WO2010063765A2 - Apparatus for pumping liquids or fluids, comprising a housing - Google Patents

Abstract

Disclosed is an apparatus for pumping liquids or fluids, comprising a housing in which an upper rotating element and a lower rotating element are rotatably mounted. The housing has an inlet associated with a suction zone and an outlet associated with a pressure zone for the liquid or fluid that is to be pumped. The suction zone is separated from the pressure zone using a sealing web. The upper and the lower rotating element can be coupled to a rotary drive unit. The facing sides of the rotating elements have radially extending elevations and depressions. The elevations on the upper rotating element are complementary to the depressions on the lower rotating element, while the depressions on the upper rotating element are complementary to the elevations on the lower rotating element. The angle between the axes of rotation of the upper rotating element and the lower rotating element is not equal to zero. The elevations and depressions on the upper and lower rotating element mesh in one subarea of the facing sides while being arranged at a distance from each other in another subarea.

Description

 Device for pumping liquids or fluids with a housing

The invention relates to a device for pumping

Liquids or fluids with at least two rotational elements according to the preamble of claim 1. In the prior art, there are a variety of devices for pumping liquids or fluids. These can initially be roughly subdivided into so-called centrifugal pumps, in which the material to be pumped is greatly accelerated and carried by the inertia through the outlet opening, and so-called positive displacement pumps, in which a volume is opened on the suction side, then sealed to a pressure side is moved and reduced there by displacement, so that the liquid contained in the volume or the fluid is pushed out to the outlet opening. Among the positive displacement pumps are, for example, piston pumps, further subdivided into reciprocating, rotary and rotary piston machines, elastic displacers such as peristaltic pumps or helical displacers. Rotary piston machines such as external or internal gear pumps are simple and inexpensive to produce, but have a non-variable displacement volume, so that a control of the transported volume is possible only on the speed of the pump.

There are also piston engines in which it is possible that

Variable stroke volume, such as inclined axial piston pumps. However, these pumps are expensive to manufacture and expensive.

For a variety of applications, for example in motor vehicle

There is a strong demand for simple, rugged pumps that can generate high pressure, allowing displacement volume control when needed, and are also suitable for small and very small displacement volumes.

The solution of this problem succeeds with a device according to

Claim 1. Advantageous developments emerge from the subclaims. A pumping device according to the present invention can be made of a few simple components and thus makes it possible to provide a cost-effective and robust pump. For this purpose, the pumping device according to the invention has a housing in which two opposite rotary elements are rotatably mounted. The rotation elements in this case have complementary elevations and depressions on the sides facing each other. In connection with an inlet opening in the housing, a suction region is formed, which is separated by a sealing web from a pressure region which has an outlet opening. The two rotation elements are arranged with their axes of rotation at an angle to each other.

This angled arrangement allows the complementary projections and depressions on the mutually facing sides of the rotation elements in a portion of its circumference in engagement with each other, while in another portion of the elevations and complementary depressions on the two surfaces are removed from each other.

Since now the elevations and depressions are in a partial region of the rotary elements in engagement with each other, can by means of

Rotation of a rotation element about a rotation axis, the second

Rotational element to be driven, the axes of rotation of the two

Rotation elements have the above-mentioned angle to each other.

As a result, the elevations and depressions move towards one another in the course of the circumference, dive into each other and move away from each other again.

The point at the revolution of the elevations and depressions, at which the

Elevation of a rotation element has lowered the deepest in the recess of the opposite rotation element, the dead center is the

Arrangement. If the elevation and the depression in the direction of rotation away from the dead center, they also move away from each other and there is an open volume space between the elevation and depression. This creates a Vacuum used to suck a liquid or fluid into the cavity between the bump and the well. The area in which the elevations and depressions move away from the dead center thus forms the suction side of the pump.

Subsequent to the suction area, the recesses of the two rotation elements are closed by means of a sealing web, so that the liquid contained in the cavity between the elevations of the respective rotation element or the fluid in the further course of rotation to the displacer, the so-called pressure side can be transported , This area lies in the direction of rotation before the dead center. The recesses of a rotary element begin to submerge in the displacement in the complementary, filled with fluid or liquid recess of the opposite rotary member and press so the liquid contained in the recess or the fluid from the recess to the outlet opening in the housing.

For the storage of the two rotation elements, it is advantageous if the outer sides of the rotation elements, d. H. the surfaces which are not arranged opposite to the respective other rotational element to perform rotationally symmetrical with respect to the axis of rotation. The housing, which preferably consists of two parts, has correspondingly complementary rotationally symmetrical recesses which serve as a bearing seat for the rotary elements. Advantageously, the shape of the rotation elements on the outside correspond to a partial cone or a partial sphere.

For supporting the rotational elements on each other, the rotational elements of the pumping device according to the invention may be provided on the mutually facing sides with a recess which has the shape of a

Partial ball having the center of the ball at the intersection of

Rotary axes of the two rotation elements is located. The term "center of the ball" is in the following with respect to part of balls or part of spherical shapes always meant the center of the solid sphere from which the part of the ball was formed Recesses is then inserted a complementary ball or part ball. Due to the bearing on the ball or part ball, the rotation elements can rotate away from each other, while the ball acts simultaneously as a seal for the recesses in the interior of the rotary member. In the outer region of the rotary element, the recesses are sealed by the housing acting as a bearing seat, while in the direction of the opposite rotational element of the sealing web takes over the sealing task. Alternatively, it is also possible, for example, to form a part-spherical recess only on one rotation element, while the other rotation element has a complementary, part-spherical recess which engages in the recess of the first rotation element.

Advantageously, the two rotation elements as

Bevel gears are formed. In a bevel gear, the elevations and depressions on the side facing the other rotary element as teeth, similar to a gear executed. The extensions of the high and low points of the teeth form at least one cone, d. H. the lines, for example, through the low point of the tooth gaps intersect at one point and have an angle to each other, so that the enveloping surface of the lines form a partial cone. The same can apply to the lines through the high point of the teeth, with at least one of the two lines of lines forming a partial cone. But it is quite possible that the other group of lines lies in one plane and thus does not form a cone. The shape of the teeth can be adapted to the respective requirements. Thus, straight toothing, helical toothing and curved toothing are possible. In order to ensure trouble-free rolling of the two bevel gear-shaped rotation elements, the tip of the pitch circle cone of both bevel gears lies at the intersection of the two axes of rotation, in which the center of the ball bearing is located.

When using the housing as a bearing seat is in the dimensioning a small radial clearance between the rotation element and

Maintain housing bearing seat so that between the rotation element and the housing during rotation of the rotary member, a lubricant film can build, which ensures a reduced friction sliding of the surfaces on each other and for receiving the axial and radial forces of the rotary elements. When using the pump, for example for pumping oil, the fluid to be pumped can simultaneously serve as lubrication of the pump according to the invention. When using a pump according to the invention for pumping low-lubricant or lubricant-free media such as diesel, gasoline or ureas, the bearing in the bearing seat of the housing can be replaced by a radial and / or axial ball bearing.

The storage of the rotational elements on a central ball allows in an advantageous embodiment of the invention, the provision of a control pump, ie the change in the flow rate by changing the displacer volume. For this purpose, the bearing seat of at least one rotary element is formed as a partial sphere. Thereby, the rotation member in the bearing seat about an axis which is perpendicular to its main axis of rotation, are rotated, so that the distance of the toothed side is changed to the toothed side of the opposite rotary member. As a result, the immersion depth of the teeth of the rotary element changes into the complementary recesses of the opposite rotary element and vice versa, the immersion depth of the teeth of the opposite rotary element in the recesses of the first rotary element. In an advantageous development of such a control pump, the bearing seat of the engageable rotation element can be designed as a separate adjustment shell, which is mounted in a part-spherical adjustment seat in the housing. The adjusting shell in turn has a bearing seat for the rotary member, in which it is mounted. By using an additional adjusting shell, it is possible to lock the rotation of the adjusting shell about the main axis of rotation of the rotary element, so that the adjusting shell is rotatably mounted exclusively about an axis perpendicular to the main axis of rotation of the rotary member. In an advantageous embodiment of the invention is the

Seal made in two or more parts. In particular, an embodiment is advantageous in which the sealing web is divided into two, so that an upper and a lower sealing web part arise and between the two sealing web halves a biasing element can be introduced, which presses the sealing web halves against the elevations or tooth heads on the adjacent rotation elements or bevel gears ,

A further embodiment of the present invention lies in the combination of several pairs of rotating elements within a common housing (double pump, multiple pump) so as to provide different pressures and / or different volume flows at the same time in a small space.

Further advantages, features, feature combinations and

Features of the invention are explained below with reference to some embodiments and in the drawings. These show in:

1 shows a bevel gear pump according to the invention in three-dimensional

Presentation,

FIG. 2 shows an exploded view of the pump according to the invention from FIG. 1,

Figure 3.1 -3.5 a bevel gear from the pump of Figures 1 and 2 in different representations,

Figure 4.1 -4.3 the sealing ridge of a pump according to the invention according to FIG

1 in different views,

Figure 5.1 -5.5 a housing shell with bearing seat of the pump of Figure 1 in different views, Figure 6.1 -6.5 the second housing shell of the pump of Figure 1 in different views,

7 shows a section through an inventive

Rotating member Ball sealing bar combination,

FIG. 8 shows a section through two rotary elements of a pump according to the invention,

FIGS. 9.1 to 9.3 show a section through a bevel gear pump according to the invention,

FIG. 10 shows a section through the teeth of a device according to the invention

Bevel gear pump in the area of the dead center,

11.1 -11.2 a section through a bevel gear pump according to the invention with a pressurization for the rotational elements,

FIG. 12 shows a two-part sealing web for a pump according to FIG

Invention,

13.1 -13.2 a bevel gear pump according to the invention with volume control,

FIG. 14 shows a further embodiment of the volume control pump according to the invention,

Figure 15 is a pump according to the invention with axial and

Radial ball bearings,

FIG. 16 shows a combination of two pumps according to the invention in a common housing with the same volume flow at different pressure, 17 shows a combination of two pumps according to the invention in a housing, each with a different volume flow and different pressure,

FIG. 18 shows an alternative embodiment of a volume control pump according to the invention,

Figure 19 An alternative embodiment for the sealing bar.

1 shows a pumping device 1 according to the invention in a three-dimensional representation, wherein a part of the housing is shown "cut open" for illustrative purposes The pumping device 1 comprises the housing halves 2 and 3 serving as bearing seats for the rotary elements 4 and The rotary elements have teeth 6 and tooth gaps 7 which lie complementary to one another on the opposite sides of the rotary elements A two-part sealing web of the individual components 8.1 and 8.2 is arranged in a partial area between the rotary elements such that the teeth 6 on the sealing web 8.1 and 8.2, and thus seal the cavity which is formed by tooth gaps 7. The sealing web 8 is connected via connecting means, such as screw, rod or bolt connections 9 with the housing halves 2 and 3 respectively.

FIG. 2 shows an exploded view of a pump device according to the invention. The two housing halves 2 and 3 are held together in the assembled state by the screws or bolts 10 shown above. In the upper half of the housing 2, a section is drawn, which allows the view into the housing half inside, where the bearing seat 14 can be seen. The rotational element 5 is seated with its top and outside in the bearing seat of the housing half 2, wherein the outer side 13 of the rotary member in the present embodiment has a surface corresponding to a spherical cutout. On the underside of the rotary member 5 are the teeth 6 and the tooth gaps 7, wherein it can be seen that the depth of the tooth gaps in the outer region of the Rotation element is greater than in the interior. This is because the extensions of the troughs and troughs of the teeth and tooth spaces intersect at a point that is the tip of the partial cones formed by the lines. In the present in Figure 2 embodiment of the invention, the lines are through the tooth tips in a plane, ie the cone of the tooth tips is degenerate into a flat disc. The lines through the bottlenecks of the tooth spaces, however, form a cone whose intersection lies in the plane of the tooth tips. In the inner region of the underside of the rotary element is a part-spherical recess, which is shown hidden in Figure 2. The center of this partial sphere is identical to the intersection of the lines through the tooth high and low points. In the recess, the ball 11 is arranged, in such a way that its center is congruent with the center of Teilkugelausnehmung and the intersections of the lines through the tooth high and low points.

The upper part 8.1 of the sealing web is fastened by means of the screw or the bolt 9 in the upper half of the housing 2. In principle, it is also possible to carry out the sealing web in one piece, but the two-part design results in manufacturing advantages. Thus, the housing halves 2, 3 are pre-assembled with the rotation elements 4, 5, wherein the rotation elements 4, 5 are held by the sealing ridge 8 in the housing half 2, 3 and thus a simple and safe installation of the two with the rotation elements 4, 5 pre-assembled Housing parts 2, 3, in which the rotation elements 4, 5 are held by the sealing web elements 8.1, 8.2, is possible.

The upper housing member 2 has a suction opening 16 through which the liquid to be pumped or the fluid is passed to the suction region of the pump. On the opposite side of the pressure region 15 can be seen, in which collects the fluid on the pressure side of the pump in front of the outlet opening, which is not shown in the figure. The lower half of the housing is basically constructed analogously, with a corresponding rotary member 4, which also has a part-spherical outer side 13 which sits in the corresponding bearing seat 14 of the lower half 3, has corresponding teeth 6 and tooth gaps 7, wherein also at the lower rotational element in According to the present embodiment, the tooth tips 6 lie in a plane, while the tooth gaps form a cone at its low point, the apex of which lies at the intersection of the lines through the tooth low points and at the same time falls into the plane through the tooth tips, a recess 12, the shape of a Part ball has and is adapted to receive the bearing ball 11 so that the center of the bearing ball 11 coincides with the Schmitt point of the cone lines through the low points of the tooth gaps. The lower housing half 3 has a recess 17 into which the lower sealing web part 8.2 can be inserted and bolted to the bolt 9 with the housing half 3.

FIG. 3 shows a rotation element in different

Representations. FIG. 3.1 shows a 3D representation of the rotary element 2, in which the inner, part-spherical recess 12, the teeth 6 and the tooth recesses 7 can be seen. FIG. 3.2 shows a view from the side where a part of the rotation element is cut along the line B (see FIG. 3.4). The cut passes through a tooth depression 7, which is recognizable on the cut side. Behind it, the tooth 6 can be seen. It can be clearly seen in FIG. 3.2 that the upper sides of the teeth of the rotary element lie in one plane, while the underside or "bottom" of the tooth recesses is inclined so that a line extending the "bottom of the valley" is the plane of the tooth tips in one point which is at the same time the tip of the sub-cone from the extension lines of the "valley bottoms" and which lies on the rotation axis of the rotation element .This point is denoted by M in Figure 3.4, Figure 3.3 shows a side view through the rotation element, taken along the line CC This cut passes through a tooth so that the high point of the cut teeth can be seen, as can be seen, the peaks of the teeth lie in a plane 18. Figure 3.5 shows the rotation element again in the uncut side view, with the teeth 6, the tooth recesses 7 and the part-circular outer side 13th

FIG. 4 shows a sealing web part 8.1 or 8.2. Figure 4.1 shows a three-dimensional representation, Figure 4.2 is a plan view and Figure 4.3 is a section through the sealing web element along the line A-A. The sealing ridge has a curved shape, which is formed on the inner side 20 for engagement with the inner bearing ball 11 (not shown). In order to compensate for the relative inclination of the rotation elements to each other, the sealing land in the section (see Figure 4.3) is wedge-shaped, so that the angle of the tooth head plane 18 of the two rotation elements 2 and 3 is compensated. Through the bore 19 of the sealing bar can be screwed to the housing halves 2 and 3 respectively.

FIG. 5 shows the lower housing half 3 in different representations. FIG. 5.1 shows a three-dimensional representation of the lower one

Housing half 3 and the bearing seat 14 and the recess 17 which is formed for receiving the lower sealing web portion. In the plan view in Figure 5.2 is the

Recess area 17 for the sealing bar 8.2 completely recognizable. In addition, the section lines B-B and C-C are shown for the representation of the sections 5.3, 5.4 and 5.5. In Figure 5.3 is a sectional side view along the line B-B shown, the end portion of the recess 17 for the sealing ridge with the bore for the bolt 9 can be seen in section, as well as the bearing seat 14 in a part-spherical design. The joining surface 21 is designed relative to the axis of rotation A of the rotary element, which is inserted into the bearing seat, so as to allow the axial angle between the two rotating elements in the assembled state.

Figure 5.4 shows a section along the line CC, again the bearing seat 14, the recess 17 for the sealing web part 8.2 and the rising joining surface 21 shows. Subsection 5.5 shows a combination of the sections from 5.3 and 5.4. FIG. 6 shows the housing half 2 in different views.

FIG. 6.1 shows a three-dimensional representation of the upper housing half 2 with the inlet opening 23, the collecting area of the suction side 24, the collecting side for the pressure side 25 and the recess 17 for the sealing web part 8.1. The joining surface 22 comes to rest on assembly of the pump on the joining surface 21 of the lower housing element 3, wherein the joining surfaces also go through the center of the pitch circle cone, the part-spherical recesses and the intersection of the axes of rotation of the rotation elements.

FIG. 6.2 shows a view in which the collecting region 24 of the suction side, the collecting region 25 of the pressure side and the recess 17 for the sealing web part 8.1 can be seen. In addition, in Figure 6.2, the intersection lines E-E, F-F and G-G for the figures 6.5, 6.4 and 6.3 are drawn. Figure 6.3 shows a section along the line G-G, in which the bearing seat 14 for the rotary member 5, the collecting chamber 24 for the suction side and the recess 17 for the sealing web part 8.2 can be seen. The joining surface 22 again runs at an angle to the axis of rotation of the rotary body (see also FIG. 6.4). In Figure 6.4, the axis of rotation A of the rotary member 5 is shown, which has a different angle of 90 ° to the joining surface 22. By combining the angles of the joining surfaces 22 and 21 in the housing parts 2 and 3, the axes of rotation of the two rotary elements 5 and 6 are given a non-zero angle in which they are inclined relative to each other. FIG. 6.5 shows the outlet opening 15 which is in connection with the collecting area of the pressure side 25 and the inlet opening 23 which is in connection with the collecting area of the suction side 24.

FIG. 7 shows a section through two rotational elements of a pump device according to the invention, which are mounted on a ball 11. The housing halves with the bearing seat are not shown in the illustration in Figure 7. The two rotary elements 4, 5 are mounted with their part-spherical recesses 12 on the ball 11. In the tooth engagement region 28, the teeth 6 of the upper bevel gear 5 engage in the tooth gaps 7 of the lower bevel gear 4 and the teeth 6 of the lower bevel gear 4 engage in the tooth gaps 7 of the upper bevel gear 5 a. By rotational drive of one of the two rotation elements, the second rotation element, which is coupled via the tooth engagement in the tooth engagement region 28 in the direction of rotation with the first rotation element, also set in rotation. On the opposite side of the tooth engagement side, the teeth 6 and tooth spaces 7 of the rotation elements 4, 5 are not engaged with each other, but they are away from each other. The cavity between the teeth 6 of the two rotary elements 4, 5 fills a sealing ridge, which is formed from the items 8.1 and 8.2. The sealing web parts are placed on the line 27 on each other, which lies in the present embodiment in a plane which is spanned by the bisector of the rotation axes of the two rotary elements 4, 5. The teeth of the upper rotary member 5 are sealed by the upper surface 29.1 of the sealing land portion 8.1, so that the tooth gap forms a closed cavity formed by bevel gear, inner bearing ball 11 and outer bearing seat of the housing (not shown) which is filled with the fluid to be pumped , The inner surface 26 of the sealing web 8.1, 8.2 is in sealing contact with the inner bearing ball 11, so that no fluid between the sealing web 8.1, 8.2 and ball 11 can escape.

FIG. 8 shows the control of the pumping volume in a schematic representation. The lower bevel gear 4 is shown with a fixed axis of rotation. In the upper bevel gear 5, the axis of rotation A5 relative to

Tilting axis A4 of the lower bevel gear to be tilted. The figure shows two different positions of the axis of rotation A5. In the position with axis angle oc 1 (axis A5.1), the tooth of a rotary element 4, 5 almost completely immersed in the tooth gap 7 of the opposite rotary element. In position 5.1 of the upper rotary element, d. H. with rotary axis A5.1 and

Achswinkel od, thus takes place maximum displacement, the volume performance of

Pumping device is set to maximum. Now the axis of rotation in the

Position A5.2 tilted with axle means oc2, so that the upper rotary element is in the position A5.2, the tooth of a rotary element immersed in

Dead center only a little way into the complementary tooth gap of the opposite rotation element, so that the displacement volume is significantly reduced. In this position, therefore, a pumping device according to the invention only has a part of its maximum pumping volume.

FIG. 9 shows a pump according to the invention in the side

Section and in section from above, wherein in the figures 9.2 and 9.3 different embodiments of the sealing ridge are shown. Figure 9.1 shows the two rotation elements of Figure 7, arranged in the housing halves 2 and 3. The sealing ridge 8 is, as shown in the drawing, partially stored in the housing halves and is supported inside the ball 1 1 from. The rotating elements 4, 5 rotate within the bearing seat in the housing halves 2 and 3. Here, it is important that the flat surfaces 14 and 30 between the rotation elements and the housing-bearing seat are suitable for forming a sliding bearing, for example by means of a corresponding coating or by a Lubrication gap that fills with oil or lubricant during operation of the pumping device.

In Figure 9.2 is a plan view of a half of a

The advantage of such an extended sealing ridge lies in the reduction of the pressure space, whereby the forces on the rotating elements and the bearings and thus Finally, the sealing bar, as shown in Figure 9.3, be made smaller.

FIG. 10 shows the two rotation elements in FIG

Meshing area. The teeth 6 of the rotary elements enter the tooth spaces 7 in the pressure area 24 and thus displace the fluid in the tooth space. In this case, by the contact of the opposing teeth with each other in the points 32, the pumping device is sealed in the circumferential direction of the rotating elements. By further rotation in the direction of rotation 33, the teeth pass through the dead center 34 and enter the suction region 25, in which the teeth 6 are removed again from the tooth spaces 7. This creates a negative pressure in the Tooth gaps through which the liquid to be pumped or the fluid is sucked and then transported over the teeth on the sealing bar in the pressure range.

Figure 11 shows another embodiment of a pumping device according to the present invention with a pressurized sealing piston 35 which is arranged in the tooth engagement region in the housing. The sealing piston 35 is pressed by a biasing means 36, such as a spring or an elastic polymer, in the tooth engagement region against the two rotation elements and ensures a minimization of the radial clearance between the rotation elements or bevel gears 4 and 5. Since the sealing piston is arranged opposite to the sealing web, be the rotational elements by the pressurized sealing piston in the region of the sealing ridge, d. H. in the transition region between the pressure and suction side, firmly pressed against the bearing seat in the housing and on the sealing web, so that the transition between the pressure and suction side, which takes place at the sealing web, is completely sealed as possible and prevents leakage from the pressure to the suction side or is minimized. The second transition from the pressure to the suction side is, as shown in FIG. 10, in the tooth engagement region, so that the second piston between the pressure side and the suction side reliably seals by the sealing piston firmly pressed against the bevel gears in this region and thus minimizes leakage losses.

The minimization of leakage losses is also a prestressed, multi-part sealing web, as shown in Figure 12. Such a sealing web consists of the sealing web parts 8.1 and 8.2, which are adapted to the bevel gear and to the inner bearing ball. Between the two sealing elements 8.1 and 8.2 there is a fastening web 37, which is fitted in grooves 38 in the sealing web elements 8.2 and 81. In the fastening web, a compression spring 39 is arranged, which presses the two sealing web elements 8.2 and 8.1 apart and thus against the teeth of the above and below rotational elements. This pressure is reinforced by an opening of the gap 40 to the pressure side, through the Liquid stored in the pressure range or the fluid to enter the fastening web 37 between the sealing web elements 8.2 and 8.1 and there as inner pressure the sealing bar elements 8.2 and 8.1 can better press against the teeth 6 of the rotary member.

FIG. 13 shows an embodiment of the invention

Flow control. For this purpose, the upper housing half 41 is modified so that the bearing seat 42 has a partial spherical shape, which essentially comprises a full hemisphere. The bearing seat for the upper rotary element 4 is partially formed by an adjusting shell 43, which is adapted on its outer side to the bearing seat in the housing half 41. The adjusting shell is mounted in the bearing seat so that it can be rotated about an axis perpendicular to the axis of rotation of the rotary member, said axis of rotation through the center of the bearing ball 11, which simultaneously the apex of the cone of the bevel gear 4 and the center of the partial sphere, the Bearing seat in the housing half 41 forms, goes. The adjusting shell in the embodiment according to FIG. 13 has an adjusting rod 44 which extends from the outer surface into an opening in the bearing seat of the housing half 41. This rod is preferably designed as a "two-bladed", ie it has at least two flat, opposite sides The rod 44 is received by a recess in an adjusting bolt 45, which is mounted in the housing half 41 so as to be displaceable substantially perpendicular to the rod 44 13, the adjusting bolt is subjected to a pressure in the direction of its longitudinal axis by means of an adjusting spring 46 and has adjusting mechanisms 47 with which it can be adjusted in the direction of its longitudinal direction. Preferably, close to a right angle, to the line through the circle center of the bearing ball 11 and the adjusting rod 44. If now the adjusting bolt 45 is moved with the adjustment mittein 47, the adjusting rod and with it the adjusting shell about the axis through the center of the bearing ball eleventh rotated and so the angle between the rotation Changed axes of the two rotary elements 4, 5, so that, as already described in Figure 8, the volume flow is adjusted. It is also advantageous in the volume-regulating

Bevel gear pump a multi-part, internally pressurized sealing web used in which by means of the spring, the recessed movements of the rotating elements can be added to the seal side. An example of such a sealing web with an upper sealing web shell 48, a lower sealing web element 49 and a compression spring 50 which presses apart the sealing shell and the sealing element is shown in FIG. 13.2.

Alternatively, it is also possible to perform the volume control internally. For this purpose, the adjusting means 47 can be dispensed with. By means of the spring 46, the adjusting piston 45 is pressed in the direction 51 in this case. As a result, the upper rotary element is pressed into the tooth engagement region, so that the maximum flow rate of the pump is achieved. Now, when the pump is put into operation, an internal pressure builds up in the tooth engagement region, which generates a torque in the upper rotary element 4 and in the adjusting shell 43 about the axis of rotation of the adjusting shell. About the adjusting rod 44, a force is generated counter to the direction 51 by the torque. Now, if the pressure in the pressure range exceeds a certain predetermined pressure, the force in the adjustment rod is greater than the counter-force of the spring 46 and the adjustment is pressed in a rotation opposite to the direction 51. As a result, the teeth in the tooth engagement area move away from each other and the volume flow decreases. With the spring 46, the desired limit pressure at which the pump reduces the flow can be adjusted.

Figure 14 shows a similar embodiment of an automatic volume-regulated pump, in which a sliding block 52 is disposed in the housing half 41 and engages in a matching groove 53 in the adjusting shell 43.

This groove leaves in conjunction with the sliding block only the movement of

Adjusting bowl in one direction of rotation too. The adjusting bolt 45 is provided with a

Compressive spring 46 biased and engages in a further groove 54 in the adjustment. This groove is formed so that upon rotation of the adjustment to the

Opening of the tooth engagement portion of the adjusting piston 45 against the compression spring 46th is pushed back. Thus, also in this embodiment, the starting point of the volume flow control in the bevel gear pump can be selected via the spring force.

FIG. 15 shows an alternative embodiment of a constant volume flow bevel gear pump for use with non-lubricating or low lubricating media. The storage takes place at this

Embodiment not via a sliding bearing in the bearing seat of the housing, but via the thrust bearings 55 and radial bearings 56. To the thrust ball bearings 55 are

Sealing rings 57 are arranged, which ensure a seal of the pump to the outside. Such pumps can be used for example for gasoline direct injection, in which a high system pressure up to 180 bar with a non-lubricating medium such as gasoline must be achieved.

Figures 16 and 17 show pump systems consisting of two

Single pumps are combined and can deliver multiple volume flows with one drive. With the pump system in FIG. 16, for example, two equal volume flows can be generated from the pumps 60 and 61 at different pressures. The arrangement in Figure 17 allows the generation of two unequal volumetric flows with different pressures from the pumps 62 and 63. Of course, various other combinations and combinations for multiple pumps are also conceivable.

With a pump according to the invention can thus be considerable

Benefits are achieved. The large meshing coverage and the reduction of the rotating parts to two makes it possible to achieve low-noise operation. The bevel gears roll in rotation without sliding to each other, whereby the wear is very low. Since a large number of teeth is selectable, a low pulsation of the pump flow rate can be achieved. By changing the axis angle, which results in a change in the meshing depth, a simple volume flow control can be realized. By means of an optimized tooth geometry, the tooth engagement over the entire width of the bevel gear can be ensured even when changing the axis angle become. A pump according to the invention is very insensitive to contamination due to its simple construction and has a high overall efficiency due to low leakage and friction losses. Due to the small number of components and the ability to produce the components in a variety of simple manufacturing processes, for example as a non-cutting molding or machining, a cost-effective production of a pump according to the invention is possible. Since a direct drive of the rotational elements via a coupling is possible, can also be dispensed with a drive shaft and the necessary storage, which further reduces costs.

FIG. 18 shows an alternative embodiment for the

Execution of the volume flow control and the sealing bar. In this embodiment, the upper rotary element 4 has a circumferential groove on the part-spherical surface, which is located in a plane perpendicular to the axis of rotation of the rotary element. This ensures that an engagement element engaging in the groove can remain in continuous engagement with the groove during rotation of the rotation element and experiences no change in position along the part-spherical surface due to a displacement of the groove, since the point of engagement does not follow the rotation of the rotation element The upper sealing web part 8.1 has a groove-complementary engagement element 67 which engages in the groove, on the side facing the lower sealing web part 8.2 the sealing web part 8.1 has elevations and recesses formed complementarily to corresponding projections and recesses in the opposite side of the lower seal land portion 8.2 (see Fig. 17) .A tooth row 65 is formed on the upper, part-spherical surface of the adjustment shell 43, into which a rack 64 intervenes. Alternatively, a worm gear could be provided for engagement here. By shifting the rack 64, the Verstallschale 43 and the upper rotary element 4 can now be tilted in the direction of rotation 70 and, as already described above, the volume flow can be controlled. It is advantageous that via the groove 66 and the engagement 67 of the upper sealing web portion 8.1 is entrained, so that eliminates the need for an internal bias between the sealing web parts.

The drive of the rack or worm gear can be done in many ways here. Advantageously, the pressure generated in the pump can be used to move the rack 64 by means of a reciprocating piston, so that an adjustment is possible without the need for an additional drive. Similarly, for example, a worm gear could hydraulically drive out of the pump. In this case, the hydraulics are then controlled via appropriately controlled valves on the pressure side of the pump or in the output region and the volume flow is adjusted in this way. It can be advantageously exploited that due to the pressure on the pressure side, an inner bias of the two rotary elements 4,5 is present, which allows control of the rack by means of a single reciprocating piston. Since the upper rotary element 4 always experiences a force for rotation in the direction 70.1 due to the pressure of the fluid in the pump, only the outlet valve of the stroke chamber of the piston has to be opened in order to tilt the rotary element 4. By the internal pressure of the pump, the hydraulic fluid is then displaced from the piston chamber via the row of teeth 65 and the rack 64. To tilt the rotary member 4 in the direction 70.2 then the inlet valve of the piston is opened and generated by the high pressure on the pressure side of the pump a compressive force in the piston, which exceeds the pressure force in the pump interior, so that the rack moves back in the other direction and the upper rotation element 4 is tilted in the direction 70.2. Alternatively, it is of course also possible to provide a separate drive, for example, electrically, or to form a mechanical adjustment for the volume flow. As a further embodiment of the adjustment of the volume flow, it would be conceivable to provide a hydraulic or pneumatic cylinder which is hinged at one end to the adjusting shell and the other end hinged to the bearing shell, so that with the pushing or pulling together of the cylinder torque the adjusting shell and subsequently applied to the rotary member, by means of which the rotary member tilted and adjusted the flow rate can be. It is important here that the articulated ends form a straight line in any operating state, which does not go through the center of the ball or part ball on which the rotation elements are mounted against each other.

FIG. 19 shows a section through the sealing web halves 8.1 and 8.2. Both sealing web halves 8.1, 8.2 have complementary elevations 68 and depressions 69, preferably with a rectangular cross-section, which engage with one another. Since the side surfaces of the elevations or depressions of the sealing web halves in each position of the adjusting shell are at least partially adjacent to each other, the pressure side of the pump is sufficiently sealed to the suction side. The advantage here is that a pressure force P results from the pressure on the pressure side of the pump located on the nearest to the pressure side elevation 68, which presses this survey 68 against the adjacent elevation 68 and thus helps to minimize leakage losses. In an advantageous embodiment of the invention, the application force of the sealing web 8.1, 8.2 can be adjusted to the tooth surfaces in addition by means of a valve or a hydraulic pressure limiter in the closed adjustment 71, so that set an optimal compromise between unavoidable leakage losses and wear of the pump by residual friction can be. During the adjustment of the upper rotary element 4 in the direction 70.2, the elevations 68 and depressions 69 can now dive deeper into one another, while the recesses 69 and elevations 68 are pulled apart when adjusting the upper rotary element 4 in the direction 70.1, but in the entire adjustment range of the upper rotary element 4 stay in touch with each other. Thus, a seal of the pump over the entire adjustment is guaranteed.

LIST OF REFERENCE NUMBERS

1 pumping device

2 housing half

3 housing half

4 rotation elements

5 rotation elements 6 teeth

7 tooth gap

8.1 individual components

8.2 Individual components

8 sealing bar

9 rod connection

10 bolts

11 ball

12 recess

13 outside

14 bearing seat

15 entrance opening

16 pressure range

17 deepening

18 level

19 hole

20 inside

21 joining surface

22 joining surface

A rotation axis

23 outlet opening

24 print side

25 suction side

26 inner surface

27 line

28 meshing area

29.1 upper surface

A5 rotary axis

A4 rotary axis od axis angle

5.1 position

A5.1 rotation axis

A5.2 position 30 plane surface

32 point

33 direction of rotation

34 dead center

35 sealing piston

37 fixing bar

38 grooves

39 compression spring

40 gap

41 housing half

42 bearing seat

43 adjustment shell

44 adjustment rod

45 adjusting bolts

47 adjustment means

48 sealing tray

49 lower sealing web element

50 compression spring

51 direction

52 sliding block

53 groove

54 groove

55 radial bearings

56 radial bearings

57 sealing ring

60, 61 pumps

62, 63 pumps

64 rack

65 rows of teeth

66 groove

67 engagement element

68 Survey

69 deepening 70,70.1, 70.2 Tipping direction

71 closed adjustment range

M WIANDANTENA TWINS B \ 0096 BOGELEIN \ 003TWO BMT RELEASE 2009 12 01 DOC

Claims

claims Device (1) for pumping liquids or fluids, comprising a housing in which an upper rotary element (4, 5) and a lower rotary element (4, 5) are rotatably mounted, the housing being associated with a suction region (24) Inlet opening (23) and a pressure range (25) associated outlet opening (15) for the liquid or fluid to be pumped and the suction region (24) by means of a sealing web (8,8.1, 8,2) is separated from the pressure region, and upper or lower rotary element (4,5) with a Rotary drive can be coupled, characterized in that the rotation elements (4,5) on the mutually facing sides with radially extending elevations (6) and depressions (7) are formed, wherein the elevations (6) on the upper rotary element (4,5 ) complementary to the depressions (7) on the lower Rotation element (4,5) and the recesses (7) on the upper rotary member (4,5) complementary to the projections (6) on the lower rotary member (4,5) are formed, and the rotation axes (A5.1, A5. 2) of the upper rotary element (4,5) and the lower rotary element (4,5) one nonzero Have angles (α1, α2) to each other, wherein the elevations (6) and recesses (7) on the upper and lower rotation element (4,5) in a partial region (28) of the mutually facing sides in engagement with each other and in another portion of each other are removed. 2. Device (1) according to claim 1, characterized in that a rotation element (4,5) has a symmetrically arranged to the respective axis of rotation recess (12) on the side facing each other, wherein the recess has the shape of a ball part, and on the another rotational element (5,4) to the recess (12) complementary, part-spherical projection is formed, or both rotation elements (4,5) arranged symmetrically to the respective axis of rotation recess (12) on the one another facing side, wherein the recess has the shape of a ball portion, and a complementary to the recesses formed ball (11) or part ball for supporting the upper and lower rotary member (4,5) in the recesses (12) is arranged. 3. Device (1) according to claim 2, characterized in that the ball-center of the ball (11), partial sphere or the part-spherical projection congruent with the intersection of the axes of rotation (A5.1, A5.2) of the upper and lower rotation element (4,5). 4. Device (1) according to one of the preceding claims, characterized in that the elevations (6) and depressions (7) are formed as a toothing, in particular as a straight toothing, helical toothing or curved toothing, wherein the upper and lower rotational element (4,5) have the same number of teeth. 5. Apparatus according to claim 4, characterized in that the Rotation elements (4, 5) are formed as bevel gears, wherein the tip of the pitch circle cone of the bevel gears in the ball center of the ball (11), part ball or the part-spherical projection is located. 6. Device (1) according to one of the preceding claims, characterized by a two-part sealing web (8.1, 8.2), wherein the Dividing line between the sealing ridge parts lies in a plane which is formed by the bisecting line of the angle between the axes of rotation (A5.1, A5.2) of the rotary elements (4,5). 7. Device (1) according to any one of the preceding claims, characterized by a multi-part sealing web, which by an inner bias, in particular by spring means (39), and / or through an opening (40) to the pressure side of the pump towards the contact pressure on the recess - / elevation side of the rotary elements (4,5) is formed. 8. Device (1) according to one of the preceding claims, characterized in that the rotational elements by a pressure element (35,36), which is substantially opposite to the engagement region (28) of the recesses / projections (6,7) is arranged, is subjected to a pressure or a bias voltage. 9. Device (1) according to one of the preceding claims, characterized in that the housing (2,3) for the rotary elements (4,5) each have a bearing seat (14,30), wherein the bearing seat (14.30) is designed as a partial cone or partial sphere and the rotation elements (4,5) have a complementary to the bearing seat (14,30) formed bearing outer side (13). 10. Device (1) according to one of the preceding claims, characterized in that at least between a rotary element (4,5) and the complementary housing portion (41) an adjusting shell (43) is arranged, wherein the adjusting shell (43) is designed as a bearing seat for the rotary member (4,5), and to the housing (41) towards a substantially Partial spherical surface, and the housing (41) has a complementary partial spherical shape, wherein the adjusting shell (43) has an engagement element (44), in particular a row of teeth on the part ball surface, for transmitting a torque to the adjusting shell (43) and in the housing (41 ) an actuating mechanism (47), in particular a rack with a row of teeth which is complementary to the row of teeth on the part ball surface, and which is designed for driving by means of mechanics, hydraulics and / or electrical, or a worm gear, or a hydraulic or pneumatic cylinder, for applying a torque to the adjusting shell (43) is formed or the adjusting shell (43) by means of a bias ung, in particular via a spring element (50), is acted upon by a torque, and by means of the torque, a rotation of the adjusting shell (43) in the housing (41) for changing the angle (α1, α2) of the axes of rotation (A5.1, A5. 2) of the rotation elements (4,5) can be performed or when exceeding a through the internal pressure of Pumping device (1) caused a limit torque rotation of the adjusting shell (43) in the housing (41) for changing the angle (α1, α2) of the rotation axes (A5.1, A5.2) of the rotation elements (4,5) is effected. 11. The device (1) according to claim 12, characterized in that the adjusting shell relative to the axis of rotation (A5.1) of the rotational element mounted in it (5) is rotatably mounted, in particular by means of a trained as a two-face engagement element (44) or by means of a Groove / sliding block (52,53) Combination in adjusting shell (43) and housing (41). 12. Device (1) according to one of the preceding claims, characterized by a mounting of the rotary elements (4,5) by means of sliding bearing, radial or axial ball bearing. 13. The device according to one of claims 10 to 12, characterized in that the rotational element (4,5) with adjusting shell (43) has a groove on the part spherical surface, which is circular in a plane perpendicular to the axis of rotation of the rotary member (4,5) extends around the surface, and a two-part sealing ridge is located between the rotary elements, wherein a sealing ridge portion has a complementary engagement element for engagement in the groove, and the sealing ridge portions on its side facing each other have complementary projections and depressions, in particular one rectangular cross-section, which are formed for engagement with each other. 14. System of two or more pumps (60,61, 62,63) according to any one of the preceding claims, characterized in that within the housing two or more pairs of rotation elements are arranged, wherein in each case a rotational element of a first pair of rotational elements by means of rotation a coupling, shaft, engaging elements or a direct connection with a rotary element of a second pair of rotary elements is connected and each pair of rotary elements a separate Suction range and a separate pressure range is assigned. 15. System according to claim 14, characterized in that the suction region of a first pair of rotational elements with the Pressure range of a second pair of rotational elements is connected. M \ MANDANTENA-Z \ MANDANTEN B \ 0096 BÖGELEIN \ 003TWO CLAIMS ENTRY ENTRY RELEASE 2009 12 01 DOC