WO2010063765A2 - Dispositif de pompage de liquides ou de fluides comportant un boîtier - Google Patents

Dispositif de pompage de liquides ou de fluides comportant un boîtier Download PDF

Info

Publication number
WO2010063765A2
WO2010063765A2 PCT/EP2009/066247 EP2009066247W WO2010063765A2 WO 2010063765 A2 WO2010063765 A2 WO 2010063765A2 EP 2009066247 W EP2009066247 W EP 2009066247W WO 2010063765 A2 WO2010063765 A2 WO 2010063765A2
Authority
WO
WIPO (PCT)
Prior art keywords
rotation
elements
rotary
housing
ball
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/EP2009/066247
Other languages
German (de)
English (en)
Other versions
WO2010063765A3 (fr
Inventor
Hans Bögelein
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Individual
Original Assignee
Individual
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Individual filed Critical Individual
Priority to EP09764251A priority Critical patent/EP2370698A2/fr
Publication of WO2010063765A2 publication Critical patent/WO2010063765A2/fr
Publication of WO2010063765A3 publication Critical patent/WO2010063765A3/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C3/00—Rotary-piston machines or pumps, with non-parallel axes of movement of co-operating members, e.g. of screw type
    • F04C3/06—Rotary-piston machines or pumps, with non-parallel axes of movement of co-operating members, e.g. of screw type the axes being arranged otherwise than at an angle of 90 degrees
    • F04C3/08—Rotary-piston machines or pumps, with non-parallel axes of movement of co-operating members, e.g. of screw type the axes being arranged otherwise than at an angle of 90 degrees of intermeshing engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C3/085—Rotary-piston machines or pumps, with non-parallel axes of movement of co-operating members, e.g. of screw type the axes being arranged otherwise than at an angle of 90 degrees of intermeshing engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing the axes of cooperating members being on the same plane
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C11/00—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations
    • F04C11/001—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations of similar working principle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/18—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber

Definitions

  • the invention relates to a device for pumping
  • Liquids or fluids with at least two rotational elements according to the preamble of claim 1.
  • centrifugal pumps in which the material to be pumped is greatly accelerated and carried by the inertia through the outlet opening
  • 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.
  • 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.
  • Variable stroke volume such as inclined axial piston pumps.
  • these pumps are expensive to manufacture and expensive.
  • a pumping device can be made of a few simple components and thus makes it possible to provide a cost-effective and robust pump.
  • 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.
  • 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.
  • Rotation elements have the above-mentioned angle to each other.
  • Elevation of a rotation element has lowered the deepest in the recess of the opposite rotation element, the dead center is the
  • 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.
  • 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.
  • the shape of the rotation elements on the outside correspond to a partial cone or a partial sphere.
  • 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.
  • Bevel gears are formed.
  • 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.
  • 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.
  • the fluid to be pumped can simultaneously serve as lubrication of the pump according to the invention.
  • 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.
  • the bearing seat of at least one rotary element is formed as a partial sphere.
  • 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.
  • 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.
  • 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.
  • Seal made in two or more parts.
  • 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.
  • FIG. 1 shows a bevel gear pump according to the invention in three-dimensional
  • 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 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
  • 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
  • FIG. 12 shows a two-part sealing web for a pump according to FIG. 12
  • 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
  • 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.
  • the pumping device 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.
  • 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.
  • 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 form a cone whose intersection lies in the plane of the tooth tips.
  • 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.
  • the ball 11 is arranged, in such a way that its center is congruent with the center of Operakugelausström supraung 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.
  • 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.
  • 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
  • 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.
  • 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
  • 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).
  • the sealing land in the section 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
  • the section lines B-B and C-C are shown for the representation of the sections 5.3, 5.4 and 5.5.
  • 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.
  • 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).
  • 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.
  • the teeth 6 of the upper bevel gear 5 engage in the tooth gaps 7 of the lower bevel gear 4
  • the teeth 6 of the lower bevel gear 4 engage in the tooth gaps 7 of the upper bevel gear 5 a.
  • 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.
  • 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.
  • 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
  • a pumping device only has a part of its maximum pumping volume.
  • FIG. 9 shows a pump according to the invention in the side
  • 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.
  • 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.
  • Figure 9.2 is a plan view of a half of a
  • FIG. 10 shows the two rotation elements in FIG.
  • 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.
  • the pumping device is sealed in the circumferential direction of the rotating elements.
  • 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.
  • 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.
  • 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
  • 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.
  • 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.
  • close to a right angle to the line through the circle center of the bearing ball 11 and the adjusting rod 44.
  • 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.
  • the adjusting means 47 can be dispensed with.
  • the spring 46 By means of the spring 46, the adjusting piston 45 is pressed in the direction 51 in this case.
  • the upper rotary element is pressed into the tooth engagement region, so that the maximum flow rate of the pump is achieved.
  • 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.
  • a force is generated counter to the direction 51 by the torque.
  • 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.
  • the teeth in the tooth engagement area move away from each other and the volume flow decreases.
  • 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.
  • 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
  • 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.
  • FIGS 16 and 17 show pump systems consisting of two
  • Single pumps are combined and can deliver multiple volume flows with one drive.
  • 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.
  • various other combinations and combinations for multiple pumps are also conceivable.
  • 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.
  • 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
  • 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.
  • 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.
  • a worm gear could be provided for engagement here.
  • the drive of the rack or worm gear can be done in many ways here.
  • 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.
  • a worm gear could hydraulically drive out of the pump.
  • 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.
  • a separate drive for example, electrically, or to form a mechanical adjustment for the volume flow.
  • 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.
  • 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.
  • 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.
  • a seal of the pump over the entire adjustment is guaranteed.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

L'invention concerne un dispositif de pompage de liquides ou de fluides comportant un boîtier dans lequel un élément rotatif supérieur et un élément rotatif inférieur sont logés rotatifs, le boîtier présentant une ouverture d'entrée affectée à une zone d'aspiration, et une ouverture de sortie affectée à une zone de pression, pour le liquide ou le fluide à pomper. La zone d'aspiration est séparée de la zone de pression au moyen d'une entretoise d'étanchéité. L'élément rotatif supérieur et l'élément rotatif inférieur peuvent être accouplés à un entraînement rotatif, et sont pourvus de saillies et de cavités radiales sur leurs côtés se faisant face, les saillies de l'élément rotatif supérieur étant complémentaires aux cavités de l'élément rotatif inférieur, et les cavités de l'élément rotatif supérieur étant complémentaires aux saillies de l'élément rotatif inférieur. Les axes de rotation de l'élément rotatif supérieur et de l'élément rotatif inférieur forment un angle non nul, les saillies et les cavités de l'élément rotatif supérieur et de l'élément rotatif inférieur s'encastrant les unes avec les autres dans une partie des côtés se faisant face, et étant espacées les unes des autres dans une autre partie.
PCT/EP2009/066247 2008-12-02 2009-12-02 Dispositif de pompage de liquides ou de fluides comportant un boîtier Ceased WO2010063765A2 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP09764251A EP2370698A2 (fr) 2008-12-02 2009-12-02 Dispositif de pompage de liquides ou de fluides comportant un boîtier

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE202008015912U DE202008015912U1 (de) 2008-12-02 2008-12-02 Vorrichtung zum Pumpen von Flüssigkeiten oder Fluiden mit einem Gehäuse
DE202008015912.1 2008-12-02

Publications (2)

Publication Number Publication Date
WO2010063765A2 true WO2010063765A2 (fr) 2010-06-10
WO2010063765A3 WO2010063765A3 (fr) 2011-01-06

Family

ID=42105530

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2009/066247 Ceased WO2010063765A2 (fr) 2008-12-02 2009-12-02 Dispositif de pompage de liquides ou de fluides comportant un boîtier

Country Status (3)

Country Link
EP (1) EP2370698A2 (fr)
DE (1) DE202008015912U1 (fr)
WO (1) WO2010063765A2 (fr)

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US32372A (en) 1861-05-21 John jones
GB1308295A (en) 1969-02-25 1973-02-21 Lucas Industries Ltd Liquid pump or motor
AT369867B (de) 1981-01-08 1983-02-10 Stelzer Adolf Zahnradmaschine, insbesondere zahnradpumpe

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2064429A1 (de) * 1969-12-30 1972-01-27 Nishioka, Hideki, Kanagawa (Japan) Kugelförmige Rotationspumpe
US3817666A (en) * 1973-02-12 1974-06-18 E Wildhaber Rotary positive displacement unit
GB2442476A (en) * 2006-10-06 2008-04-09 Mark David Mortimer Hughes Rotary Positive-Displacement Machine

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US32372A (en) 1861-05-21 John jones
GB1308295A (en) 1969-02-25 1973-02-21 Lucas Industries Ltd Liquid pump or motor
AT369867B (de) 1981-01-08 1983-02-10 Stelzer Adolf Zahnradmaschine, insbesondere zahnradpumpe

Also Published As

Publication number Publication date
EP2370698A2 (fr) 2011-10-05
DE202008015912U1 (de) 2010-04-15
WO2010063765A3 (fr) 2011-01-06

Similar Documents

Publication Publication Date Title
WO2015082722A2 (fr) Bielle de longueur variable d'un moteur à combustion interne
DE4200305C2 (de) Regelbare Flügelzellenpumpe in kompakter Bauweise
DE3044363C2 (fr)
DE202013103826U1 (de) Innenzahnradmaschine mit Füllstück-Rückhalteeinrichtung
EP2094980A2 (fr) Coquille de coussinet pour machine hydrostatique et machine hydrostatique pourvue de cette coquille de coussinet
WO2018007534A1 (fr) Bielle à longueur réglable et à actionnement mécanique
DE102018214481A1 (de) Hydrostatische Verdrängermaschine
DE102004021216B4 (de) Hochdruck-Innenzahnradmaschine mit mehrfacher hydrostatischer Lagerung pro Hohlrad
DE10040823A1 (de) Gefüllter Hydraulikkolben und Verfahren für dessen Herstellung
DE10044784A1 (de) Verstellvorrichtung für eine Axialkolbenmaschine in Schrägachsenbauweise
EP0846861B1 (fr) Pompe annulaire à engrenages continuellement variable
WO2016058736A1 (fr) Pompe à carburant
DE19913889B4 (de) Hubkolbenmaschine
EP1448895A1 (fr) Pompe a piston rotatif
EP3987183A1 (fr) Machine à pistons radiaux comprenant un piston à bille
DE4224075A1 (de) Hydraulisches Antriebs- und Bremssystem
WO2010063765A2 (fr) Dispositif de pompage de liquides ou de fluides comportant un boîtier
EP0929743B1 (fr) Pompe a piston radial
DE10322501A1 (de) Drehkolbenpumpe
EP2655802B1 (fr) Machine à engrenage à rapport diamètre-longueur réduit
DE4312498C2 (de) Förderpumpe
DE10226492B4 (de) Axialkolbenmaschine mit verstellbarem Kolbenhub
DE10248338A1 (de) Tauchkolbenpumpe
DE2161560A1 (de) Kolbenpumpe
DE3112930A1 (de) Axialkolbenpumpe

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 09764251

Country of ref document: EP

Kind code of ref document: A2

NENP Non-entry into the national phase

Ref country code: DE

REEP Request for entry into the european phase

Ref document number: 2009764251

Country of ref document: EP

WWE Wipo information: entry into national phase

Ref document number: 2009764251

Country of ref document: EP