EP1797327B1 - Pompe à pistons rotatifs comportant un carter et deux pistons rotatifs à deux pales - Google Patents

Pompe à pistons rotatifs comportant un carter et deux pistons rotatifs à deux pales Download PDF

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Publication number
EP1797327B1
EP1797327B1 EP05783062A EP05783062A EP1797327B1 EP 1797327 B1 EP1797327 B1 EP 1797327B1 EP 05783062 A EP05783062 A EP 05783062A EP 05783062 A EP05783062 A EP 05783062A EP 1797327 B1 EP1797327 B1 EP 1797327B1
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EP
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Prior art keywords
rotary
rotary piston
pistons
pump
contour
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EP05783062A
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German (de)
English (en)
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EP1797327A1 (fr
Inventor
Alois Börger
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Borger GmbH
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Borger GmbH
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    • 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
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/12—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C2/126—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with radially from the rotor body extending elements, not necessarily co-operating with corresponding recesses in the other rotor, e.g. lobes, Roots type
    • 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
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/082—Details specially related to intermeshing engagement type machines or pumps
    • F04C2/084—Toothed wheels
    • 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
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C18/14—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F04C18/16—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type

Definitions

  • the present invention relates to a rotary pump with a pump housing and with two double-wing rotary pistons, wherein the pump housing on the one hand a medium inlet and opposite a medium outlet and an interior having in cross-section substantially the contour of an oval with two opposing semicircles of radius R, their centers have the distance A, wherein the rotary pistons are rotatably supported in opposite directions on two parallel axes, wherein the one axis passes through the one semicircular center and the other axis through the other semicircular center, each rotary piston sealing in its rotation to one in the region of the semicircles running along the housing and on the other sealingly abuts against the respective other piston, wherein each rotary piston in two diametrically opposite peripheral regions each over a circumferential angular range ⁇ an outer contour with the constant radius R order having its axis, wherein each rotary piston in its other peripheral regions in each case a continuous, non-invasive and volume inclusion-free contour having measured from the axis radii smaller than the radius R
  • a rotary lobe pump of the type mentioned is out US 1 361 423 A known.
  • This rotary lobe pump which is primarily intended as a fire pump, has a housing which has a water reservoir below the interior, in which the rotary pistons rotate.
  • This water reservoir communicates with the interior via a relatively large inlet in fluid communication.
  • the edges of the inlet are seen in the direction of rotation of the rotary piston, formed with curves and transition slopes, to achieve that a volume of water within the interior upon rotation of the piston is not abruptly, but rather steadily and with a certain transition phase separated from the volume of water in the reservoir , This is to reduce vibrations during operation of the rotary lobe pump.
  • the outlet Since the inlet is relatively large, the outlet must be made correspondingly narrower, in order to ensure a seal between inlet side and outlet side in each position of the rotary piston.
  • the disadvantage here is due to the relatively narrow outlet here to a high flow resistance for the funded by the pump water, which reduces the pump efficiency.
  • the rotary pistons used in this rotary pump are considered rectilinear in their axial direction.
  • Out EP 0 283 755 A1 is a device for distributing inhomogeneous liquids, in particular manure known.
  • This device has a distributor which comprises a supply container for supplied liquid having a plurality of outlet openings for connectable discharge lines.
  • the distribution container comprises a partitioned by intermediate walls in a plurality of separate, each having a rotary piston pair on the type of Roots rotors containing delivery chambers housing. All delivery rooms are on their diesstechnikszu slaughterhouse with each other in open connection and are provided on their liquid outlet side each with a separate outlet.
  • each separate outlet of the delivery chambers is divided into two individual outlet channels, which are each associated with one of the two cooperating rotary piston of the rotary piston pair of the associated pumping chamber.
  • the two outlet channels are alternately separated by their associated, rotating rotary pistons each of the delivery chamber and connected to this.
  • Another rotary lobe pump is off EP 0 599 333 A1 known.
  • the rotary pistons each have at their radially outer ends a radius which is smaller than the radius of the housing contour forming semicircles.
  • the center of the radius of the outer ends of the rotary pistons is offset outwardly at a radial distance from the axis about which the rotary piston in question is rotatable.
  • each radially outer end of the rotary pistons sweeps along only along a line-shaped sealing contour on the housing when the rotary pistons are rotated.
  • This only line-shaped seal has the disadvantage of high wear, which means that the rotary piston or at least parts thereof must be replaced relatively often.
  • the rotary pistons are formed with replaceable sealing strips, which each form the radially outer part of the rotary piston and are individually interchangeable.
  • the replaceable design of the sealing strips requires a relatively high design effort for the rotary piston, which makes them and thus the pump more expensive.
  • rotary piston pumps are known, for example DE 100 22 097 C1 .
  • Characteristic of rotary piston pumps are rotary pistons which have over a relatively large peripheral area an outer contour whose radius coincides with the semicircular radius of the housing and in which the center of the radius coincides with the axis about which the rotary piston is rotatable.
  • it is characteristic of the rotary pistons of a rotary piston pump that the radially outer end region of each rotary piston merges at its leading and trailing sides in each case via an acute-angled edge in a concave contour region extending in the direction of the associated axis of rotation.
  • the acute-angled edges are subject to a particularly high degree of wear in the operation of a rotary piston pump.
  • a sufficiently large gap space between the two circular pistons must be kept free to allow the medium to drain and flow in the area of cavitation, especially if the medium is a non-compressible medium, such as a liquid.
  • the acute-angled edges of the rotary pistons are usually chamfered, so that the circumference of the piston wings is reduced and it is easier for the medium to escape from the cavitation or for the medium to flow into the cavitation.
  • a reduction of the delivery rate of the pump must be accepted.
  • the DE 198 02 264 C1 and the DE 43 30 085 A1 each show a rotor pump with a pump housing, with a pair of arranged in the housing, in opposite directions rotatably rotatable rotors, which each have in the form of a helix oblique or coiled to the associated shaft extending displacer, which sealingly upon rotation of the rotors on the inside of the wall tion of the pump housing and on the other rotor fitting revolve.
  • the oblique displacer vanes reduce the pulsations in the pumped medium, but they only rest on the pump housing along a tight line.
  • each displacer has an interchangeable sealing strip.
  • the design of the rotors with the interchangeable sealing strips leads to increased manufacturing costs and thus to increased costs for the pump as a whole.
  • the object is to provide a rotary piston pump of the type mentioned, which avoids the disadvantages set forth and in which a good seal of the rotary piston to the pump housing and a low-pulsation promotion can be achieved and cavitations and associated gap currents can be avoided.
  • the rotary lobe pump should have a good efficiency and low wear and be inexpensive to manufacture and in operation.
  • the novel rotary lobe pump according to the invention combines several advantages in itself.
  • a planar seal is achieved between the rotary piston and the pump housing, which is sensitive to wear to a much lesser extent than a linear seal and at the same time effects an improved seal.
  • This ensures a longer maintenance-free operation with increased efficiency.
  • Wear-prone acute-angled edges are completely avoided in rotary lobe pump according to the invention.
  • no cavitations occur in the rotary piston pump according to the invention, because due to the absence of acute-angled edges no pressure angles occur and thus no volume of the pump to be funded by the rotary pump medium between the two rotary pistons can be included.
  • the angle ⁇ and ⁇ ensures a steady seal between the suction side and pressure side of the pump in each position of the rotary piston through the surface sealing contact with the pump housing and unwanted medium backflow between the rotary piston and housing are despite the large inlet and outlet cross sections and despite the spiraling of the rotary pistons avoided.
  • the seal between the two rotary pistons is at least linear, so that there are no worse sealing properties than in known rotary piston or rotary piston pumps.
  • the obtuse-angled edge forms a scraping edge, wherein the leading side of the rotary piston with its immediately following the Abschabekante surface area with the inner circumference of the housing includes a much less acute angle.
  • the scraping edges in their interaction with the inner peripheral surface of the housing ensure that solid particles in the medium to be conveyed in the direction of piston rotation remain largely in front of the rotary pistons and are transported further by them, without becoming trapped between the inner circumference of the housing and the rotary pistons and causing damage there.
  • the obtuse-angled edge encloses an angle between 140 and 160 °, preferably of about 150 °. On the one hand, this achieves the desired scraping function of the edge and, on the other hand, avoids too sharp an edge subject to increased wear.
  • a first axis-parallel edge of the medium inlet and the medium outlet respectively substantially at the level of one axis and a second axis-parallel edge of the medium inlet and the medium outlet respectively at the level of other axis lies.
  • Another measure for achieving the largest possible inlet and outlet cross-section is that preferably viewed in the axial direction of the rotary piston, a width of the medium inlet and the medium outlet each extends over 80 to 100% of the axial length of each rotary piston.
  • the degree of coiling of the rotary pistons may be different for different pumps, this being dependent on the particular requirements in the application. Prefers is provided that the angle of rotation ⁇ is up to 60 °.
  • the largest possible circumferential area with the constant radius R is desirable.
  • the peripheral region with the constant radius R can not exceed a certain circumferential angle range ⁇ of theoretically 90 °.
  • a circumferential angle range ⁇ between 10 ° and 60 ° is preferred for the rotary piston pump according to the invention.
  • this circumferential angle range ⁇ in any case is so small that in the course of the further contour of the rotary piston acute-angled edges are not required ,
  • the desired continuous sealing between the inlet side and the outlet side of the pump by the rotary pistons can be easily ensured by suitably adjusting the extent of this circumferential angular range ⁇ with the aforementioned twist angle and the size and / or location of medium inlet and outlet.
  • the circumferential angle range ⁇ of the circumferential region with the constant radius R is at least as great as the angle of rotation of the coiled rotary pistons. In this way it is ensured that you can put an imaginary axis-parallel linear sealing line over the entire axial length of each rotary piston and that while this imaginary sealing line on their entire length in the peripheral region with the constant radius R runs.
  • the inlet and outlet can have a width corresponding to the full axial length of the rotary pistons without losing the desired continuous seal between the inlet side and the outlet side of the pump.
  • the distance A is 1.3 to 1.7 times, preferably 1.5 times, as large as the radius R.
  • a further development of the rotary piston pump according to the invention provides that the rotary pistons, seen in cross section, each form a sequence of three convex contour regions in each of its two remaining peripheral regions, which lie between the two peripheral regions with the constant radius R, wherein two convex contour regions each one concave contour area lies.
  • This contour is a geometrically favorable way to achieve the desired continuous shape of the rotary piston, whereby the desired good seal between the two rotary piston is reliably achieved without it can lead to an inclusion of a medium volume between the rotary piston, so cavitation.
  • the invention proposes that the rotary pistons are provided with a coating or support resistant to the medium on their surfaces coming into contact with a medium to be conveyed by the rotary pump.
  • a coating or support can be easily applied to the rotary piston in the rotary piston pump according to the invention, because these are not for a Coating or edition hinderlichen acute-angled edges have.
  • the rotary piston itself, a material which is not resistant to the medium to be conveyed, because it is protected by the coating or support against attack of the medium. This is the use of cheaper material, eg. As of cast steel or tool steel instead of stainless steel, possible.
  • the possibility is created to regenerate after wear of the coating or support the rotary piston by applying a new coating or overlay and then use again in a rotary lobe pump. As a result, a substantial part of the rotary piston is reusable.
  • the coating or overlay is preferably formed by a rubber coating.
  • a rubber coating offers in terms of the protection of the rotary piston against attacks of the medium to be conveyed good properties.
  • a rubber coating improves the seal on the one hand, the rotary piston against the pump housing and on the other hand, the rotary piston up to today. This undesirable backflows are further reduced contrary to the desired conveying direction of the rotary piston pump, which improves the efficiency of the pump.
  • FIG. 1 shows a rotary lobe pump 1, which has a housing 10 and two, two-lobed rotary piston 2 arranged therein.
  • the pump housing 10 defines an interior 10 ', which in the in FIG. 1 Example shown in cross-section an oval-shaped inner contour 12 has.
  • the inner contour 12 is formed by a respective semicircular contour section 12.1, whose facing each other ends are connected by two straight contour sections 12.2.
  • an inlet 11 through which a medium to be conveyed in the flow direction 28 enters the housing 10 of the rotary lobe pump 1.
  • an outlet 11 ' is provided through which the pumped by the rotary lobe pump 1 medium leaves the pump housing 10.
  • Both the inlet 11 and the outlet 11 ' has a respective rectangular cross-section.
  • the inlet 11 is bounded by a respective perpendicular to the drawing plane upper edge 11.1 and lower edge 11.2 and by two perpendicular thereto and parallel to the plane of the drawing extending side edges 11.3.
  • the two rotary pistons 2 in the interior 10 'of the housing 10 are two parallel to each other and perpendicular to the plane of the drawing FIG. 1 extending axes 20 rotatably mounted.
  • the two axes 20 have a distance A from each other.
  • the two axes 20 coincide here in each case with the semicircular center of the semicircular contour sections 12.1 of the inner contour 12.
  • the upper edges are 11.1 and 11.1 'of inlet 11 and outlet 11 'substantially at the level of the upper axis 20 and the lower edges 11.2 and 11.2' of inlet 11 and outlet 11 'substantially equal to the lower axis 20, resulting in large and low-resistance inflow and outflow-side flow cross sections of the pump 1.
  • each rotary piston 2 has two diametrically opposite circumferential region 21, whose radius R measured from the axis 20 coincides with the radius R of the semicircular portions 12.1 of the inner contour 12.
  • these circumferential regions 21 extend with the constant radius R over a respective circumferential angle range ⁇ of the associated rotary piston 2, the circumferential angle range ⁇ in each case being approximately 40 °.
  • this peripheral region 21 so each rotary piston 2 is to form a flat seal on the semicircular portion 12.1 of the inner contour 12 of the housing 10, when moving the rotary piston 2 along the portion 12.1 during operation of the pump 1.
  • a better sealing effect and a reduced wear of the regions 21 of the rotary pistons 2 are achieved in comparison to a purely linear seal.
  • the radius, measured from the associated axis 20, is smaller than the radius R.
  • these radii are dependent on their position on the circumference of the Rotary piston 2 are each dimensioned so that the radii of the two rotary pistons 2 seen along a connecting line between the two axes 20 add in each case to form an at least line-shaped seal 27 to the distance A.
  • the contour of the rotary pistons 2 is continuous both in the circumferential regions 21 with the constant radius R and in the two other circumferential regions 22 therebetween and in particular without acute-angled edges, whereby volume inclusions or cavitations between the two rotary pistons 2 in each rotational position are avoided relative to each other become.
  • the at least line-shaped seal 27 between the two rotary pistons 2 is ensured in each rotational position of the two rotary pistons 2 relative to each other.
  • a plurality of holes 13 are visible in the background, which serve to connect a rear housing cover, which is not visible here, with the housing 10.
  • This rear housing cover can also be part of a drive unit with which the rotary piston 2 can be displaced in opposite directions.
  • FIG. 1 On the housing 10, a few further holes 13 'can be seen, which are used for releasably attaching a front-side housing cover, which is omitted here, in order to close the housing 10.
  • a front-side housing cover which is omitted here, in order to close the housing 10.
  • these can be removed from the housing 10 and installed in the housing 10 with open, the viewer side facing the housing 10 without further decomposition is required.
  • the two rotary pistons 2 are formed as coiled pistons.
  • the angle of rotation of the rotary piston 2 is considered in itself about 35 ° over the entire axial length of the rotary piston 2, that is slightly smaller than the circumferential angle range ⁇ from here about 40 ° of the peripheral regions 21 with the constant radius R. Upwards the angle of rotation is limited to those values at which the required sealing between the relatively moving parts of the pump remains assured.
  • the coiled piston 2 is achieved that pulsations in the promotion of the medium in the flow direction 28 are reduced by the rotary piston pump 1, which is advantageous or essential for many applications of the pump 1.
  • FIG. 2 shows in an enlarged view only the end face of a single coiled rotary piston 2 for a rotary piston pump according to FIG. 1 ,
  • the rotary piston 2 illustrated position of the rotary piston 2 has this at the top and bottom of a respective peripheral portion 21 with a constant radius R, measured from the axis 20 about which the rotary piston 2 is rotatable.
  • each circumferential region 21 with the constant radius R extends over a circumferential angular range ⁇ of approximately 24 °.
  • the transition from a peripheral region 21 to an adjacent peripheral region 22 forms in each case an obtuse-angled edge 26.
  • the four obtuse-angled edges 26 present on the rotary piston 2 in each case enclose an angle ⁇ . In the in FIG. 2 illustrated example, the angle ⁇ is about 150 °.
  • the obtuse-angled edges 26, which in operation, ie during rotation of the rotary piston 2, form the leading edges, have in cooperation with the in FIG. 2 Pump housing not shown a function as Abschabekanten. As a result, pinching of solid particles contained in the medium to be conveyed, between the outer periphery of the rotary piston 2 and the inner circumference of the in FIG. 2 Pump housing, not shown, largely avoided.
  • a convex region 22.1 initially follows, in which the radius of the rotary piston 2, starting from the radius R, decreases steadily in the circumferential direction, away from the peripheral region 21.
  • the rotary piston 2 on a shaft 23 which is rotatable about the axis 20 to mount.
  • a piston carrier body 24 is mounted rotationally fixed to the shaft 23 with a cylindrical basic shape.
  • the piston support body 24 On its outer circumference the piston support body 24 carries an outwardly projecting spring 24 '.
  • a piston core 25 is arranged rotationally fixed, which has a bore whose inner diameter corresponds with a clearance fit to the outer diameter of the piston carrier body 24.
  • the piston core 25 has a radially outwardly deepened, extending in the axial direction groove 25 'on its inner circumference, in the assembled state, like him FIG. 2 represents the spring 24 'receives. As a result, the rotary piston 2 is held rotationally and accurately positioned on the shaft 23.
  • FIG. 3 shows the rotary lobe pump 1 FIG. 1 in a perspective view, wherein a housing cover is omitted and wherein the viewer facing the right half of the housing 10 of the rotary lobe pump 1 is indicated in dashed lines only to make the two arranged in the housing 10 rotary piston 2 completely visible.
  • the coiled design of the rotary piston 2 is particularly clear.
  • the peripheral regions 21 of the rotary pistons 2, which cooperate sealingly with the semicircular sections 12.1 of the inner contour 12 of the housing 10, are in FIG. 3 highlighted by hatching. Between the peripheral regions 21 are the remaining peripheral regions 22 whose contour is already based on the FIG. 2 was explained.
  • Each transition from a peripheral region 21 to an adjacent peripheral region 22 is in each case formed by an obtuse-angled edge 26.
  • the respectively leading in the direction of rotation 29 edges 26 each form a Abschabekante, which cooperates with the portion 12.1 of the inner contour 12 of the housing 10 and pinching of solid particles between the rotary piston 2 and the inner contour 12 of the housing 10 largely prevented.
  • the two rotary pistons 2 are rotatable about their mutually parallel axes 20 in the sense of the rotation arrows 29 in opposite directions, to which a not shown here, known per se drive is used.
  • the pump housing 10 has here right in the foreground in dashed lines its inlet 11, which has a rectangular outline.
  • the inlet 11 is delimited by an upper edge 11.1 and at the bottom by a lower edge 11.2.
  • the upper edge 11.1 extends substantially in the height of the upper axis 20 and the lower edge 11.2 extends substantially at the level of the lower axis 20.
  • the inlet 11 is bounded by two lateral edges 11.3, parallel to each other and perpendicular to the upper edge 11.1 and lower edge 11.2 run.
  • the pump housing 10 On the opposite, here facing away from the viewer side, the pump housing 10 has its outlet 11 ', which also has a rectangular outline.
  • An outlet 11 'limiting upper edge is hidden here by the upper rotary piston 2; down the outlet 11 'is limited by a lower edge 11.2'. Furthermore, two lateral edges 11.3 'limit the outlet 11'.
  • the inlet 11 and the outlet 11 have a large free flow area, whereby a low-resistance inflow and outflow of the funded by the rotary lobe pump 1 medium is ensured.
  • the rotary piston 2 with their extending over a certain circumferential angular range peripheral regions 21 that, despite the spiraling the rotary piston 2 is always a good, complete and at the same time low-wear seal between the inlet side and the outlet side of the pump 1, regardless of the respective position of the two rotary pistons. 2
  • the rotary pistons 2 can, as in FIG. 3 shown, on its outer, coming into contact with the medium to be pumped by the rotary lobe pump 1 surfaces with a coating or support 3, in particular a rubber coating, be provided to prevent direct attack of the pumped medium on the supporting material of the rotary piston 2. Due to their elasticity, a rubber coating also offers improved sealing of both the rotary pistons 2 relative to the housing 10 and the two rotary pistons 2 against each other. In case of wear or damage, the coating or support 3 can be renewed, the rest of the rotary piston 2 is still usable.
  • FIG. 4 shows for purposes of a direct comparison with each other left a conventional rotary lobe pump and right a rotary piston pump according to the invention, each in a schematic partial cross-section only through the upper part of the pump.
  • the visible part of the pump housing 10 is here that housing part which has the semicircular portion 12.1 of the inner contour 12.
  • the rotary piston 2 of the conventional pump here is a dreierieliger rotary piston 2; Alternatively, this rotary piston 2 can also be two or four wings. Like the left part of the FIG. 4 illustrates, this rotary piston 2, regardless of the number of its wings, only with a circumferentially very narrow, practically only linear area 21 in sealing contact with the section 12.1 of the inner contour 12 of the housing 10, in the example shown here over a circumferential angle ⁇ of only about 3 °.
  • This results in the seen in the direction of rotation 29 of the rotary piston 2 leading side of the rotary piston 2 is a very acute-angled, wedge-shaped gap between the peripheral portion 22 of the rotary piston 2 and the portion 12.1 of the inner contour 12 of the housing 10, here with a gap angle of only about 5 °.
  • FIG. 4 In the right part of the FIG. 4 is the rotary lobe pump with a rotary piston 2 of the above already on the basis of FIGS. 1 to 3 equipped type.
  • This rotary piston 2 is above a circumferentially relatively large angle range ⁇ from here about 50 ° in sealing contact with the portion 12.1 of the inner contour 12 of the housing 10.
  • This area 21 is bounded in the circumferential direction to both sides by a respective obtuse edge 26; This is followed, viewed in the circumferential direction, on both sides by the further peripheral region 22.
  • the gap between the leading in the direction of rotation 29 side of the rotary piston 2 and the semicircular portion 12.1 of the inner contour 12 of the housing 10 is much less acute-angled and a much larger angle, here of about 32 °, forms.
  • This relatively large angle in front of the edge 26 between the leading side of the rotary piston 2 on the one hand and the inner contour 12 of the housing 10 on the other hand largely prevents a damaging pinching of solid particles contained in the medium to be pumped by the pump. In this way it is achieved that solid particles are largely passed through the interior 10 'of the housing 10 of the pump by means of the rotary piston 2 largely without the solid particles lead to heavy wear or even greater damage to the rotary piston 2 and the housing 10.
  • FIG. 5 shows a single rotary piston 2 from the rotary piston pump shown in Figure 3 in a perspective view.
  • the rotary piston 2 according to FIG. 5 is rotatable about its axis of rotation 20.
  • up and down facing peripheral portions 21 have a constant radius R (see. FIG. 2 ) and run during operation of the rotary lobe pump in flat sealing contact with the semicircular portions 12.1 of the inner contour 12 of the housing 10 to.
  • Each peripheral region 21 is seen in the circumferential direction bounded on both sides by a respective obtuse-angled edge 26; in the circumferential direction on both sides then follows in each case one of the two remaining peripheral regions 22 of the rotary piston 2.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
  • Reciprocating Pumps (AREA)
  • Details Of Reciprocating Pumps (AREA)

Claims (11)

  1. Pompe à pistons rotatifs (1) comportant un carter (10) et deux pistons rotatifs à deux pales (2), le carter (10) présentant d'un côté une entrée de milieu (11) et en face une sortie de milieu (11') ainsi qu'un espace interne (10') qui présente en coupe transversale essentiellement le contour d'un ovale avec deux demi-cercles se faisant face avec le rayon R dont les centres ont la distance A, les pistons rotatifs (2) étant logés sur deux axes parallèles (20) de manière rotative en sens opposé, un des axes (20) s'étendant à travers un des centres de demi-cercle et l'autre axe (20) s'étendant à travers l'autre centre de demi-cercle, chaque piston rotatif (2) passant lors de sa rotation d'une part dans la région des demi-cercles de manière étanche le long du carter (10) et reposant d'autre part de manière étanche contre l'autre piston respectif (2), chaque piston rotatif (2) présentant dans deux zones périphériques diamétralement opposées (21) à chaque fois sur une plage d'angle périphérique α un contour externe avec le rayon constant R autour de son axe (20), chaque piston rotatif (2) présentant dans ses zones périphériques restantes (22) à chaque fois un contour continu, exempt d'angle d'attaque et exempt d'inclusion de volume, avec des rayons mesurés depuis l'axe (20) inférieurs au rayon R et les rayons des deux pistons rotatifs (2) s'ajoutant vu dans la direction d'une ligne de jonction des deux axes (20) dans chaque position de rotation des pistons rotatifs (2) pour former un joint (27) au moins linéaire entre les deux pistons rotatifs (2) vers la distance constante A,
    caractérisée en ce
    - que les pistons rotatifs (2) sont réalisés vu dans leur direction axiale d'une manière s'étendant en hélice à l'opposé l'un de l'autre, un des côtés frontaux de chaque piston rotatif (2) étant à chaque fois tourné d'un angle de rotation β par rapport à l'autre côté frontal du même piston rotatif (2),
    - qu'aussi bien l'entrée de milieu (11) que la sortie de milieu (11') du carter (10) présentent une section transversale essentiellement rectangulaire avec à chaque fois deux bords parallèles à l'axe (11.1, 11.2, 11.1', 11.2') et à chaque fois deux bords s'étendant perpendiculairement à ceux-ci (11.3, 11.3'),
    - que la plage d'angle périphérique α et l'angle de rotation β sont à chaque fois mesurés et accordés l'un à l'autre de sorte qu'une ligne d'étanchéité imaginaire (21') s'étendant parallèlement à l'axe respectif (20) s'étend sur la longueur axiale complète de chaque piston rotatif (2) au sein de sa zone périphérique (21) qui a le contour externe avec le rayon constant R,
    - que les pistons rotatifs (2), vu en coupe transversale, présentent à chaque fois au début et à la fin de leurs deux zones périphériques (21) avec le rayon constant R vers l'autre zone périphérique (22) qui s'y raccorde respectivement une transition sous la forme d'un bord à angle obtus (26) et
    - que les bords (26) s'étendant dans un sens de rotation (29) des pistons rotatifs (2) forment à chaque fois un bord de raclage coopérant avec une section (12.1) d'un contour interne (12) du carter (10).
  2. Pompe à pistons rotatifs selon la revendication 1, caractérisée en ce qu'un premier bord parallèle à l'axe (11.1, 11.1') de l'entrée de milieu (11) et de la sortie de milieu (11') se situe à chaque fois essentiellement à hauteur d'un des axes (20) et un second bord parallèle à l'axe (11.2, 11.2') de l'entrée de milieu (11) et de la sortie de milieu (11') se situe à chaque fois essentiellement à hauteur de l'autre axe (20).
  3. Pompe à pistons rotatifs selon la revendication 1 ou 2, caractérisée en ce que vu dans la direction axiale des pistons rotatifs (2), une largeur de l'entrée de milieu (11) et de la sortie de milieu (11') s'étend à chaque fois sur 80 à 100 % de la longueur axiale de chaque piston rotatif (2).
  4. Pompe à pistons rotatifs selon l'une quelconque des revendications précédentes, caractérisée en ce que l'angle de rotation β mesure jusqu'à 60°.
  5. Pompe à pistons rotatifs selon l'une quelconque des revendications précédentes, caractérisée en ce que la zone périphérique (21) avec le rayon constant R s'étend à chaque fois sur une plage d'angle périphérique α comprise entre 10° et 60°.
  6. Pompe à pistons rotatifs selon l'une quelconque des revendications précédentes, caractérisée en ce que la plage d'angle périphérique α de la zone périphérique (21) avec le rayon constant R est au moins aussi grande que l'angle de rotation des pistons rotatifs en hélice (2).
  7. Pompe à pistons rotatifs selon l'une quelconque des revendications précédentes, caractérisée en ce que la distance A est 1,3 à 1,7 fois, de préférence 1,5 fois plus grande que le rayon R.
  8. Pompe à pistons rotatifs selon l'une quelconque des revendications précédentes, caractérisée en ce que les pistons rotatifs (2) forment, vu en coupe transversale à chaque fois dans leurs deux zones périphériques restantes (22) qui se situent entre les deux zones périphériques (21) avec le rayon constant R, une succession d'à chaque fois trois zones de contour convexes (22.1), une zone de contour concave (22.2) se situant à chaque fois entre deux zones de contour convexes (22.1).
  9. Pompe à pistons rotatifs selon l'une quelconque des revendications précédentes, caractérisée en ce que le bord à angle obtus (26) inclut un angle β compris entre 140 et 160°, de préférence d'environ 150°.
  10. Pompe à pistons rotatifs selon l'une quelconque des revendications précédentes, caractérisée en ce que les pistons rotatifs (2) sont pourvus au niveau de leurs surfaces entrant en contact avec un milieu à transporter à travers la pompe à pistons rotatifs (1) d'un revêtement ou placage (3) résistant au milieu.
  11. Pompe à pistons rotatifs selon la revendication 10, caractérisée en ce que le revêtement ou placage (3) est formé d'un gommage.
EP05783062A 2004-08-05 2005-08-02 Pompe à pistons rotatifs comportant un carter et deux pistons rotatifs à deux pales Active EP1797327B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102004037995 2004-08-05
DE102005017575A DE102005017575A1 (de) 2004-08-05 2005-04-16 Drehkolbenpumpe mit einem Pumpengehäuse und zwei zweiflügeligen Drehkolben
PCT/EP2005/008348 WO2006015766A1 (fr) 2004-08-05 2005-08-02 Pompe à pistons rotatifs comportant un carter et deux pistons rotatifs à deux pales

Publications (2)

Publication Number Publication Date
EP1797327A1 EP1797327A1 (fr) 2007-06-20
EP1797327B1 true EP1797327B1 (fr) 2008-12-31

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ID=35355649

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Application Number Title Priority Date Filing Date
EP05783062A Active EP1797327B1 (fr) 2004-08-05 2005-08-02 Pompe à pistons rotatifs comportant un carter et deux pistons rotatifs à deux pales

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US (1) US20090123319A1 (fr)
EP (1) EP1797327B1 (fr)
AT (1) ATE419464T1 (fr)
DE (2) DE102005017575A1 (fr)
WO (1) WO2006015766A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
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DE102022120550A1 (de) 2022-08-15 2024-02-15 Börger GmbH Pumpengehäuse für eine Drehkolbenpumpe

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DE102006041633A1 (de) * 2006-09-05 2008-03-13 Herold & Co. Gmbh Pumpe
FR2921444A1 (fr) * 2007-09-26 2009-03-27 Alcatel Lucent Sas Pompe a vide a deux rotors helicoidaux.
DE102008045440B4 (de) * 2008-09-02 2017-02-09 Börger GmbH Drehkolben einer Drehkolbenpumpe und Drehkolbenpumpe
DE202009012158U1 (de) 2009-09-08 2011-02-03 Hugo Vogelsang Maschinenbau Gmbh Drehkolbenpumpe
DE202010011626U1 (de) 2010-08-20 2010-10-21 Hugo Vogelsang Maschinenbau Gmbh Drehkolbenpumpe
DE202010012494U1 (de) * 2010-09-13 2011-12-15 Hugo Vogelsang Maschinenbau Gmbh Drehkolbenpumpe und Drehkolben
DE202010015439U1 (de) 2010-11-16 2012-02-17 Hugo Vogelsang Maschinenbau Gmbh Drehkolbenpumpe und Gehäuse-Halbschale für selbige
DE202011100622U1 (de) * 2011-05-12 2012-08-14 Hugo Vogelsang Maschinenbau Gmbh Vorrichtung zum Abdichten eines Pumpraums einer Drehkolbenpumpe, sowie Drehkolbenpumpe mit selbiger
WO2013019948A1 (fr) * 2011-08-03 2013-02-07 Ramos Rolando Nico M Piston à surfaces remplaçables et/ou ajustables
DE202012010401U1 (de) * 2012-10-31 2014-02-03 Hugo Vogelsang Maschinenbau Gmbh Drehkolbenpumpe mit Direktantrieb
DE102013110091B3 (de) * 2013-09-13 2015-02-12 Pfeiffer Vacuum Gmbh Wälzkolbenpumpe mit zwei Rotoren
CN108916038B (zh) * 2018-06-28 2019-10-11 兰州理工大学 一种大功率低脉动凸轮转子泵
CN109460581B (zh) * 2018-10-15 2023-01-13 扬州大学 一种球形泵排量计算方法
DE102018008264B4 (de) * 2018-10-18 2020-11-12 Doris Korthaus Drehkolbenpumpe mit Verschleißelementen zur Förderung von mit Feststoffen durchsetzten Fördermedien

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US1361423A (en) * 1916-04-19 1920-12-07 Waterous Engine Works Company Rotary pump
US3105634A (en) * 1960-12-27 1963-10-01 Polysius Gmbh Rotary piston for a roots blower
DE2108714B2 (de) * 1971-02-24 1973-05-30 Gebr Wmkelstrater GmbH, 5600 Wuppertal Barmen Parallel- und aussenachsige rotationskolbenmaschine
JP2946010B2 (ja) * 1993-03-15 1999-09-06 小倉クラッチ株式会社 エアポンプ
DE4330085A1 (de) * 1993-09-06 1995-03-09 Hugo Vogelsang Maschinenbau Gm Rotationskolben für Verdrängerpumpen nach dem Roots-Prinzip für inkompressible Medien
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DE102022120550A1 (de) 2022-08-15 2024-02-15 Börger GmbH Pumpengehäuse für eine Drehkolbenpumpe

Also Published As

Publication number Publication date
DE502005006392D1 (de) 2009-02-12
ATE419464T1 (de) 2009-01-15
WO2006015766A1 (fr) 2006-02-16
US20090123319A1 (en) 2009-05-14
EP1797327A1 (fr) 2007-06-20
DE102005017575A1 (de) 2006-03-16

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