structure in the axial direction against a support structure, wherein the support structure, as already mentioned, is preferably formed by the first housing structure.
  • a tilting or pivoting axis about which the second housing structure tilts or pivots relative to the first housing structure extends, preferably transversely to the rotational axis of the impeller, expediently it extends orthogonally to the axis of rotation in such embodiments.
  • the support structure, preferably the first housing structure, and the second housing structure can together form a pivot bearing in the form of an open bearing cup and a bearing cam shaped to fit the bearing cup.
  • the bearing cup may have, for example, a cylindrical or spherical bearing surface which advantageously extends over an angle of 180 ° or less about the tilt or pivot axis thus formed.
  • the bearing cam is shaped congruent to the bearing cup.
  • the pan can advantageously be formed on the support structure, but basically also instead of the second housing structure.
  • the bearing cam is correspondingly arranged in each case on the other structure, expediently formed with this in one piece.
  • the bearing cup can in particular in a second housing structure facing shoulder, which form an end face and an axis of rotation facing inner surface of the support structure together, so to speak, in the region of an inner angle of the end face and inner surface formed.
  • the second housing structure forms a housing cover and, accordingly, the second chamber wall is an end wall of the delivery chamber
  • the second housing structure is secured relative to the first housing structure against relative rotational movements about the axis of rotation of the impeller.
  • the second housing structure may in particular be arranged immovably relative to the first housing structure by means of an axially and preferably radially extended guide in the circumferential direction.
  • the guide is designed so that it allows for adjusting the delivery volume required movement in the first position.
  • the guide is arranged in advantageous embodiments in the region or at least near the tilting or pivoting axis.
  • the tilting or pivoting axis extends through the guide.
  • the rotary pump can be designed as a positive displacement pump or as a turbomachine, such as a centrifugal pump.
  • positive displacement pumps are especially internal-axis pumps such as internal gear pumps and vane pumps, but for example also external gear pumps into consideration.
  • a particularly preferred type of pump is the side channel pump.
  • the rotary pump comprises one or more side channel stages, ie one or more corresponding pump wheels.
  • the rotary pump is single-stage.
  • the rotary pump has at least one impeller with impeller cells, such as an impeller, and this impeller axially, ie laterally facing at least one side channel, in the circumferential direction about the axis of rotation of the impeller axially adjacent extends the impeller. If the side channel pump has only a single side channel, this side channel is connected to the inlet of the rotary pump and circumferentially spaced from the outlet of the rotary pump.
  • a side channel can also be provided laterally to the left and to the right of the at least one impeller. If the side channel pump has a plurality of stages and has a first and at least one second impeller, only one side channel can be provided laterally facing the first impeller or only one side channel and the second impeller facing sideways, only one side channel or one side channel on each side.
  • the pressing device can act mechanically, hydraulically, pneumatically or electrically.
  • the pressing force is an elastic restoring force, i. H. a spring force.
  • the pressing device comprises in such embodiments according to one or more pneumatic or preferably one or more mechanical springs. If the pressing force is generated by one or more mechanical springs, the spring or the plurality of springs can act on the load in particular as a compression spring (s). In principle, however, the pressing force can instead be generated for example by one or more tension springs.
  • the one or the plurality of springs may each be, for example, a helical spring, a plate spring, a leaf spring or in particular a corrugated ring spring.
  • the pressing device can also have springs of different types in combination.
  • the spring is shaped and arranged so that its spring axis coincides with the axis of rotation of the impeller. If the pressing device has a plurality of springs, the plurality of springs are preferably distributed around the axis of rotation, and the spring axes extend parallel to the axis of rotation.
  • the rotary pump can be used in particular as a servo pump in combination with a primary pump, in the following working pump, for example, for adjusting the delivery volume of the working pump.
  • a particularly favorable combination of a work pump adjustable in the delivery volume and a servo pump designed as a rotary pump is disclosed.
  • the rotary pump according to the invention can replace any of the rotary pumps disclosed in this earlier application to the Fluidic adjustment of the working pump in the delivery volume.
  • the working pump may advantageously be a coolant pump for a vehicle, in particular for an internal combustion engine of a vehicle or for the heating or cooling of a vehicle.
  • the EP 2 489 881 A2 is referred to in relation to advantageous combinations of a working pump with servo-rotation pumps.
  • the subject of the invention is also a pump arrangement for supplying an aggregate, preferably an engine of an internal combustion engine, with a working fluid
  • the pump assembly has a working pump for the promotion of the working fluid to the aggregate or away from the unit and a rotary pump according to the invention.
  • the work pump includes a work pump housing, a working impeller rotatably driven by a drive shaft for conveying the working fluid, and an actuator structure which is adjustable to different positions by means of a control fluid relative to the work pump housing to adjust a configuration of the work pump.
  • the adjustable configuration of the working pump is preferably such that the configuration for the delivery volume of the working pump is decisive.
  • the adjustable working pump configuration can be in the execution of the working pump as an internal gear pump in particular the existing between an externally toothed internal gear and an internally toothed outer eccentricity and the execution of the working pump as a vane pump the position of an impeller surrounding adjusting ring.
  • the work pump designed as a turbomachine such as the work pump of EP 2 489 881 A2
  • the variable working pump configuration is an adjustable flow geometry, such as a flow area or flow on a flow path of the working fluid, which flow path includes an inflow area, the working impeller, and an outflow area of the working impeller.
  • the EP 2 489 881 A2 Possibilities of adjusting the flow geometry for a turbomachine in Radialbauart be shown.
  • FIG. 1 shows a pump assembly of a first embodiment in a perspective view.
  • the pump arrangement can be used as a coolant pump for an internal combustion engine, preferably as a coolant pump for an internal combustion engine of a motor vehicle, and is referred to below as a whole as a coolant pump. It is a coolant pump in radial design.
  • a radial impeller 2 is rotatably mounted about a rotation axis R.
  • the housing 1 has mounting points for mounting in the cooling circuit of the internal combustion engine, preferably on the internal combustion engine on.
  • the coolant pump is coupled in the mounted state for its drive with the internal combustion engine, so it can be rotationally driven by this about a suitable transmission, such as a traction drive.
  • a drive wheel 3 is correspondingly arranged on a drive side of the coolant pump.
  • a belt pulley could also be replaced by a sprocket in the case of a chain drive or by a gear for an optional gear drive instead of a traction drive.
  • the drive wheel 3 is arranged coaxially to the radial impeller 2 and thus rotatable about the same axis of rotation R.
  • the radial impeller 2 is connected torque-fixed to the drive wheel 3.
  • both wheels 2 and 3 are each secured against rotation with a common drive shaft 4, which is rotatably supported by the housing 1.
  • the radial conveying wheel 2 conveys a coolant, preferably a liquid coolant, from a central inflow region 5, the suction side of the pump, into an outflow region 6 extending on the outer circumference around the radial impeller 2.
  • the radial impeller 2 is in contact via the inflow region 5 Coolant reservoir and the pressure side via the outflow 6 to the supplied with the coolant internal combustion engine or one or more other consumers, such as a heater connected.
  • the coolant pump is adjustable in relation to the delivery flow.
  • the flow rate is adjusted by varying the flow geometry, for example by variation of the flow cross section in the passage from Radialdirrad 2 in the outflow 6, as known from radial pumps, from an annular channel or partial ring channel of a FIG. 1 not shown, removed part of the housing 1 is formed.
  • the annular or partial annular channel extends on the outer circumference of the Radialfordrads 2 to this completely over 360 ° or at least partially encircling.
  • the variation of the flow geometry is used an adjusting structure 10 which is formed as an annular slide, preferably as a split-ring slide and relative to the housing 1 and the Radial complicatrad 2 axially back and forth in different Adjustment positions can be adjusted.
  • the adjusting structure 10 forms an annular gap enclosing this directly with the radial conveying wheel 2, thus acting as a split-ring slide.
  • the adjusting structure 10 is adjustable back and forth between a first axial adjustment position and a second axial adjustment position. In FIG. 1 It assumes the first adjustment position in which the crossover cross section from the radial impeller 2 in the discharge area 6 is maximum. In the second adjustment position, this crossover cross section is minimal.
  • the adjusting structure 10 releases the radial conveying wheel 2 over its entire effective axial conveying width.
  • the second adjustment position it covers the effective conveying width of the radial conveying wheel 2 as preferred, but only by way of example completely.
  • the adjusting structure 10 is therefore an adjustment between an example of the zero promotion corresponding minimum delivery volume and a maximum delivery volume possible.
  • the coolant pump comprises an actuator device with a control valve 7, which is formed as preferred, but only by way of example as an electromagnetically acting valve.
  • the control valve 7 can be fed via a connection 8 electrical energy and control signals.
  • the control valve 7 can be connected via the connection 8 in particular to a control of the internal combustion engine, for example a motor control in the case of a drive motor of a motor vehicle, or a control for a vehicle heating system.
  • the adjusting structure 10 is fluidically adjustable by means of a control fluid, which is formed by the coolant to be delivered.
  • the actuating structure 10 is for this purpose coupled in the housing 1 with a piston which is acted upon by the control valve 7 controlled by a pressure of the control fluid.
  • the control valve 7 can be supplied via the terminal 8, a control signal.
  • the control signal can be generated as a function of a measured temperature, in particular a temperature measured in the cooling circuit, such as a coolant temperature.
  • a temperature sensor may be arranged at a representative point of the cooling circuit, preferably at a plurality of representative points in each case Sensor output signal of the control is given, which forms the control variable for the control valve 7 from the one or more sensor signal (s).
  • FIG. 2 shows the coolant pump in a longitudinal section.
  • the drive shaft 4 is divided in the representation into functional axial sections 4a to 4e and rotatably mounted in the shaft section 4d from and in the housing 1 by means of a roller bearing.
  • the radial impeller 2 is connected in a front end portion 4a secured against rotation with the drive shaft 4.
  • the drive wheel 3 is arranged behind the rotary bearing section 4d in a rear shaft section 4e, which is axially remote from the shaft section 4a, as viewed from the radial conveyor wheel 2, and is connected there to the shaft 4 so as not to rotate.
  • the coolant pump comprises an additional pump 20, which is referred to below as a servo pump 20 for the conceptual distinction from the working pump comprising the radial impeller 2, the actual coolant pump.
  • the servo pump 20 is a positive displacement type rotary pump and exemplified as an internal gear pump. It comprises a non-rotatably connected to the shaft 4, provided with an external toothed inner wheel 21 and the inner wheel 21 surrounding, internally toothed outer wheel 22, which are in meshing engagement with each other, namely meshing, in which they rotates about rotational axis R in rotationally driven shaft 4 form periodically increasing and decreasing delivery cells.
  • the control fluid in this case the coolant, is sucked in by the increasing delivery cells.
  • the high-pressure side of the servo pump 20 the control fluid is discharged again under increased pressure.
  • the servo pump 20 is connected at its high pressure side via a pressure channel 31 to the control valve 7.
  • the control fluid area which extends from the outlet of the servo pump 20 to the control valve 7, that includes the pressure channel 31, forms the high pressure side of the servo pump 20.
  • the control fluid acts on this high pressure side on a piston 15 which is axially movably guided in the housing 1 of the coolant pump and coupled to the actuator structure 10 so that the actuator structure 10 upon application of the piston 15 with appropriate control fluid pressure in the direction of the adjustment of the maximum axial overlap of Radialeuerrads 2 is moved.
  • the piston 15 is, as preferred, axially fixedly connected to the actuator structure 10, so that they easily join the axial movement of the piston 15.
  • the adjusting structure 10 is acted upon by a spring device with springs 17 distributed uniformly around the axis of rotation R in the axial opposite direction with spring force.
  • the control fluid pressure acting on the piston 15 thus restores the spring force in the direction of the adjustment position of minimal overlap, which the adjusting structure 10 in FIG FIG. 2 takes, contrary.
  • the control valve 7 may be, for example, a switchable between different switching positions multi-way valve shuts off the high pressure side of the servo pump 20 in a first switching position and short-circuiting the high pressure side of the servo pump 20 with the coolant circuit in a second switching position and for this purpose preferably connects the pressure side of the coolant pump.
  • the servo pump 20 is expediently designed so that the control fluid pressure generated by it is sufficient even at idle of the internal combustion engine to adjust the actuator structure 10 in the first switching position, the blocking position befindlichem control valve 7 in the adjustment position of the maximum coverage.
  • Corresponds to the adjustment of the maximum coverage as preferably the full coverage promotes the Radialfordrad 2 virtually no coolant. This allows a rapid heating of the internal combustion engine when it is started from the cold state. In addition, the power consumption of the coolant pump is reduced.
  • the control valve 7 may have in simple embodiments at all only the two switch positions mentioned and always take one of these switch positions.
  • the control of the actuating structure 10 can be designed in such simple embodiments so that the actuator structure 10 can take only one of the two extreme positions, so either the maximum adjustment or the adjustment minimum coverage.
  • the control valve 7 can be set up to switch back and forth between the two switch positions so rapidly that the actuator structure 10 can also be adjusted axially to any desired adjustment position between the two extreme positions.
  • the control valve 7 may be adapted to continuously adjust the pressure of the control fluid to a specific value and thereby the actuator structure 10 to the balance of control fluid pressure and resiliency to a particular or any desired position between the maximum adjustment position and the adjustment position to set minimum coverage.
  • a pressure-holding device 28 is arranged, which prevents the control fluid can flow back into the servo pump 20.
  • the pressure holding device 28 blocks in a blocking position a flow cross section against a backflow to the servo pump 20, but allows an outflow in the direction of the control valve 7 to. It opens only when the pressure of the control fluid at an upstream inlet of the pressure holding device 28 close to the servo pump 20 exceeds the pressure of the control fluid at a downstream outlet of the pressure holding device 28 close to the control valve 7. It is acted upon by spring force in the locked position, so takes the blocking position at constant pressure.
  • the in the locked position acting spring force is such that the pressure-maintaining device 28 opens at least in the direction of the control valve 7 when the internal combustion engine is idling and the pressure acting on the piston 15 corresponds to the ambient pressure.
  • the pressure-maintaining device 28 is as preferred, but only as an example designed as a check valve.
  • the actuating structure 10 When the control valve 7 is shut off, the actuating structure 10 can be held in the adjustment position of maximum overlap over a comparatively long period of time due to the pressure-retaining device 28, since backflow of the control fluid via the servo-pump 20 is prevented. If the adjusting structure 10 largely closes off the transition cross section on the outer circumference of the radial impeller 2 as preferred, the coolant upstream of the radial impeller 2 of the tightness of the transitional cross section can be retained correspondingly longer than is the case with rapid pressure reduction on the high pressure side of the servo pump 20 would. The internal combustion engine can cool down more slowly after stopping, the cooling process can be continued.
  • the servo pump 20 and the pressure holding device 28, if the latter is present, are preferably designed such that the pressure generated by the servo pump 20 during idling of the internal combustion engine is sufficient to adjust the adjusting structure 10 into the adjustment position of maximum overlap.
  • this pressure can either be maintained or reduced and thus the position of the actuator structure 10 can be adjusted as needed even when idling.
  • This preferably also applies to any other operating state of the internal combustion engine, as long as the control fluid pressure generated by the servo pump 20 is sufficient to overcome the restoring spring force acting on the adjusting structure 10 in the direction of the position of minimal overlap.
  • the control fluid pressure can be determined by means of a in FIG. 4 illustrated optional pressure limiter 35 are limited to a maximum value, so that it can not exceed this value even at high speeds and correspondingly high delivery volume of the servo pump 20. Due to the limitation of the control fluid pressure, the force with which the actuating structure 10 can press in the adjustment position of maximum overlap against an axial stop, limited to a resulting from the control fluid pressure and the effective pressure surface of the piston 15 maximum value. An inlet of the pressure limiter 35 is connected to the space in which the piston 15 is supplied with the control fluid. An outlet of the pressure limiter 35 redirects the control fluid into the main flow of the coolant conveyed by the radial impeller 2.
  • the pressure limiter 35 is as preferred, but only as an example formed as a check valve.
  • the pressure limiter 35 is arranged offset in the circumferential direction about the rotation axis R to the pressure-retaining device 28.
  • the in FIG. 4 shown longitudinal section is in the circumferential direction corresponding to the longitudinal section of Figures 2 and 3 added.
  • the servo pump gears 21 and 22 are accommodated in a separate servo pump housing comprising a first housing structure 23 and a second housing structure 24.
  • the housing structure 23 rotatably supports the outer wheel 22 in a sliding contact over the outer periphery thereof.
  • the inclusion of the servo pump gears 21 and 22 in the own servo pump housing 23, 24 facilitates the assembly of the pump assembly by the servo pump 20 can be installed in a preassembled state.
  • the servo pump housing 23, 24 is arranged in the housing 1 of the working or coolant pump, as preferred, within the annular adjustment structure 10.
  • the pressure retaining device 28 and the pressure limiter 35 are also arranged in the servo pump housing 23, 24.
  • FIG. 3 shows in an enlarged view the central region of the coolant pump in the same longitudinal section as FIG. 2 ,
  • the centrally arranged servo pump housing 23, 24 is covered by a support structure 13 on its end facing the radial impeller 2.
  • the support structure 13 simultaneously covers the housing 1 of the coolant pump at the relevant side.
  • the housing structure 24 is arranged, which directly covers the housing structure 23 and in which the inlet 25 and the outlet 27 of the servo pump 20 are formed.
  • a filter 26 is arranged in the inlet 25, for example a filter screen which retains dirt particles.
  • the servo pump 20 draws coolant from a location in the centrifugal force field, for example at or near the outer periphery of the Radial dressrads 2 or by one or more perforations in the Radial impeller 2, through the inlet 25 and ejects the coolant as control fluid with increased pressure through the outlet 27 from.
  • the outlet 27 is connected via the pressure-retaining device 28 to the pressure channel 31 and this with the rear side facing away from the radial impeller 2 of the piston 15.
  • the pressure-retaining device 28 assumes the blocking position.
  • the servo pump 20 stands still, or it has just been reduced in blocking control valve 7, for example, the pump speed.
  • the servo pump 20 is disposed in the shaft portion 4b axially adjoining the shaft portion 4a. Between the housing structure 23 and the shaft bearing 4d forming the rotary bearing, a shaft seal 19, for example in the form of a mechanical seal or lip seal, which seals the housing 1, is arranged in the shaft section 4c.
  • a shaft seal 19 for example in the form of a mechanical seal or lip seal, which seals the housing 1 is arranged in the shaft section 4c.
  • the servo pump 20 designed as a rotary pump is advantageously narrow axially, as a result of which the radial impeller 2 can be arranged axially particularly close to the rotary bearing formed in the shaft section 4d. Because of the design as an internal gear pump, this axial distance can be kept particularly low.
  • the adjusting structure 10 is guided axially along a guide 12 in a sliding contact.
  • the guide 12 is a sleeve inserted into the housing 1, as is preferred but only by way of example a steel sleeve.
  • the guide 12 surrounds the servo pump housing 23, 24 and is exemplarily pushed directly over the servo pump housing 23, 24.
  • the guide 12 is supported on the servo pump housing 23, 24 thus from the inside. It is also supported on the housing 1 by being pushed in the housing 1 on a free peripheral surface of the housing 1, preferably pressed.
  • the housing 1 is preferably made of an aluminum material and may in particular be cast from aluminum or an aluminum-based alloy.
  • the adjusting structure 10 may in particular be a plastic structure, for example an injection molded part made of a thermoplastic material.
  • the piston 15 is suitably formed from an elastomer or natural rubber.
  • the piston 15 is axially reciprocally accommodated in a ring cylinder space.
  • the annular cylinder space is externally from an inner peripheral surface of the housing 1, for example a housing neck 11, and bounded on the inside by the guide 12.
  • the limitation of the annular cylinder space through metal surfaces is favorable for the respective sliding pair with the piston 15.
  • the piston 15 is acted upon at a free piston side as already mentioned with the control fluid.
  • the piston 15 is arranged at one axial end of the adjusting structure 10, which faces away from the radial conveying wheel 2, as preferred, and can in particular be fixedly connected to the adjusting structure 10, for example by a material fit. In principle, however, the piston 15 can also be in the direction of its application to the control fluid in only one pressure contact with the actuating structure 10.
  • the pressure of the control fluid act as mentioned several distributed around the axis of rotation R arranged springs 17, which are supported with one spring end respectively on the lid 13 and the other end of the spring to a spring seat 18 formed on the adjusting structure 10.
  • the springs 17 are exemplified as helical compression springs. They are arranged in an annular space, which is bounded radially inward by the guide 12 and radially outward by the adjusting structure 10.
  • the adjusting structure 10 is supported in the guide contact with the guide 12 at this by means of a web bearing, which is formed by axially extending webs 16.
  • the webs 16 are formed on one of the guide 12 radially facing inner periphery of the adjusting structure 10.
  • FIG. 5 shows the coolant pump in a cross section axially at the height of the servo pump gears 21 and 22. From radially inward to outward are the shaft 4, the inner wheel 21 arranged thereon secured against rotation, the outer wheel 22 therewithin the conveying engagement, the servo pump housing 23, 24 and the pump housing 23, 24 surrounding guide 12 recognizable. Also visible are the receiving space formed in the servo pump housing 23 for forming the pressure limiter 35 and a housing structure 24 and the support structure 13 (FIG. FIG. 3 ) connected to the outlet 27 of the power steering pump 20 connecting channel 30 which is connected to the leading to the control valve 7 pressure channel 31 and in which the pressure holding device 28 is formed. Another connecting channel 33 is connected to a discharge channel 32.
  • the discharge channel 32 is connected to the control valve 7.
  • the discharge channel 32 leads from the control valve 7 via the connecting channel 33 back into the coolant circuit.
  • the control valve 7 connects the pressure channel 31 with the discharge channel 32, so that the piston 15 (FIG. FIG. 3 ) is acted upon only with a comparatively low pressure and the actuator structure 10 by the force of the springs 17 in the in the Figures 2 and 3 shown adjusting minimum coverage is kept.
  • FIG. 5 Furthermore, the axial webs 16 formed on the inner circumference of the adjusting structure 10 can be seen, which are exposed on the inner circumference by recesses adjacent to each other in the circumferential direction and ensure a clean axial guidance of the adjusting structure 10.
  • the adjusting structure 10 is guided relative to the housing 1 of the coolant pump secured against rotation by means of rod-shaped anti-rotation 14, which protrude into corresponding counter-guides of the adjusting structure 10.
  • One of the anti-rotation 14 is also in FIG. 3 recognizable.
  • the anti-rotation 14 protrude axially from the back of the support structure 13.
  • FIG. 5 also located on the adjusting structure 10 supporting points for the springs 17, namely the spring seats 18 recognizable.
  • FIG. 6 shows the coolant pump again in another cross-section axially at the height of the pivot bearing formed in the shaft portion 4d.
  • the cross-sectional plane extends along the pressure channel 31 and the discharge channel 32.
  • For pivot bearing is nachzutragen that this is formed by at least two axially spaced bearing grooves and in the bearing grooves about the rotation axis R arranged rolling elements and the rolling elements outside enclosing bearing sleeve 9.
  • the bearing grooves are formed directly on the outer circumference of the drive shaft 4.
  • the bearing sleeve 9 is pressed into the housing 1.
  • the drive shaft 4 forms with the rolling bearing or the plurality of axially spaced rolling bearings and the bearing sleeve 9 is a structural unit, which is used in the assembly of the coolant pump in the housing 1.
  • FIGS. 7 and 8th show a pump assembly of a second embodiment, which instead of the servo pump 20 comprises a rotary-type servo pump 40, which is formed as a side channel pump.
  • the servo pump 40 is multi-stage, two-stage example, the pump stages are connected to achieve high delivery pressure in series.
  • the pump arrangement also differs from the first embodiment in the way in which the working fluid is supplied to the servo pump 40.
  • the pump arrangement can be used as a coolant pump, as in the first embodiment Simplified hereinafter also referred to as a coolant pump.
  • the working fluid is a refrigerant in such use.
  • the coolant is already branched off centrally from the main flow in the inflow region 5 of the coolant pump in the centrifugal force field generated by the radial impeller 2 via a connection 38 formed there and guided by the drive shaft 4 to the servo pump 40.
  • the terminal 38 forms at least one opening on the outer circumference of the drive shaft 4 inlet opening.
  • a plurality of inlet openings spaced apart in the circumferential direction form the connection 38 in common.
  • the refrigerant sucked by the servo pump 40 flows through the port 38 in and axially through the drive shaft 4 to an outlet 39 which also opens at the outer circumference of the drive shaft 4, and flows through the outlet 39 into a fluid space 45 provided with an in the figures unrecognizable inlet of the servo pump 40 is in communication.
  • the outlet 39 may include a plurality of such outlet openings. Due to the centrifugal force central branch, additionally favors that the port 38 opens at an at least substantially axially extending outer peripheral surface in the centrifugal force field, only due to the centrifugal force of dirt particles depleted coolant to the servo pump 40th
  • the servo pump 40 includes a first servo pump 41 and a second servo pump 42.
  • the pump wheels 41 and 42 are identical as such, which is appropriate, but not essential required.
  • the pump wheels are cell wheels each having a central region, a circumferential outer ring and a ring region located between the central region and the outer ring, which, as seen from the synopsis of FIGS. 7 and 8th recognizable, is divided by cell webs in axially permeable conveying cells 43, which are separated from each other in the circumferential direction by the cell webs.
  • the servo pump wheels 41 and 42 can also be formed as impellers open on the outside by dispensing with an outer ring surrounding the delivery cells 43 radially on the outside.
  • side channels are formed in addition to the servo pump wheels 41 and 42, which extend in the circumferential direction and radially at the height of the conveyor cells 43 over an angle of less than 360 °. So extend a first side channel 46 and a second side channel 47 next to each of the first impeller 41, one left and the other right next to it, and a third side channel 48 and a fourth side channel 49 next to the second impeller 42, one on the left and the other right next to the impeller 42nd
  • Each of the side channels 46 to 49 is formed in the housing 23, 24 as an open axially to the feed cells 43 of the associated impeller 41 or 42, so that the fluid, here the coolant, between the feed cells 43 and the side channels 46, 47 and 48, 49 of the respective impeller 41 or 42 can flow back and forth in order to achieve the pressure increase known from side channel pumps, based on impulse transmission in the multiple passage between the conveyor cells 43 and the respective side channel.
  • the first side channel 46 is connected to the fluid space 45 via the inlet of the servo pump 40.
  • the second side channel 47 is connected to the third side channel 48 and the fourth side channel is connected to the outlet 28 of the power steering pump 40.
  • the servo pump 40 With rotary drive, the servo pump 40 sucks the coolant from the fluid space 45 via the inlet of the servo pump 40 into the side channel 46 and thus into the first pump stage formed by the impeller 41 and the side channels 46 and 47.
  • the sucked-in coolant is conveyed at elevated pressure through an internal outlet of the second side channel 47 to an internal inlet of the third side channel 48 and in the second pump stage formed by the impeller 42 and the side channels 48 and 49 with further pressure increase through the servo pump outlet 28 in the direction of the pressure-retaining device 28 conveyed away.
  • FIGS. 7 and 8th combines a side channel pump with centrifugal force cleaning of the coolant.
  • this type of coolant cleaning can also be combined with any other servo pump according to the invention, for example with the power steering pump 20 of the first embodiment.
  • each of the filter material cleaning arrangements of filter or filter and associated cleaning means may be combined with a single or multi-stage side channel pump to mention only a few possible variations.
  • FIG. 9 shows a pump assembly, which can be used as the other embodiments, in particular as a coolant pump.
  • the pump assembly includes a radial impeller 2 and an actuator structure 10, as in the other embodiments explained cooperate for adjusting the delivery volume of the coolant pump.
  • the pump assembly comprises a servo pump 50 of the rotation type, which serves as also in the other embodiments, the required for the adjustment of the adjustment structure 10 control fluid pressure for in FIG. 9 not shown control valve 7 ( FIGS. 1 and 2 ) to create.
  • the power steering pump 50 is a one-stage side channel pump having only one servo pump 51 which may correspond to the servo pump 41 of the second embodiment.
  • the power steering pump 50 includes a servo pump housing having the first housing structure, 23, and the second housing structure 24.
  • the housing structures 23 and 24 define with each other a delivery chamber in which the servo pump 51 is rotatably received about the rotation axis R.
  • the servo pump 51 is rotatably connected to the drive shaft 4 in the shaft portion 4b as in the other embodiments, and thus arranged coaxially with the radial impeller 2.
  • the mode of action corresponds apart from differences in the number of stages that of the second embodiment.
  • the control fluid which is also formed in the third embodiment by the working fluid of the main or working pump, is sucked via a servo pump inlet 55 into a low-pressure region of the delivery chamber 52.
  • the inlet 55 extends through the housing structure 24 and opens in the low pressure region of the delivery chamber 52 in a housing channel 56 on the housing structure 24 facing side channel 56 facing the side channel 56 opposite side channel is formed in the housing structure 23, a side channel 57, in the direction of rotation to Inlet 55 offset in a high pressure region of the delivery chamber 52 an outlet 58 opens.
  • the fluid sucked in through the inlet 55 is conveyed to the outlet 58 by pulse transmission between the pumping cells 53 of the servo pump 51 and the laterally adjacent side channels 56 and 57 under pressure increase.
  • the fluid flows via the already described pressure-retaining device 28 into the pressure channel 31 and the associated pressure chamber at the back of the piston 15.
  • the control valve 7 is closed, a corresponding fluid pressure builds up in the pressure chamber, so that the piston 15 and thus together the actuator structure 10 in the in FIG. 9 shown adjusted second adjustment position and held in the second adjustment position. Opens the control valve, which can be from the servo pump 50 conveyed fluid flow and the actuator structure 10 move under the action of the return spring 17 in the direction of their first adjustment position.
  • the delivery volume of the servo pump 50 increases with the speed of the Servopumpenrads 51. If the servo pump 50 provide even at relatively low speeds of the drive shaft 4 sufficient for the adjustment of the actuator structure 10 fluid pressure, the problem may arise at higher speeds that the servo pump 50 is a flow promotes when open control valve 7 ( FIGS. 1 and 2 ) not instantaneously, but can only flow off gradually. The actuating structure 10 remains in such situations despite open control valve 7 longer than desired in the second adjustment position, which corresponds to the state of lowest delivery volume of the coolant pump in the third embodiment.
  • the servo pump 50 is adjustable in its delivery volume.
  • the second housing structure 24 is arranged relative to the first housing structure 23 to move back and forth between a first position and a second position. If the housing structure 24 assumes the first position, the delivery chamber 52 is fluid-tight except for the inlet 55 and outlet 58 and unavoidable leakage at the end faces of the impeller 51. The first position can therefore also be referred to as the closed position.
  • the housing structure 24 In the second position, the housing structure 24 is detached from the first housing structure 23 so that there is a gap between a first chamber wall formed by the housing structure 23 and a second chamber wall formed by the housing structure 24 by the fluid from the delivery chamber 52 Bypass the inlet 55 and the outlet 58 can escape to the outside.
  • the second housing structure 24 assumes the first position from which it can be moved toward the second position to form the gap.
  • the movement in the direction of the second position can be carried out continuously, ie corresponding to the pressure in the delivery chamber 52, and the gap width can thus be increased continuously. Instead, the movement can happen even if it exceeds a certain one Internal pressure abruptly.
  • the gap which does not exist in the illustrated first position is indicated by "S".
  • the housing structure 24 is held in the first position by a pressing force.
  • the pressing force is generated by a pressing device 60, which acts as preferred, but only by way of example, directly on the second housing structure 24.
  • the pressing device 60 is formed by a compression spring which is designed as a corrugated ring spring. Instead of a corrugated spring and a coil spring or disc spring and basically any other suitable spring could be used.
  • the arrangement as a compression spring is preferred. Instead of a compression spring but could also be provided, for example, a tension spring to press the housing structure 24 in the first position.
  • the pressing device 60 acts axially on the housing structure 24.
  • the pressing device 60 is supported axially directly on the housing structure 24 and on one of the housing structure 24 axially facing opposite support structure 61 from. It is coaxial with the axis of rotation R and arranged circumferentially around it so that the spring axis coincides with the axis of rotation R.
  • the pressing device 60 is preferably arranged with biasing force between the housing structure 24 and the axially opposite support structure 61.
  • the adjusting structure 10 is guided axially through the housing structure 23 directly.
  • the sleeve used in the other embodiments as a guide 12 is omitted.
  • the piston 15 is movably arranged in an annular space, which is formed correspondingly directly from the housing 1 of the working pump and the housing structure 23.
  • the housing structure 23 has a guide section 29 extending almost to the rear side of the radial conveying wheel 2, which in addition also supports the return spring 17 acting on the adjusting structure 10.
  • the support structure 61 is in the region of Guide section 29 with the housing structure 23 firmly joined, in the embodiment by means of a press connection.
  • the second housing structure 24 also does not serve as a support for the pressure-retaining device 28.
  • the pressure-retaining device 28 is accommodated and supported in the first housing structure 23.
  • part of the support function of the housing structure 23 could be taken over by the housing 1 of the working or coolant pump.
  • the housing structure 24 may be arranged to translate the delivery volume of the servo pump 50 translationally, in particular axially movable. It can for example be axially guided on the drive shaft 4. But it can also on an axis of rotation R facing inner surface of the first housing structure 23, in particular a circumferential axis of rotation R circumferential inner surface of the housing structure 23, or instead on an axis extending around the axis of rotation R outer surface of the housing structure 23, in particular a circumferential axis of rotation R. Peripheral outer surface of the housing structure 23, are guided axially. In the exemplary embodiment, however, the housing structure 24 is arranged such that it can be tilted, as preferred, and can therefore be tilted about the housing structure 23 about a tilting axis K while forming the said gap.
  • FIGS. 10 and 11 show each in a opposite FIG. 9 enlarged representation of a contact region of the housing structures 23 and 24th
  • FIG. 11 shows the support region in which the housing structure 24 in the tilted state, when it assumes the second position, on the first housing structure 23 is supported to form the tilting axis K.
  • FIG. 10 shows the opposite side of the axis of rotation R, in which the housing structure 24 with the formation of the gap S of the housing structure 23 lifts when they leave the in the FIGS. 10 and 11 still shown first position moves toward the second position.
  • the housing structure 24 is located around the rotation axis R circumferentially sealed with an end face 24a on a facing End face 23a of the housing structure 23 and is pressed by the pressing device 60 in a circumferentially around the axis of rotation R dense pressure contact.
  • the housing structure 24 is rotatably connected to the housing structure 23 so as to be rotatable about the rotation axis R so that the position of the inlet 55 passing through the housing structure 24 can not vary circumferentially during the adjustment movements of the housing structure 24.
  • the housing structure 24 is guided within the scope of its mobility by means of a guide 62.
  • the guide 62 extends axially and is preferably firmly joined to the housing structure 23.
  • a feather key forms the guide 62.
  • the guide 62 protrudes axially and inwardly in the direction of the axis of rotation R in a support region containing the tilting axis K.
  • the housing structure 24 has a recess in its support region, for example, a narrow axially extending gap into which the guide 62 engages in a guiding engagement with the housing structure 24.
  • the guide 62 cooperates with the housing structure 24 in the manner of a tongue-and-groove guide, wherein the geometry could also be reversed by providing the "spring" on the housing structure 24 and the "groove” on the housing structure 23.
  • the housing structure 24 is secured relative to the housing structure 23 in its rotational angular position and allows for the adjustment of the delivery volume required mobility.
  • An advantage of the tilting mobility compared to an axial mobility of the housing structure 24 is that the risk of tilting and thereby jamming of the housing structure 24 can be avoided or at least reduced.
  • the pressure force exerted by the working fluid on the housing structure 24 acts on the housing structure 24 namely with an eccentricity with respect to the axis of rotation R, so that for a tilt-free axial guide, the pressing force would not have concentric to the axis of rotation R, but also correspondingly eccentric to the housing structure 24. Due to the tilting mobility, however, there is no danger of tilting.
  • the housing structure 23 surrounds the housing structure 24 with a peripheral inner surface 23b.
  • the circumferential inner surface 23b does not assume any bearing or guiding function for the housing structure 24. Rather, as already explained, the housing structure 24 is supported only on the facing end face 23a of the housing structure 23. Because of the cramped space conditions, the circumferential inner surface 23b of a peripheral outer surface 24b of the housing structure 24 is opposite in a very short distance.
  • the housing structure 24 is circumferentially provided with a chamfer on its circumferential outer surface 24b, as in FIG FIG. 10 is recognizable, so that the circumferential outer surface 24b merges over the chamfer in the end face 24a. The free position obtained by the chamfer is sufficient to allow the required short-stroke tilting movement in the context of the usual gap games without jamming.
  • FIG. 12 shows the Abkipp Scheme the FIG. 10 with a modification, which consists in that the housing structure 23 immediately after the end face 23a then initially has a short hollow cylindrical section to which then as in the Figures 9-11 an expanded section connects.
  • FIG. 13 shows the Abkipp Scheme again in another modification, in which on the one hand, the housing structure 24 radially opposite circumferential inner surface 23b almost cylindrical over the axial length of the housing structure 24 and on the other the housing structure 24 is spherically formed on its peripheral outer surface.
  • FIG. 14 For this variant, the support region is shown with the housing structure 24 located in the second position, the tilted position.
  • the gap S is only exaggeratedly drawn for the purpose of illustration; in fact, it suffices if the gap S in the second position in the tilting region, which lies opposite the tilting axis K facing the axis of rotation R, is only one or a few tenths of a millimeter or even less than a tenth of a millimeter.
  • the pump arrangement has a further modified filter device for the cleaning of the working fluid flowing to the servo pump 50.
  • the filter device has a stationary filter 36, which is arranged on the support structure 61 and joined for example by means of gluing or welding.
  • the filter 36 is in contrast to the coolant pump the FIGS. 1 to 6
  • a cleaning device associated with 37 which causes a mechanical cleaning of the filter 36 with rotating drive shaft 4.
  • the cleaning device 37 is formed by a scraper, which is not rotatably connected to the drive shaft 4 and seen in the flow direction to the power steering pump 50 upstream, d. H. is arranged in front of the filter 36.
  • the cleaning device 37 is pushed onto the drive shaft 4 in a positive engagement with the shaft portion 4b, whereby the rotationally fixed connection is obtained.
  • the cleaning device 37 sweeps over the front of the filter 36 facing it and scrape off dirt particles during this relative rotation.
  • the cleaning device 37 is as preferred, but only by way of example as an impeller formed with a plurality of projecting wings. Each of the wings can act as a scraper.
  • mechanical cleaning of the filter 36 may be effected with a brush acting cleaner instead of the scraping cleaner 37 or a combination of cockroaches and brushes, for example by either the blades as brushes or at least one of the blades as a brush and at least one other of the blades are formed as scrapers.
  • the scraping action can be either purely mechanical, ie only by contact, or purely fluidly or mechanically and fluidly.
  • the cleaning device 37 thus strokes in the very small distance over the facing filter surface and can thereby have contact only with adhering dirt particles and thereby strip it from the filter surface, the distance to the filter surface would be in the size range of the dirt particles.
  • the scraping effect can also be fluidic in that a rotating flow is generated by the relative rotational movement of the cleaning device 37 on the facing filter surface, and entrained adhesive particles from this flow and thus fluidly and either only or additionally removed by particle contact of the Filteraber configuration become.
  • the pump arrangement of the third embodiment corresponds to that of the first embodiment.
  • the housing structure 24 may also be movably arranged between a first position and a second position in order to be able to adjust the delivery volume of the servo pump 20 as described with reference to the third exemplary embodiment.
  • the housing structure 24 of the first embodiment like the housing structure 24 of the third embodiment, in particular tiltably movable against a pressing force. However, it must be between the housing structure 24 and the support structure 13 (for example FIG. 3 ) of the pressure device 60 may also be arranged according to a pressing device. It would also be advantageous if the pressure-retaining device 28 of the first exemplary embodiment is supported axially not on the housing structure 24 but also on the housing structure 23.
  • the outlet 27 leads through the housing structure 24 of the first embodiment, which may require the arrangement of a flexible fluid connection.
  • the housing structure 24 can be composed of at least two partial structures, namely a first partial structure, through which the outlet 27 extends and which can also support the pressure-retaining device 28, and a second movable relative to this partial structure and the first housing structure 23 Partial structure that forms the second housing structure of the claims in such modifications.
  • the servo pump 40 of the second embodiment may be modified in the manner explained for the first embodiment, in order to adjust the servo pump 40 in the delivery volume can.
  • FIGS. 1 to 8 may be provided on the respective housing structure 24 axially opposite end wall of the housing structure 23, a movable housing structure and there form the end wall of the delivery chamber or part of the end wall of the respective delivery chamber and as explained with reference to the movable housing structure 24 to be movable.
  • the servo pump 20, 40 or 50 can be adjusted in the delivery volume, it is possible, for example, to refer to the pressure limiter 35 (FIG. FIG. 4 ) are waived. In principle, however, such a pressure limiter 35 can also be provided in the case of a servo pump 20, 40 or 50 which can be adjusted in the delivery volume.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
EP13180155.7A 2012-08-14 2013-08-12 Pompe rotative avec volume d'alimentation réglable, notamment pour le réglage d'une pompe de liquide de refroidissement Withdrawn EP2698541A3 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102012214503.6A DE102012214503B4 (de) 2012-08-14 2012-08-14 Rotationspumpe mit verstellbarem Fördervolumen, insbesondere zum Verstellen einer Kühlmittelpumpe

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EP2698541A2 true EP2698541A2 (fr) 2014-02-19
EP2698541A3 EP2698541A3 (fr) 2015-09-30

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EP13180155.7A Withdrawn EP2698541A3 (fr) 2012-08-14 2013-08-12 Pompe rotative avec volume d'alimentation réglable, notamment pour le réglage d'une pompe de liquide de refroidissement

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US (1) US9416786B2 (fr)
EP (1) EP2698541A3 (fr)
CN (1) CN103591020B (fr)
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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT522124A1 (de) * 2019-02-08 2020-08-15 Tcg Unitech Systemtechnik Gmbh Radialpumpe
EP4067665A1 (fr) * 2021-03-31 2022-10-05 Airtex Products, S.A.U. Pompes de refroidissement variable

Families Citing this family (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102011113040B3 (de) * 2011-09-09 2012-04-26 Geräte- und Pumpenbau GmbH Dr. Eugen Schmidt "Regelbare Kühlmittelpumpe"
DE102014102643A1 (de) 2014-02-27 2015-08-27 Schwäbische Hüttenwerke Automotive GmbH Rotationspumpe mit Kunststoffverbundstruktur
DE102014114964B4 (de) * 2014-10-15 2016-05-25 Pierburg Gmbh Regelbare, mechanisch angetriebene Kühlmittelpumpe für eine Verbrennungskraftmaschine
CN105179382B (zh) * 2015-09-17 2017-05-10 北京精密机电控制设备研究所 一种集成式液压伺服机构用浮动通油管支撑结构
DE102015119097B4 (de) * 2015-11-06 2019-03-21 Pierburg Gmbh Kühlmittelpumpe für eine Verbrennungskraftmaschine
DE102015119095B4 (de) 2015-11-06 2019-03-21 Pierburg Gmbh Kühlmittelpumpe für eine Verbrennungskraftmaschine
CN107542570B (zh) * 2016-06-27 2021-09-10 舍弗勒技术股份两合公司 热管理模块
GB2564677B (en) * 2017-07-19 2019-07-31 Charles Austen Pumps Ltd A rotary diaphragm positive displacement pump
DE102018107776B4 (de) 2018-04-03 2020-01-23 Nidec Gpm Gmbh Hybridangetriebene Doppelpumpe
WO2019209577A1 (fr) * 2018-04-25 2019-10-31 Kickstart International, Inc. Ensemble pompe
CN114837792A (zh) 2021-03-10 2022-08-02 美普盛（上海）汽车零部件有限公司 一种带膨胀补偿密封件的电动冷却液泵
EP4341538B1 (fr) * 2021-05-20 2025-04-30 Pierburg Pump Technology GmbH Pompe mécanique à liquide de refroidissement pour véhicule à moteur pouvant être commandée
CN113464446B (zh) * 2021-07-23 2022-11-01 芜湖长江泵业有限公司 一种船用流量可调节式高压卧式单级旋涡泵
DE102022202215B4 (de) * 2022-03-04 2025-12-31 Schaeffler Technologies AG & Co. KG Ventil-Pumpen-Einheit mit einem einen Elektromotor umschließenden Mehrwegeventil
CN115507039B (zh) * 2022-10-12 2023-07-25 东莞市华汇精密机械有限公司 一种悬浊液输送泵
DE102024120435A1 (de) * 2024-07-18 2026-01-22 Nidec Gpm Gmbh Regelbare Kühlmittelpumpe mit elektrischer Nebenpumpe
EP4700245A1 (fr) * 2024-08-22 2026-02-25 Industrias Dolz, S.A.U. Pompe à eau de refroidissement mécanique commutable

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AT522124B1 (de) * 2019-02-08 2021-09-15 Tcg Unitech Systemtechnik Gmbh Radialpumpe
EP4067665A1 (fr) * 2021-03-31 2022-10-05 Airtex Products, S.A.U. Pompes de refroidissement variable

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EP2698541A3 (fr) 2015-09-30
DE102012214503A1 (de) 2014-02-20
US20140050562A1 (en) 2014-02-20
US9416786B2 (en) 2016-08-16
CN103591020A (zh) 2014-02-19
CN103591020B (zh) 2017-04-12
DE102012214503B4 (de) 2017-10-12

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