Abstract: A toothing for a gerotor pump comprises a plurality of outer teeth (10) at a gerotor inner element (1) and a plurality of inner teeth (20) greater by one at a gerotor outer element (2), wherein a centre (M1) of the gerotor inner element (1) is offset from a centre (M2) of the gerotor outer element (2) by an eccentricity (e), the outer teeth (10) thereby meshing with the inner teeth (20). A contour of the outer teeth (10) at the gerotor inner element (1) is essentially defined by a curve of a single ellipse from a tooth tip (11) continuously via tooth flanks (13) to a transition radius (14) towards a tooth space or a tooth root (12); wherein the principal axis of the ellipse is arranged radially to the gerotor inner element (1) and the centre of the ellipse determines a radius (Rmin) at the gerotor inner element (1) which corresponds to the maximum meshing depth of the gerotor outer element (2) between the outer teeth (10) at the meshing.

Abstract: A toothing for a gerotor pump comprises a plurality of outer teeth (10) at a gerotor inner element (1) and a plurality of inner teeth (20) greater by one at a gerotor outer element (2), wherein a centre (M1) of the gerotor inner element (1) is offset from a centre (M2) of the gerotor outer element (2) by an eccentricity (e), the outer teeth (10) thereby meshing with the inner teeth (20). A contour of the outer teeth (10) at the gerotor inner element (1) is essentially defined by a curve of a single ellipse from a tooth tip (11) continuously via tooth flanks (13) to a transition radius (14) towards a tooth space or a tooth root (12); wherein the principal axis of the ellipse is arranged radially to the gerotor inner element (1) and the centre of the ellipse determines a radius (Rmin) at the gerotor inner element (1) which corresponds to the maximum meshing depth of the gerotor outer element (2) between the outer teeth (10) at the meshing.

Abstract: A gerotor pump includes a rotor wherein only on the face wall of the rotor that lies adjacent to a pressure kidney and a suction kidney, a lubrication surface inclined in the direction of rotation of the rotor, relative to the surface plane of the face wall of the rotor, is disposed on each tooth, in each instance, over its tooth height, either starting directly in the center tooth plane or starting “offset” ahead of the center tooth plane in the direction of rotation of the rotor, which surface is formed from a level surface or multiple, always level partial surfaces that follow one another, which enclose an angle of inclination relative to the surface plane of the face wall of the rotor, in each instance, which angle lies in the range from 0.2° to 7°, in each instance.

Abstract: A gerotor pump includes a rotor wherein only on the face wall of the rotor that lies adjacent to a pressure kidney and a suction kidney, a lubrication surface inclined in the direction of rotation of the rotor, relative to the surface plane of the face wall of the rotor, is disposed on each tooth, in each instance, over its tooth height, either starting directly in the center tooth plane or starting “offset” ahead of the center tooth plane in the direction of rotation of the rotor, which surface is formed from a level surface or multiple, always level partial surfaces that follow one another, which enclose an angle of inclination relative to the surface plane of the face wall of the rotor, in each instance, which angle lies in the range from 0.2° to 7°, in each instance.

Abstract: A radial shaft seal for sealing a rotating shaft led out from a space filled with a fluid medium, for example for sealing the drive shaft of a coolant pump, minimizes wear, especially the starting wear acting upon the sealing lips in double lip sealing systems, and allows end-of-line motor tests with coolant pumps without cooling liquid for up to several hours without damages to the radial shaft seal. The radial shaft seal includes two sealing bodies, an outer lip element on the pressure side and an inner lip element on the atmosphere side, each having a sealing cylinder resting on the shaft or the sleeve, arranged in a sealing housing with a joined metal supporting body, the sealing cylinders having three adjoining sealing cylinder regions such that on each pressure side a conical inlet surface and opposite thereof on each negative pressure side a conical outlet surface are provided, in each case a cylindrical contact zone being present between the conical inlet surface and the conical outlet surface.

Abstract: A gear ring pump includes a pump bearing arranged in the housing cover. A port support is mounted in the pump housing between the impeller set and the end wall of the working chamber in a movable manner towards the driveshaft such that the port support is prevented from rotating. The port support has a suction kidney and a pressure kidney which pass through the port support separately from each other across the entire width of the port support. The thickness of the port support approximately matches the thickness of the impeller set but can also project past the thickness of the impeller set by up to 20%. The thermal expansion coefficient of the port support is approximately 70% to 120% greater than the thermal expansion coefficient of the pump housing. The driveshaft which is rotationally fixed to the inner rotor does not protrude into the port support.

Abstract: In producing tooth shapes of two toothed rings of an annular gear machine, a starting geometry of a first toothed ring, at least one quality criterion of the annular gear machine, and a desired eccentricity between rotational axes of the two toothed rings are defined. A motion is performed with the starting geometry that performs a rotational motion about its rotational axis and a revolving motion about the rotational axis of the second toothed ring. The rotational and revolving motions are coupled so the rotational angle of the eccentricity equals the product of the rotational angle and tooth count of the first toothed ring. A tooth shape contour of the second toothed ring is generated by recording the path described by the envelope of the starting geometry. If the defined quality criterion is not met, the previously used starting geometry and/or the defined eccentricity is changed and steps are repeated.

Abstract: An axial sliding bearing has a sliding ring disposed between two planar, ring-shaped sliding surfaces pressure-stressed against one another. The axial sliding bearing is overload-proof, in particular by about 30% to 80% with regard to the average pressure stress of about 30 to 40 bar per wedge segment that is usual in the case of wedge segment bearings, and at the same time, is not susceptible to axial vibrations, and, in this connection, can be easily produced in terms of production technology, and easily installed, and furthermore does not permit the “snap-over effects” that drastically impair the lubricant wedge effect, so that even under more difficult operating conditions, targeted optimal variation of the wedge angle, adapted to the operating conditions, in each instance, is always guaranteed, and great reliability of the axial sliding bearing, at a long useful lifetime, can be guaranteed, while simultaneously expanding the optimal dynamic supporting range.

Abstract: An axial sliding bearing has a sliding ring disposed between two planar, ring-shaped sliding surfaces pressure-stressed against one another. The axial sliding bearing is overload-proof, in particular by about 30% to 80% with regard to the average pressure stress of about 30 to 40 bar per wedge segment that is usual in the case of wedge segment bearings, and at the same time, is not susceptible to axial vibrations, and, in this connection, can be easily produced in terms of production technology, and easily installed, and furthermore does not permit the “snap-over effects” that drastically impair the lubricant wedge effect, so that even under more difficult operating conditions, targeted optimal variation of the wedge angle, adapted to the operating conditions, in each instance, is always guaranteed, and great reliability of the axial sliding bearing, at a long useful lifetime, can be guaranteed, while simultaneously expanding the optimal dynamic supporting range.

Abstract: A vane cell pump has a rotor mounted in a pump housing and driven by a shaft, multiple vane plates mounted in the outer circumference of this rotor, and an outer ring that surrounds the rotor and the vane plates, whereby this ring is disposed either directly in the pump housing, or in a setting ring that can be moved in the pump housing, along predetermined paths. The vane cell pump has transverse grooves disposed in the cylinder mantle surface of the rotor, between the bearing grooves of the vane plates, running over the entire rotor width, disposed parallel to the bearing grooves of the vane plates, spaced apart from the bearing grooves by a bearing crosspiece. These transverse grooves have a non-symmetrical cross-section progression, which has a low point in each cell chamber, which point is always disposed behind the cell chamber center axis, seen in the direction of rotation.

Abstract: The invention relates to a gear ring pump, in particular for use in small pump assemblies which are preferably driven by an electric motor, which are produced as pump kits, and which are used in vehicle and engine construction. The aim of the invention is to develop a gear ring pump which can be used in pump assemblies with a small housing outer diameter, the pump control times of which can be easily modified with respect to the production process in accordance with the respective customer request, and which always ensures an optimal axial gap even when using very inexpensive assemblies, such as pump housings made of aluminum and impellers made of steel, even under the extreme use conditions of an oil pump in conjunction with an internal combustion engine.

Abstract: In producing tooth shapes of two toothed rings of an annular gear machine, a starting geometry of a first toothed ring, at least one quality criterion of the annular gear machine, and a desired eccentricity between rotational axes of the two toothed rings are defined. A motion is performed with the starting geometry that performs a rotational motion about its rotational axis and a revolving motion about the rotational axis of the second toothed ring. The rotational and revolving motions are coupled so the rotational angle of the eccentricity equals the product of the rotational angle and tooth count of the first toothed ring. A tooth shape contour of the second toothed ring is generated by recording the path described by the envelope of the starting geometry. If the defined quality criterion is not met, the previously used starting geometry and/or the defined eccentricity is changed and steps are repeated.

Abstract: The invention relates to vane cell pumps having a rotor mounted in a pump housing and driven by a shaft, multiple vane plates mounted in the outer circumference of this rotor, and an outer ring that surrounds the rotor and the vane plates, whereby this ring is disposed either directly in the pump housing, or in a setting ring that can be moved in the pump housing, along predetermined paths. The purpose is to develop a new type of vane cell pump having a new type of pump chamber geometry, which guarantees optimal, complete filling, in terms of flow technology, of the pump chambers, particularly at speeds of rotation in the range from 4500 rpm to beyond 6000 rpm, and furthermore is easy to manufacture, in terms of production technology.