EP2754899B1 - Radial pump - Google Patents
Radial pump Download PDFInfo
- Publication number
- EP2754899B1 EP2754899B1 EP13192804.6A EP13192804A EP2754899B1 EP 2754899 B1 EP2754899 B1 EP 2754899B1 EP 13192804 A EP13192804 A EP 13192804A EP 2754899 B1 EP2754899 B1 EP 2754899B1
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- EP
- European Patent Office
- Prior art keywords
- actuating
- radial pump
- axis
- impeller
- point
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- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D15/00—Control, e.g. regulation, of pumps, pumping installations or systems
- F04D15/0027—Varying behaviour or the very pump
- F04D15/0038—Varying behaviour or the very pump by varying the effective cross-sectional area of flow through the rotor
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D15/00—Control, e.g. regulation, of pumps, pumping installations or systems
- F04D15/0005—Control, e.g. regulation, of pumps, pumping installations or systems by using valves
- F04D15/0022—Control, e.g. regulation, of pumps, pumping installations or systems by using valves throttling valves or valves varying the pump inlet opening or the outlet opening
Definitions
- the invention relates to a radial pump with a rotatably mounted in a housing about an impeller axis impeller, with a split-ring slide, which is axially movable between the impeller and an outlet region, and with an actuating element for actuating the split-ring slide, wherein in the transmission path between the actuating element and split-ring slide at least a deflectable by the actuating element Kraftumlenkelement is arranged, which is rotatably mounted in a housing-fixed bearing point about a deflection axis, wherein the force deflecting element directly or indirectly via a first point pivotally about a first pivot axis - in particular via at least one actuating rod - with the actuating element and at least one second engagement point is pivotally connected about a second pivot axis with the split-ring valve, wherein the force deflecting element is annular, ring-segment-shaped or fork-shaped and to at least partially surrounds the impeller axis, preferably at
- split gate valves It is known to carry out radial pumps with split gate valves. These have the purpose, shut off pump pressure line, but continuing pump to shut off the impeller against the pressure housing by a smooth wall and to keep in this way the hydraulic losses as low as possible.
- the adjustment of the split ring valve is usually done pneumatically by a vacuum box, hydraulically by servomotors or electrically via electromagnets.
- the DE 881 306 C describes a centrifugal pump with hydraulically adjustable split-ring valve, wherein the split-ring valve has a solid-walled in the pump housing axially guided hub disc, which itself serves as a hydraulic pressure piston.
- the hub disc is adjacent to an exit region, which is hydraulically connected to the suction side of the radial pump.
- the split-ring valve is opened by the pressure difference between the suction side and pressure side of the radial pump against the force of a closing spring. Control valves can be used to regulate the pressure difference.
- a centrifugal pump with an annular slide known, which is arranged axially movable in a side wall of the housing.
- the annular slide is displaced axially by a pressure medium, wherein the pressure medium is fed into a region adjacent to an end face of the annular slide outlet region.
- the annular slide is designed as a rotary valve and has openings that can be brought by the rotation of the slide in or out of alignment with the mouths of connecting channels that lead from the impeller to the exit area.
- the DE 199 01 123 A1 discloses a controllable radial pump for conveying a coolant for a motor vehicle, which has an adjusting device for independent of the speed of the impeller control of the medium to be transported.
- the adjusting device is operatively connected to a sleeve which is displaceable over the pump blades in the axial direction.
- the DE 10 2005 062 200 B3 describes a controllable coolant pump with a pump housing, a mounted in the pump housing driven shaft and a valve spool with an outflow region of the impeller variable overlapping outer cylinder.
- the ring-shaped valve slide is arranged on a plurality of actuating rods, which are mounted displaceably in the pump housing, wherein the valve slide is arranged opposite to the actuating rods mounted in an annular groove in the pump housing annular piston, which can be moved by means of positive or negative pressure in the annular groove.
- the AT 508 413 A1 shows a radial pump with a split-ring valve, which can be moved by an actuating element formed by a pressure cell via a lever mounted in the housing in the axial direction.
- the DE 2 255 503 A1 discloses an infinitely variable discharge rate control apparatus for centrifugal pumps, fans and blowers which has impeller passage cross section changing means formed by a split shifter and a control means which enables stepless adjustment of the respective delivery amount in accordance with the effective demand on the discharge side without interruption of operation.
- the split ring valve is by a Actuator actuated by a lever which is pivotally mounted about an axis. The lever is pivotally connected via a first point of attack with the actuating element and a second point of application pivotally connected to the split-ring valve. A fork-shaped end of the lever surrounds the impeller axis.
- the object of the invention is to avoid these disadvantages and to allow for a radial pump, a flexible arrangement of the actuating element for the split-ring valve with the least possible space occupied.
- the actuating element acts on a pressure plate on at least one actuating rod, wherein the pressure plate engages the actuating rod on an end facing away from the Kraftumlenkelement.
- the first point of attack and the second point of application of the impeller axis - preferably within a tolerance range of +/- 10% - be arranged approximately equidistant. Furthermore, the bearing point of the lever - preferably within a tolerance range of +/- 10% - be arranged the same distance from the impeller axis, as the first and second point of attack. This allows a very compact training.
- the deflection axis or the first pivot axis or the second pivot axis is arranged radially with respect to the impeller axis of the impeller, wherein preferably the force deflecting element via two second points of attack pivotally about a second Swivel axis is connected to the split ring valve. Every other point of application can - viewed in the direction of the deflection axis and / or the first and / or second pivot axis - be arranged between the housing-fixed bearing point and the first point of attack on Kraftumlenkelement.
- At least two axes from the group deflection axis, first pivot axis and second pivot axis may be arranged on different sides of the longitudinal axis including the impeller axis, wherein preferably the longitudinal plane is spanned by the impeller axis and the second pivot axis and the first pivot axis and the deflection axis on different sides with respect are arranged on this longitudinal plane.
- At least two axes of the group deflection axis, first pivot axis and second pivot axis are arranged on the same side of the impeller axis containing longitudinal plane, wherein preferably the longitudinal plane is spanned by the impeller axis and the first pivot axis and the deflection axis and the second pivot axis are arranged on the same side with respect to this longitudinal plane.
- the pressure plate is of annular design.
- a flat attack surface for the flexible membrane of the actuating element is formed.
- the pressure plate can be pivotally mounted about at least one support point in the housing so that it forms a one-sided lever.
- a first support point is arranged on a balance lever, which is rotatably mounted about a housing-fixed second support point. The balance lever thus forms an additional compensating joint to compensate for the relative movements between the pressure plate and the actuating rods.
- the deflection movement of the membrane can be transmitted to the operating rod trouble-free.
- the actuating rod can with its longitudinal axis parallel to the axis of rotation, or at an angle of not more than 35 ° inclined to the impeller axis containing Be arranged inclined longitudinal plane.
- the longitudinal plane is normal to a symmetry plane of the force deflecting element containing the impeller axis. This allows a very compact design.
- the actuating element can be formed by an overpressure or vacuum box.
- hydraulic, pneumatic, electrical or thermal actuators are possible.
- the force deflecting element is preferably designed as a one-sided lever, wherein the housing-fixed bearing point can be arranged at one end of the lever.
- the split-ring slide can be formed, for example, by a sheet-metal forming part, in particular with at least one vulcanized sealing element.
- the Spaltringschieber made of plastic, preferably made of carbon fiber reinforced plastic, wherein it is particularly advantageous if at least one sealing element is designed in one piece with the split-ring valve.
- Carbon fiber reinforced plastic has strength and tribological advantages.
- Polyether ketones (PEEK) with carbon fibers PES with carbon fibers and slip modification
- PPS polyphenylene sulfide
- PPA polyphthalamide
- PF phenol-formaldehyde resin
- the integration of the sealing element reduces the manufacturing costs.
- Plastic allows a streamlined and lightweight design.
- Another advantage is that in particular carbon fiber reinforced plastic has high resistance to cavitation.
- the split-ring slide preferably directly, is mounted on the shaft of the rotor. This can - especially when the split ring valve is made of plastic - space and parts can be saved. Utilizing the sliding properties of the plastic, the split ring pusher can be mounted directly on the shaft - without the use of additional bearing bushes.
- An unwanted twisting of the split ring valve can be prevented by a rotation. This can be formed by the Kraftumlenkelement itself.
- FIGS. Each show a radial pump 1 with an impeller 2, whose shaft 2b rotatable about an axis of rotation 2a is rotatably mounted in a housing 3 via a bearing 4.
- Reference numeral 5 designates the inlet region, with reference numeral 6 the outlet region of the radial pump 1.
- the radial pump 1 has a slit ring slide 7 which is displaceably mounted in the housing 3 and which can be displaced into the exit region 6 via the rotor 2.
- sealing elements 8 and 9 are arranged on the split-ring slide 7, as in FIG Fig. 6 is shown.
- FIG. 12 can be shown as an alternative to Fig. 6 the sealing element 8 formed, for example, by a shaft seal may be pressed into the housing 3.
- the split-ring slide 7 in this case has a thickening 7a on the impeller 2 facing away from the end, which cooperates with the sealing element 8 in the closed position of the split-ring slide 7, as in Fig. 12 can be seen.
- the drive of the impeller shaft 2 takes place in each case via a not further illustrated drive wheel.
- an actuating element 11 formed by a pressure cell is arranged within the housing 3, said actuating element 11 being arranged via an actuating rod 12 (FIG. Fig. 1 to Fig. 5 ) or two actuating rods 12 (FIG. FIG. 7 to FIG. 12 ) and a force deflecting element 13 formed by a lever 15 acts on the split-ring slide 7.
- the deflection on the actuator 11 is carried out against the restoring force of at least one example in the FIGS. 7 to 10 shown return spring 22nd
- the Kraftumlenkelement 13 is formed in each of the two embodiments by a rotatable about a deflection axis 18a one-sided annular, ring segment-shaped or fork-shaped lever 15, acts on the first lever arm 15a in a first point 16, the actuating rod 12 of the actuating element 11 and the second lever arm 15b in a second point 17 acts on the split ring valve 7.
- the lever 15 is pivotally connected in the first point 16 about a first pivot axis 16a with the actuating rod 12 or a pressure plate 12b and at least one second point 17 directly or indirectly about a second pivot axis 17a with the split ring valve 7.
- the lever 15 is rotatably mounted in a housing-fixed bearing point 18 about a deflection axis 18a.
- the second pivot axis 17a is arranged substantially radially with respect to the impeller axis 2a of the impeller 2 (FIG. Fig. 1 ).
- the first pivot axis 16a is arranged substantially radially with respect to the impeller axis 2a of the impeller 2.
- Reference symbol ⁇ designates a symmetry plane containing the impeller axis 2a.
- the actuating parts such as actuator 11 and actuating rod (s) 12 and force deflecting element 13 are arranged symmetrically to this plane of symmetry ⁇ .
- FIG. 1 to Fig. 3 such as 11 and FIG. 12 shown oblique views and sectional views are only Laufzeug - ie impeller 2 with shaft 2b - and split ring valve 7 together with actuating parts such as actuator 11 and actuating rod 12, without housing 3, shown.
- FIGS. 7 to 10 only split ring valves 7 including actuating parts such as actuating element 11 and actuating rod 12 are shown.
- the lever 15 is formed as an annular one-sided lever which concentric with the
- Impeller axis 2a is formed and arranged.
- the first point of attack 16 and the second point 17 are approximately equidistant from the impeller axis 2a.
- the bearing point 18 of the lever 15 within a tolerance range of +/- 10% of the impeller axis 2a is located equidistant, as the first point 16 and the two second points of attack 17, which are positioned diametrically opposite to the impeller axis 2a.
- the first point of attack 16 and the housing-fixed support point 18 are located at different ends of the lever 15 diametrically opposite to the impeller axis 2a.
- the second point 17 is thus arranged between the bearing point 18 and the first point 16 on the lever 12.
- the actuating element acts on the actuating rod 12 via an annular pressure plate 12b, the pressure plate 12b engaging on an end of the actuating rod 12 facing away from the force deflection element 13.
- the pressure plate 12b is - as in Fig. 3 is shown - arranged between a pressurized or negative pressure diaphragm 11b of the actuating element 11 and the actuating rod 12 and pivotally mounted about a support base 23 fixed to the housing. This has the effect that, when the actuating element 11 is deflected, the diaphragm 11b connected to the pressure plate 12b performs a slight tilting movement.
- the longitudinal axis 12a is arranged parallel to the axis of rotation 2a of the impeller 2.
- the in the FIG. 7 to FIG. 12 illustrated second embodiment differs from the first embodiment in that two substantially parallel actuating rods 12 are provided between the actuating element 11 and the Kraftumlenkelement 13.
- the longitudinal axes 12a of the two actuating rods 12 are arranged inclined at an angle ⁇ to a longitudinal axis ⁇ including the rotor axis 2a, wherein the angle ⁇ in advantageous embodiments is less than 35 °.
- the first point of application 16 and the housing-fixed support point 18 are at different ends of the lever 15.
- the second point 17 is - in a side view in the direction of the first pivot axis 16a and / or the second pivot axis 17a and / or the deflection axis 18a considered - thus arranged between the bearing point 18 and the first point 16 on the lever 12.
- the first pivot axis 16a and the deflection axis 18a are located on different sides of the lever 12.
- Das Actuator here also acts on the two actuating rods 12 via the annular pressure plate 12b, the pressure plate 12b engaging on an end of the actuating rod 12 facing away from the force deflection element 13.
- the pressure plate 12b in the second embodiment is pivotally mounted about a first support point 23a, which is arranged on a balance lever 24.
- the balancing lever 24 itself is pivotally mounted about a housing-fixed second support point 23b. The balancing lever 24 thus forms an additional compensating joint for compensating the relative movements between the pressure plate 12 b and the actuating rods 12.
- actuators 11 can be positioned relatively freely within the housing 3, which allows high design freedom, without affecting the space in a disadvantageous manner.
Description
Die Erfindung betrifft eine Radialpumpe mit einem in einem Gehäuse drehbar um eine Laufradachse gelagerten Laufrad, mit einem Spaltringschieber, welcher zwischen dem Laufrad und einem Austrittsbereich axial verfahrbar ausgebildet ist, sowie mit einem Betätigungselement zum Betätigen des Spaltringschiebers, wobei im Übertragungsweg zwischen Betätigungselement und Spaltringschieber zumindest ein durch das Betätigungselement auslenkbares Kraftumlenkelement angeordnet ist, welches in einem gehäusefesten Lagerpunkt um eine Umlenkachse drehbar gelagert ist, wobei das Kraftumlenkelement direkt oder indirekt über einen ersten Angriffspunkt schwenkbar um eine erste Schwenkachse - insbesondere über zumindest eine Betätigungsstange - mit dem Betätigungselement und über zumindest einen zweiten Angriffspunkt schwenkbar um eine zweite Schwenkachse mit dem Spaltringschieber verbunden ist, wobei das Kraftumlenkelement ringförmig, ringsegmentförmig oder gabelförmig ausgebildet ist und zumindest abschnittsweise die Laufradachse umgibt, vorzugsweise zumindest abschnittsweise konzentrisch zur Laufradachse geformt ist.The invention relates to a radial pump with a rotatably mounted in a housing about an impeller axis impeller, with a split-ring slide, which is axially movable between the impeller and an outlet region, and with an actuating element for actuating the split-ring slide, wherein in the transmission path between the actuating element and split-ring slide at least a deflectable by the actuating element Kraftumlenkelement is arranged, which is rotatably mounted in a housing-fixed bearing point about a deflection axis, wherein the force deflecting element directly or indirectly via a first point pivotally about a first pivot axis - in particular via at least one actuating rod - with the actuating element and at least one second engagement point is pivotally connected about a second pivot axis with the split-ring valve, wherein the force deflecting element is annular, ring-segment-shaped or fork-shaped and to at least partially surrounds the impeller axis, preferably at least partially formed concentrically to the impeller axis.
Es ist bekannt, Radialpumpen mit Spaltringschiebern auszuführen. Diese haben den Zweck, bei abgesperrter Pumpendruckleitung, aber weiterlaufender Pumpe, das Laufrad gegen das Druckgehäuse durch eine glatte Wand abzusperren und auf diese Weise die hydraulischen Verluste möglichst gering zu halten. Das Verstellen des Spaltringschiebers erfolgt zumeist pneumatisch durch eine Unterdruckdose, hydraulisch durch Servomotoren oder elektrisch über Elektromagneten.It is known to carry out radial pumps with split gate valves. These have the purpose, shut off pump pressure line, but continuing pump to shut off the impeller against the pressure housing by a smooth wall and to keep in this way the hydraulic losses as low as possible. The adjustment of the split ring valve is usually done pneumatically by a vacuum box, hydraulically by servomotors or electrically via electromagnets.
Die
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Weitere über Hebel betätigbare Spaltringschieber von Pumpen sind aus den Veröffentlichungen
Bei bekannten Radialpumpen, insbesondere solche ohne Hebel, wird das Betätigungselement so in das Pumpengehäuse integriert, dass eine direkte Krafteinwirkung auf den Spaltringschieber erfolgt. Dadurch ergeben sich allerdings bauliche und konstruktive Zwänge, welche den Konstruktions- und Herstellungsaufwand der Radialpumpe erhöhen. Bekannte hebelbetätigte Systeme erlauben zwar eine flexible Anordnung der Betätigungselemente, haben aber wiederum den Nachteil, dass Teile des Betätigungsmechanismus wie Betätigungselement, Hebel oder dergleichen zumindest teilweise außerhalb des Gehäuses angeordnet werden müssen, was den erforderlichen Bauraum erhöht.In known radial pumps, in particular those without lever, the actuating element is integrated into the pump housing so that a direct force is applied to the split ring valve. However, this results in structural and design constraints, which increase the design and manufacturing costs of the radial pump. Although known lever-actuated systems allow a flexible arrangement of the actuators, but in turn have the disadvantage that parts of the actuating mechanism such as actuator, lever or the like must be at least partially disposed outside of the housing, which increases the required space.
Aufgabe der Erfindung ist es, diese Nachteile zu vermeiden und bei einer Radialpumpe eine flexible Anordnung des Betätigungselementes für den Spaltringschieber bei möglichst geringem beanspruchten Bauraum zu ermöglichen.The object of the invention is to avoid these disadvantages and to allow for a radial pump, a flexible arrangement of the actuating element for the split-ring valve with the least possible space occupied.
Erfindungsgemäß wird dies dadurch erreicht, dass das Betätigungselement über eine Druckplatte auf zumindest eine Betätigungsstange einwirkt, wobei die Druckplatte an der Betätigungsstange an einem dem Kraftumlenkelement abgewandten Ende angreift.According to the invention this is achieved in that the actuating element acts on a pressure plate on at least one actuating rod, wherein the pressure plate engages the actuating rod on an end facing away from the Kraftumlenkelement.
Es hat sich gezeigt, dass diese Anordnung eine sehr kompakte, raumsparende Bauweise ermöglicht, wobei der von hebelbetätigten Systemen bekannte Vorteil einer flexiblen Anordnung des Betätigungselementes beibehalten werten kann. Somit können die Vorteile von hebellosen und hebelbetätigten Systemen vereinigt werden, ohne jeweils deren spezifischen Nachteile in Kauf nehmen zu müssen.It has been found that this arrangement allows a very compact, space-saving design, whereby the advantage known from lever-operated systems of a flexible arrangement of the actuating element can be maintained. Thus, the advantages of leverless and lever operated systems can be combined without having to accept their specific disadvantages.
Dabei kann der erste Angriffspunkt und der zweite Angriffspunkt von der Laufradachse - vorzugsweise innerhalb eines Toleranzbereiches von +/- 10 % - etwa gleich weit entfernt angeordnet sein. Weiters kann der Lagerpunkt des Hebels - vorzugsweise innerhalb eines Toleranzbereiches von +/- 10 % - von der Laufradachse gleich entfernt angeordnet sein, wie der erste und zweite Angriffspunkt. Die erlaubt eine sehr kompakte Ausbildung.In this case, the first point of attack and the second point of application of the impeller axis - preferably within a tolerance range of +/- 10% - be arranged approximately equidistant. Furthermore, the bearing point of the lever - preferably within a tolerance range of +/- 10% - be arranged the same distance from the impeller axis, as the first and second point of attack. This allows a very compact training.
In einer sehr platzsparenden Anordnung ist vorgesehen, dass die Umlenkachse oder die erste Schwenkachse oder die zweite Schwenkachse radial bezüglich der Laufradachse des Laufrades angeordnet ist, wobei vorzugsweise das Kraftumlenkelement über zwei zweite Angriffspunkte schwenkbar um jeweils eine zweite Schwenkachse mit dem Spaltringschieber verbunden ist. Jeder zweite Angriffspunkt kann - in Richtung der Umlenkachse und/oder der ersten und/oder zweiten Schwenkachse betrachtet - zwischen dem gehäusefesten Lagerpunkt und dem ersten Angriffspunkt am Kraftumlenkelement angeordnet sein. Zumindest zwei Achsen aus der Gruppe Umlenkachse, erste Schwenkachse und zweite Schwenkachse können auf unterschiedlichen Seiten einer die Laufradachse beinhaltenden Längsebene angeordnet sein, wobei vorzugsweise die Längsebene durch die Laufradachse und die zweite Schwenkachse aufgespannt ist und die erste Schwenkachse und die Umlenkachse auf unterschiedlichen Seiten in Bezug auf diese Längsebene angeordnet sind.In a very space-saving arrangement it is provided that the deflection axis or the first pivot axis or the second pivot axis is arranged radially with respect to the impeller axis of the impeller, wherein preferably the force deflecting element via two second points of attack pivotally about a second Swivel axis is connected to the split ring valve. Every other point of application can - viewed in the direction of the deflection axis and / or the first and / or second pivot axis - be arranged between the housing-fixed bearing point and the first point of attack on Kraftumlenkelement. At least two axes from the group deflection axis, first pivot axis and second pivot axis may be arranged on different sides of the longitudinal axis including the impeller axis, wherein preferably the longitudinal plane is spanned by the impeller axis and the second pivot axis and the first pivot axis and the deflection axis on different sides with respect are arranged on this longitudinal plane.
Alternativ dazu ist es auch möglich, dass zumindest zwei Achsen aus der Gruppe Umlenkachse, erste Schwenkachse und zweite Schwenkachse auf der gleichen Seite einer die Laufradachse beinhaltenden Längsebene angeordnet sind, wobei vorzugsweise die Längsebene durch die Laufradachse und die erste Schwenkachse aufgespannt ist und die Umlenkachse und die zweite Schwenkachse auf der gleichen Seiten in Bezug auf diese Längsebene angeordnet sind.Alternatively, it is also possible that at least two axes of the group deflection axis, first pivot axis and second pivot axis are arranged on the same side of the impeller axis containing longitudinal plane, wherein preferably the longitudinal plane is spanned by the impeller axis and the first pivot axis and the deflection axis and the second pivot axis are arranged on the same side with respect to this longitudinal plane.
Besonders vorteilhaft ist es, wenn die Druckplatte ringförmig ausgebildet ist. Durch die zwischen einer durch eine Betätigungskraft beaufschlagten Membran des Betätigungselementes und der Betätigungsstange angeordneten Druckplatte wird eine flächige Angriffsfläche für die flexible Membran des Betätigungselementes gebildet. Die Druckplatte kann dabei schwenkbar um zumindest einen Stützpunkt derart im Gehäuse gelagert sein, dass diese einen einseitigen Hebel bildet. Um Relativbewegungen zwischen der Druckplatte und der zumindest einen Betätigungsstange auszugleichen, ist es dabei besonders vorteilhaft, wenn ein erste Stützpunkt an einem Ausgleichhebel angeordnet ist, der um einen gehäusefesten zweiten Stützpunkt drehbar gelagert ist. Der Ausgleichhebel bildet somit ein zusätzliches Ausgleichgelenk zur Kompensation der Relativbewegungen zwischen der Druckplatte und den Betätigungsstangen. Somit kann die Auslenkbewegung der Membran störungsfrei auf die Betätigungsstange übertragen werden.It is particularly advantageous if the pressure plate is of annular design. By between a acted upon by an actuating force membrane of the actuating element and the actuating rod pressure plate is a flat attack surface for the flexible membrane of the actuating element is formed. The pressure plate can be pivotally mounted about at least one support point in the housing so that it forms a one-sided lever. In order to compensate for relative movements between the pressure plate and the at least one actuating rod, it is particularly advantageous if a first support point is arranged on a balance lever, which is rotatably mounted about a housing-fixed second support point. The balance lever thus forms an additional compensating joint to compensate for the relative movements between the pressure plate and the actuating rods. Thus, the deflection movement of the membrane can be transmitted to the operating rod trouble-free.
In einer besonders bevorzugten Ausführung der Erfindung ist vorgesehen, dass genau eine Betätigungsstange oder genau zwei Betätigungsstangen und nicht mehr als ein Betätigungselement vorgesehen sind. Dadurch kann die Zahl der Bauteile und der beanspruchte Bauraum äußerst klein gehalten werden. Es ist auch problemlos möglich, das Betätigungselement und die Betätigungsstange innerhalb des Gehäuses anzuordnen.In a particularly preferred embodiment of the invention, it is provided that exactly one actuating rod or exactly two actuating rods and not more than one actuating element are provided. As a result, the number of components and the claimed space can be kept extremely small. It is also easily possible to arrange the actuating element and the actuating rod within the housing.
Die Betätigungsstange kann mit ihrer Längsachse parallel zur Laufachse, oder unter einem Winkel von maximal 35° geneigt zu einer die Laufradachse beinhaltenden Längsebene geneigt angeordnet sein. Die Längsebene steht dabei normal auf eine die Laufradachse beinhaltenden Symmetrieebene des Kraftumlenkelementes. Dies erlaubt eine sehr kompakte Bauweise.The actuating rod can with its longitudinal axis parallel to the axis of rotation, or at an angle of not more than 35 ° inclined to the impeller axis containing Be arranged inclined longitudinal plane. The longitudinal plane is normal to a symmetry plane of the force deflecting element containing the impeller axis. This allows a very compact design.
Das Betätigungselement kann durch eine Überdruck- oder Unterdruckdose gebildet sein. Alternativ dazu sind auch hydraulische, pneumatische, elektrische oder thermische Betätigungselemente möglich.The actuating element can be formed by an overpressure or vacuum box. Alternatively, hydraulic, pneumatic, electrical or thermal actuators are possible.
Das Kraftumlenkelement ist bevorzugt als einseitiger Hebel ausgebildet, wobei der gehäusefeste Lagerpunkt an einem Ende des Hebels angeordnet sein kann.The force deflecting element is preferably designed as a one-sided lever, wherein the housing-fixed bearing point can be arranged at one end of the lever.
Der Spaltringschieber kann beispielsweise durch ein Blechumformteil, insbesondere mit zumindest einem aufvulkanisierten Dichtelement, gebildet sein. Alternativ dazu kann im Rahmen der Erfindung auch vorgesehen sein, dass der Spaltringschieber aus Kunststoff, vorzugsweise aus kohlefaserverstärktem Kunststoff besteht, wobei es besonders vorteilhaft ist, wenn zumindest ein Dichtelement einteilig mit dem Spaltringschieber ausgeführt ist. Bevorzugt wird faserverstärkter, kühlmittelbeständiger und temperaturbeständiger Kunststoff mit Gleitmodifikation wie etwa Polytetrafluorethylen und Abwandlungen, Graphit, Aramid oder Molybdänsulfid, insbesondere mit Möglichkeit der chemischen Haftung von Silikon oder Kautschuk, eingesetzt. Kohlefaserverstärkter Kunststoff hat festigkeits- und tribologische Vorteile. Dabei können Polyetherketone (PEEK) mit Kohlefasern, Polyphenylensulfid (PPS) mit Kohlefasern und Gleitmodifikation, Polyphthalamid (PPA) mit Kohlefasern und Gleitmodifikation oder Phenol-Formaldehyd Harz (PF) mit Kohlefasern und Gleitmodifikation eingesetzt werden. Aber auch der Einsatz von glasfaserverstärktem Kunststoff ist möglich.The split-ring slide can be formed, for example, by a sheet-metal forming part, in particular with at least one vulcanized sealing element. Alternatively, it can also be provided within the scope of the invention that the Spaltringschieber made of plastic, preferably made of carbon fiber reinforced plastic, wherein it is particularly advantageous if at least one sealing element is designed in one piece with the split-ring valve. Preference is given to fiber-reinforced, coolant-resistant and temperature-resistant plastic with sliding modification such as polytetrafluoroethylene and modifications, graphite, aramid or molybdenum sulfide, in particular with the possibility of chemical adhesion of silicone or rubber used. Carbon fiber reinforced plastic has strength and tribological advantages. Polyether ketones (PEEK) with carbon fibers, polyphenylene sulfide (PPS) with carbon fibers and slip modification, polyphthalamide (PPA) with carbon fibers and slip modification or phenol-formaldehyde resin (PF) with carbon fibers and slip modification can be used. But also the use of glass fiber reinforced plastic is possible.
Die Integration des Dichtelementes verringert die Herstellungskosten. Kunststoff ermöglicht eine strömungsgünstige und leichte Ausführung. Ein weitere Vorteil ist, dass insbesondere kohlefaserverstärkter Kunststoff hohe Resistenz gegen Kavitation aufweist.The integration of the sealing element reduces the manufacturing costs. Plastic allows a streamlined and lightweight design. Another advantage is that in particular carbon fiber reinforced plastic has high resistance to cavitation.
Besonders vorteilhaft ist es, wenn der Spaltringschieber, vorzugsweise direkt, auf der Welle des Laufrades gelagert ist. Dadurch können - insbesondere wenn der Spaltringschieber aus Kunststoff besteht - Bauraum und Teile eingespart werden. Unter Nützung der Gleiteigenschaften des Kunststoff kann der Spaltringschieber - ohne Verwendung von zusätzlichen Lagerbuchsen - direkt auf der Welle gelagert sein.It is particularly advantageous if the split-ring slide, preferably directly, is mounted on the shaft of the rotor. This can - especially when the split ring valve is made of plastic - space and parts can be saved. Utilizing the sliding properties of the plastic, the split ring pusher can be mounted directly on the shaft - without the use of additional bearing bushes.
Ein ungewolltes Verdrehen des Spaltringschiebers kann durch eine Verdrehsicherung verhindert werden. Diese kann durch das Kraftumlenkelement selbst gebildet sein.An unwanted twisting of the split ring valve can be prevented by a rotation. This can be formed by the Kraftumlenkelement itself.
Die Erfindung wird im Folgenden anhand der Fig. näher erläutert. Es zeigen:
- Fig. 1
- eine erfindungsgemäße Radialpumpe in einer ersten Ausführungsvariante in einer Schrägansicht;
- Fig. 2
- diese Radialpumpe in einer weiteren Schrägansicht;
- Fig. 3
- diese Radialpumpe in einer geschnittenen Schrägansicht gemäß der Linie III - III in
Fig. 1 ; - Fig. 4
- diese Radialpumpe in einem weiteren Schnitt gemäß der Linie III - III in
Fig. 1 in einer Öffnungsstellung des Spaltringschiebers; - Fig. 5
- diese Radialpumpe in einem weiteren Schnitt gemäß der Linie III - III in
Fig. 1 in einer Schließstellung des Spaltringschiebers; - Fig. 6
- einen Spaltringschieber im Detail in einem Längsschnitt;
- Fig. 7
- ein Spaltringschieber samt Betätigungselement in Schließstellung einer erfindungsgemäßen Radialpumpe in einer zweiten Ausführungsvariante in einer Schrägansicht;
- Fig. 8
- diesen Spaltringschieber samt Betätigungselement in Schließstellung in einer Schrägansicht;
- Fig. 9
- den Spaltringschieber samt Betätigungselement aus
Fig. 7 in Öffnungsstellung in einer Seitenansicht; - Fig. 10
- den Spaltringschieber aus
Fig. 8 samt Betätigungselement in Schließstellung in einer Seitenansicht; - Fig. 11
- die Radialpumpe in der zweiten Ausführungsvariante der Erfindung in einem Längsschnitt in einer Öffnungsstellung des Spaltringschiebers; und
- Fig. 12
- diese Radialpumpe in einem Längsschnitt analog zu
Fig. 11 in einer Schließstellung des Spaltringschiebers.
- Fig. 1
- a radial pump according to the invention in a first embodiment in an oblique view;
- Fig. 2
- this radial pump in a further oblique view;
- Fig. 3
- this radial pump in a sectional oblique view along the line III - III in
Fig. 1 ; - Fig. 4
- this radial pump in a further section along the line III - III in
Fig. 1 in an open position of the split ring valve; - Fig. 5
- this radial pump in a further section along the line III - III in
Fig. 1 in a closed position of the split-ring slide; - Fig. 6
- a split ring valve in detail in a longitudinal section;
- Fig. 7
- a split-ring slide including actuator in the closed position of a radial pump according to the invention in a second embodiment in an oblique view;
- Fig. 8
- this split-ring slide including actuator in the closed position in an oblique view;
- Fig. 9
- the split ring slide including actuator
Fig. 7 in the open position in a side view; - Fig. 10
- the split ring valve
Fig. 8 including actuator in the closed position in a side view; - Fig. 11
- the radial pump in the second embodiment of the invention in a longitudinal section in an open position of the split ring valve; and
- Fig. 12
- this radial pump in a longitudinal section analogous to
Fig. 11 in a closed position of the split ring valve.
Funktionsgleiche Teile sind in den Ausführungsvarianten mit gleichen Bezugszeichen versehen.Functionally identical parts are provided in the embodiment variants with the same reference numerals.
Die Fig. zeigen jeweils eine Radialpumpe 1 mit einem Laufrad 2, dessen um eine Drehachse 2a drehbare Welle 2b in einem Gehäuse 3 über ein Lager 4 drehbar gelagert ist. Mit Bezugszeichen 5 ist der Eintrittsbereich, mit Bezugszeichen 6 der Austrittsbereich der Radialpumpe 1 bezeichnet.The FIGS. Each show a
Die Radialpumpe 1 weist einen im Gehäuse 3 verschiebbar gelagerten Spaltringschieber 7 auf, welcher in den Austrittsbereich 6 über das Laufrad 2 verschoben werden kann.The
Um insbesondere im geschlossenen Zustand des Spaltringschiebers 7 Leckagen zu vermeiden, sind am Spaltringschieber 7 Dichtelemente 8 und 9 angeordnet, wie in
Der Antrieb der Laufradswelle 2 erfolgt jeweils über ein nicht weiter dargestelltes Antriebsrad. Zum Verschieben des Spaltringschiebers 7 ist innerhalb des Gehäuses 3 ein durch eine Druckdose gebildetes Betätigungselement 11 angeordnet, welches über eine Betätigungsstange 12 (
Das Kraftumlenkelement 13 ist in jeder der beiden Ausführungsvarianten durch einen um eine Umlenkachse 18a drehbaren einseitigen ringförmigen, ringsegmentförmigen oder gabelförmigen Hebel 15 gebildet, an dessen erstem Hebelsarm 15a in einem ersten Angriffspunkt 16 die Betätigungsstange 12 des Betätigungselements 11 angreift und dessen zweiter Hebelarm 15b in einem zweiten Angriffspunkt 17 auf den Spaltringschiebers 7 einwirkt. Der Hebel 15 ist im ersten Angriffspunkt 16 schwenkbar um eine erste Schwenkachse 16a mit der Betätigungsstange 12 oder einer Druckplatte 12b und über zumindest einen zweiten Angriffspunkt 17 direkt oder indirekt schwenkbar um eine zweite Schwenkachse 17a mit dem Spaltringschieber 7 verbunden. Der Hebel 15 ist in einem gehäusefeste Lagerpunkt 18 um eine Umlenkachse 18a drehbar gelagert.The
Im ersten Ausführungsbeispiel ist die zweite Schwenkachse 17a im Wesentlichen radial bezüglich der Laufradachse 2a des Laufrades 2 angeordnet (
Mit Bezugszeichen δ ist eine die Laufradachse 2a beinhaltende Symmetrieebene bezeichnet. Die Betätigungsteile wie Betätigungselement 11 und Betätigungsstange(n) 12 und Kraftumlenkelement 13 sind symmetrisch zu dieser Symmetrieebene δ angeordnet.Reference symbol δ designates a symmetry plane containing the
In den in den
Bei den in den
Laufradachse 2a geformt und angeordnet ist. Der erste Angriffspunkt 16 und der zweite Angriffspunkt 17 sind von der Laufradachse 2a etwa gleich weit entfernt. Weiters ist auch der Lagerpunkt 18 des Hebels 15 innerhalb eines Toleranzbereiches von +/- 10 % von der Laufradachse 2a gleich entfernt angeordnet ist, wie der erste Angriffspunkt 16 und die beiden zweiten Angriffspunkte 17, welche bezüglich der Laufradachse 2a diametral gegenüberliegend positioniert sind. Der erste Angriffspunkt 16 und der gehäusefeste Lagerungspunkt 18 befinden sich an unterschiedlichen Enden des Hebels 15 diametral bezüglich der Laufradachse 2a gegenüberliegend. Der zweite Angriffspunkt 17 ist somit zwischen dem Lagerpunkt 18 und dem ersten Angriffspunkt 16 am Hebel 12 angeordnet. Somit sind die erste Schwenkachse 16a und die Umlenkachse 18a an unterschiedlichen Seiten der Laufradachse 2a - bezogen auf eine die Laufradachse 2a beinhaltenden Längsebene ε angeordnet, welche normal zur Symmetrieebene δ ausgebildet ist. Das Betätigungselement wirkt über eine ringförmige Druckplatte 12b auf die Betätigungsstange 12 ein, wobei die Druckplatte 12b an einem dem Kraftumlenkelement 13 abgewandten Ende der Betätigungsstange 12 angreift. Die Druckplatte 12b ist - wie in
Bei dem in den
Wie beim ersten Ausführungsbeispiel befinden sich der erste Angriffspunkt 16 und der gehäusefeste Lagerungspunkt 18 an unterschiedlichen Enden des Hebels 15. Der zweite Angriffspunkt 17 ist - in einer Seitenansicht in Richtung der ersten Schwenkachse 16a und/oder der zweiten Schwenkachse 17a und/oder der Umlenkachse 18a betrachtet - somit zwischen dem Lagerpunkt 18 und dem ersten Angriffspunkt 16 am Hebel 12 angeordnet. Die erste Schwenkachse 16a und die Umlenkachse 18a befinden sich an unterschiedlichen Seiten des Hebels 12. Das Betätigungselement wirkt auch hier wieder über die ringförmige Druckplatte 12b auf die beiden Betätigungsstangen 12 ein, wobei die Druckplatte 12b an einem dem Kraftumlenkelement 13 abgewandten Ende der Betätigungsstange 12 angreift.As in the first embodiment, the first point of
Zum Unterschied zur ersten Ausführungsvariante sind die ersten und zweiten Schwenkachsen 16a, 17a sowie die Umlenkachse 18a an der gleichen Seite der die Laufradachse 2a beinhaltenden - normal zur Symmetrieebenen δ stehenden - Längsebene ε, angeordnet.In contrast to the first embodiment, the first and
Wie aus den
Allen Varianten ist gemeinsam, dass die Betätigungselemente 11 relativ frei innerhalb des Gehäuses 3 positioniert werden können, was hohe konstruktive Gestaltungsfreiheit ermöglicht, ohne den Bauraum in nachteiliger Weise zu beeinflussen. All variants have in common that the
Claims (15)
- Radial pump (1) comprising an impeller (4) mounted rotatably about an impeller axis (2a) in a housing (3), comprising a split ring slider (7) which is configured to be axially movable between the impeller (4) and an outlet region (6) as well as comprising an actuating element (11) for actuating the split ring slider (7), wherein at least one force deflecting element (13) which can be deflected by the actuating element (11) is disposed in the transmission path between actuating element (11) and split ring slider (7), which force deflecting element (13) is mounted rotatably about a deflection axis (18a) in a housing-fixed bearing point (18), wherein the force deflecting element (13) is connected directly or indirectly via a first application point (16) pivotably about a first pivot axis (16a) - preferably via at least one actuating rod (12) - to the actuating element (11) and via at least one second application point (17) pivotably about a second pivot axis (17a) to the split ring slider (7), the force deflecting element (13) is configured to be annular, ring-segment-shaped or fork-shaped and surrounds the impeller axis (2a) at least in sections, preferably is formed concentrically to the impeller axis (2a) at least in sections, characterised in that the actuating element (11) acts on at least one actuating rod (12) via a pressure plate (12b), wherein the pressure plate (12b) acts on the actuating rod (12) at an end facing away from the force deflecting element (13).
- The radial pump (1) according to claim 1, characterised in that the first application point (16) and the second application point (17) are disposed approximately at the same distance from the impeller axis (2a) - preferably within a tolerance range of +/-10%.
- The radial pump (1) according to claim 1 or 2, characterised in that the bearing point (18) of the force deflecting element (13) is disposed at the same distance from the impeller axis (2a) as the first and second application point (16, 17) - preferably within a tolerance range of +/-10%.
- The radial pump (1) according to one of claims 1 to 3, characterised in that the deflection axis (18a) or the first pivot axis (16a) or the second pivot axis (17a) is disposed radially in relation to the impeller axis (2a) of the impeller (2).
- The radial pump (1) according to one of claims 1 to 4, characterised in that the second application point (17) or two second application points (17) is or are disposed between the housing-fixed bearing point (18) and the first application point (16) on the force deflecting element (13).
- The radial pump (1) according to one of claims 1 to 5, characterised in that the force deflecting element (13) is connected via two second application points (17) pivotably about respectively one second pivot axis (17a) to the split ring slider (7).
- The radial pump (1) according to one of claims 1 to 6, characterised in that the pressure plate (12b) is configured to be annular.
- The radial pump (1) according to one of claims 1 to 7, characterised in that the pressure plate (12b) is disposed between a membrane (11b) of the actuating element (11) exposed to an actuating force and the actuating rod (12).
- The radial pump (1) according to one of claims 1 to 8, characterised in that the pressure plate (12b) is mounted pivotably or displaceably in the housing (3).
- The radial pump (1) according to one of claims 1 to 9, characterised in that the actuating element (11) is formed by a pressure sensor, preferably a negative pressure sensor.
- The radial pump (1) according to one of claims 1 to 10, characterised in that precisely one or precisely two actuating rod(s) (12) - preferably arranged parallel to one another, is or are provided for actuating the split ring slider (7), wherein preferably each actuating rod is inclined at an angle (α) of a maximum of 35° to a longitudinal plane (ε) containing the impeller axis (2a).
- The radial pump (1) according to one of claims 1 to 11, characterised in that the split ring slider (7) is secured against rotation, wherein preferably the rotation prevention is formed by the force deflecting element (13).
- The radial pump (1) according to one of claims 1 to 12, characterised in that the force-deflecting element (13) is configured as a one-sided lever (15), wherein the housing-fixed bearing point (18) is disposed at one end of the lever (15).
- The radial pump (1) according to one of claims 1 to 13, characterised in that the pressure plate (12b) is pivotably mounted about at least one support point (23; 23a, 23b).
- The radial pump (1) according to claim 14, characterised in that a first support point (23a) is disposed on a compensating lever (24) which is rotatably mounted about a housing-fixed second support point (23b).
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
ATA50005/2013A AT513770B1 (en) | 2013-01-09 | 2013-01-09 | radial pump |
Publications (3)
Publication Number | Publication Date |
---|---|
EP2754899A2 EP2754899A2 (en) | 2014-07-16 |
EP2754899A3 EP2754899A3 (en) | 2015-09-09 |
EP2754899B1 true EP2754899B1 (en) | 2018-07-25 |
Family
ID=49666945
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP13192804.6A Active EP2754899B1 (en) | 2013-01-09 | 2013-11-14 | Radial pump |
Country Status (2)
Country | Link |
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EP (1) | EP2754899B1 (en) |
AT (1) | AT513770B1 (en) |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102014019609B4 (en) * | 2014-12-30 | 2019-08-22 | Nidec Gpm Gmbh | Coolant pump |
Family Cites Families (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CH133892A (en) | 1928-07-18 | 1929-06-30 | Sulzer Ag | Centrifugal pump. |
DE881306C (en) | 1941-10-28 | 1953-06-29 | Voith Gmbh J M | Centrifugal pump with split ring protection |
GB974958A (en) | 1962-09-03 | 1964-11-11 | Dowty Fuel Syst Ltd | Fluid metering device |
BE793550A (en) | 1971-12-29 | 1973-04-16 | Gen Electric | CENTRIFUGAL PUMP WITH ADJUSTABLE DIFFUSER |
DE2255503A1 (en) | 1972-11-13 | 1974-05-16 | Heinz Knebel | DEVICE FOR CONTINUOUSLY ADJUSTABLE EMISSION VOLUME CONTROL FOR CENTRIFUGAL PUMPS, FANS AND BLOWERS |
US4802817A (en) | 1987-12-23 | 1989-02-07 | Sundstrand Corporation | Centrifugal pump with self-regulating impeller discharge shutter |
DE19901123A1 (en) | 1999-01-14 | 2000-07-20 | Bosch Gmbh Robert | Controllable radial pump, especially for supplying coolant for car has adjuster connected with sleeve which can be slid over pump blades in axial direction |
DE102005062200B3 (en) | 2005-12-23 | 2007-02-22 | Geräte- und Pumpenbau GmbH Dr. Eugen Schmidt | Adjustable coolant pump for internal combustion engine has annular valve pusher fitted to several piston rods movable in pump housing |
AT508413A1 (en) * | 2009-06-29 | 2011-01-15 | Tcg Unitech Systemtechnik Gmbh | RADIAL PUMP |
DE102011004172B3 (en) * | 2011-02-15 | 2012-03-01 | Schwäbische Hüttenwerke Automotive GmbH | Coolant pump with adjustable delivery volume |
-
2013
- 2013-01-09 AT ATA50005/2013A patent/AT513770B1/en not_active IP Right Cessation
- 2013-11-14 EP EP13192804.6A patent/EP2754899B1/en active Active
Non-Patent Citations (1)
Title |
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None * |
Also Published As
Publication number | Publication date |
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AT513770B1 (en) | 2016-06-15 |
AT513770A1 (en) | 2014-07-15 |
EP2754899A3 (en) | 2015-09-09 |
EP2754899A2 (en) | 2014-07-16 |
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