EP2754899A2 - Radial pump - Google Patents

Abstract

The pump (1) has a force deflecting element (13) directly or indirectly pivotably connected with an actuating element (11) around a pivot axis (16a) over a contact point (16) by an actuating rod (12), and with a split-ring slider (7) around another pivot axis (17a) over another contact point (17). The deflecting element is formed in a ring-, a ring segment- or a fork shape, and sectionally formed concentric to an impeller axis (2a). The deflecting element sectionally surrounds the axis, and is rotatably mounted in a housing-fixed bearing point (18) around a deflection axis (18a). The actuating element is a vacuum actuator.

Description

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 point of attack is pivotally connected about a second pivot axis with the split-ring valve.

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. Thus, 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.

From the DE 22 62 883 C2 is a radial pump with a ring slide known, which is arranged axially inserted between the impeller and guide channels. The operation of the annular slide is effected via a piston adjacent to an outlet region in the housing by means of servo.

Furthermore, from the CH 133 892 A a centrifugal pump with an annular slide known, which is arranged axially movable in a side wall of the housing. The annular slide is moved 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. In one embodiment, 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.

Furthermore, is from the US 4,802,817 A a radial pump with self-regulating impeller outlet known, wherein in the region of the impeller outlet, an axially displaceable slide is arranged, which is automatically adjusted axially depending on the pressure in the outlet spiral.

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 annular 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.

Other over lever actuated split ring valves of pumps are from the publications DE 22 55 503 A1 or US Pat. No. 3,265,000 A known.

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-operated 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 arranged at least partially outside the housing, which increases the required space.

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.

According to the invention this is achieved in that the force deflecting element is annular, ring segment-shaped or fork-shaped and at least partially surrounding the impeller axis, preferably at least partially formed concentrically to the impeller axis.

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.

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 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 is connected via two second points of attack pivotally about a second pivot axis with 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.

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 a longitudinal axis containing the impeller axis, wherein preferably the longitudinal plane through the impeller axis and the first pivot axis is spanned and the deflection axis and the second pivot axis are arranged on the same sides with respect to this longitudinal plane.

It is particularly advantageous if the actuating element acts on the at least one actuating rod via a preferably annular pressure plate, wherein the pressure plate acts on the actuating rod on an end facing away from the force deflecting element. 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 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.

The actuating rod may be arranged with its longitudinal axis parallel to the axis of rotation, or at an angle of at most 35 ° inclined to a longitudinal axis containing the impeller axis inclined. 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. Alternatively, 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. 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.

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.

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.

An unwanted twisting of the split ring valve can be prevented by a rotation. This can be formed by the Kraftumlenkelement itself.

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.

The invention will be explained in more detail below with reference to FIG. Show it:

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.

Functionally identical parts are provided in the embodiment variants with the same reference numerals.

The 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.

In order to avoid leaks, in particular in the closed state of the split-ring slide 7, sealing elements 8 and 9 are arranged on the split-ring slide 7, as in FIG Fig. 6 is shown. As in 11 and 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. For displacing the split-ring slide 7, 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 sealing of the actuating rod 12 relative to the housing 3 via rod seals 20. 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.

In the first exemplary embodiment, the second pivot axis 17a is arranged substantially radially with respect to the impeller axis 2a of the impeller 2 (FIG. Fig. 1 ). In the second embodiment, the first pivot axis 16a is arranged substantially radially with respect to the impeller axis 2a of the impeller 2.

Reference symbol δ 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 δ.

In the in the 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. In the FIGS. 7 to 10 only split ring valves 7 including actuating parts such as actuating element 11 and actuating rod 12 are shown.

In the in the Fig. 1 to Fig. 5 illustrated first embodiments, 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. Furthermore, 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. Thus, the first pivot axis 16a and the deflection axis 18a on different sides of the impeller axis 2a - with respect to a wheel axis 2a containing longitudinal plane disposed ε, which is formed normal to the plane of symmetry δ. 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.

In the in the Fig. 1 to Fig. 5 shown first embodiments, only a single actuating rod 12 is provided, 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 α to a longitudinal axis ε including the rotor axis 2a, wherein the angle α in advantageous embodiments is less than 35 °.

As in the first embodiment, 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.

In contrast to the first embodiment, the first and second pivot axes 16a, 17a and the deflection axis 18a on the same side of the impeller axis 2a containing - normal to the symmetry planes δ standing - longitudinal plane ε arranged.

Like from the FIG. 7 to FIG. 12 shows, 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.

All variants have in common that the actuators 11 can be positioned relatively freely within the housing 3, which allows high design freedom, without affecting the space in a disadvantageous manner.

Claims (15)

Radial pump (1) having a rotor (4) rotatably mounted in a housing (3) about an impeller axis (2a), having a split-ring slide (7) which is axially movable between the impeller (4) and an exit region (6), and with an actuating element (11) for actuating the split-ring slide (7), wherein in the transmission path between the actuating element (11) and split-ring slide (7) at least one by the actuating element (11) deflectable Kraftumlenkelement (13) is arranged, which in a housing-fixed bearing point ( 18) is rotatably mounted about a deflection axis (18a), wherein the force deflecting element (13) is pivotable about a first pivot point (16a) directly or indirectly via a first engagement point (16) - preferably via at least one actuating rod (12) - with the actuating element (16). 11) and at least one second engagement point (17) pivotally connected about a second pivot axis (17a) with the split-ring slide (7), characterized gekennzeichn et, that the Kraftumlenkelement (13) is annular, ring segment-shaped or fork-shaped and at least partially surrounds the impeller axis (2a), preferably at least partially concentric with the impeller axis (2a) is formed. Radial pump (1) according to claim 1, characterized in that the first point (16) and the second point (17) of the impeller axis (2a) - are arranged approximately equidistant - preferably within a tolerance range of +/- 10%. Radial pump (1) according to claim 1 or 2, characterized in that the bearing point (18) of the Kraftumlenkelementes (13) - preferably within a tolerance range of +/- 10% - of the impeller axis (2a) is arranged the same distance as the first and second point of attack (16, 17). Radial pump (1) according to one of claims 1 to 3, characterized in that the deflection axis (18a) or the first pivot axis (16a) or the second pivot axis (17a) is arranged radially with respect to the impeller axis (2a) of the impeller (2). Radial pump (1) according to one of claims 1 to 4, characterized in that the second engagement point (17) or two second engagement points (17) between the housing-fixed bearing point (18) and the first engagement point (16) on Kraftumlenkelement (13) is arranged or are. Radial pump (1) according to one of claims 1 to 5, characterized in that the Kraftumlenkelement (13) via two second engagement points (17) is pivotally connected to a respective second pivot axis (17a) with the split-ring slide (7). Radial pump (1) according to one of claims 1 to 6, characterized in that the actuating element (11) via a preferably annular pressure plate (12b) acts on at least one actuating rod (12), wherein the pressure plate (12b) on the actuating rod (12). engages on a force deflecting element (13) facing away from the end. Radial pump (1) according to one of the claims 7, characterized in that the pressure plate (12b) is arranged between a membrane (11b) of the actuating element (11) and the actuating rod (12) acted upon by an actuating force. Radial pump (1) according to one of claims 7 or 8, characterized in that the pressure plate (12b) is pivotally or displaceably mounted in the housing (3). Radial pump (1) according to one of claims 1 to 9, characterized in that the actuating element (11) is formed by a pressure cell, preferably a vacuum box. Radial pump (1) according to one of claims 1 to 10, characterized in that exactly one or exactly two - preferably arranged parallel to each other actuating rod (s) (12) for the actuation of the split ring valve (7) is or are, preferably each Actuating rod at an angle (α) of a maximum of 35 ° to a the wheel axis (2a) containing longitudinal plane (ε) is inclined. Radial pump (1) according to one of claims 1 to 11, characterized in that the split-ring slide (7) is secured against rotation, wherein preferably the anti-rotation is formed by the Kraftumlenkelement (13). Radial pump (1) according to one of claims 1 to 12, characterized in that the Kraftumlenkelement (13) is designed as a one-sided lever (15), wherein the housing-fixed bearing point (18) at one end of the lever (15) is arranged (Fig. 1 to 5). Radial pump (1) according to one of claims 7 to 13, characterized in that the pressure plate (12b) is pivotably mounted about at least one support point (23; 23a, 23b), Radial pump (1) according to claim 14, characterized in that a first support point (23a) is arranged on a balance lever (24) which is rotatably mounted about a housing-fixed second support point (23b).

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