EP1797327A1 - Drehkolbenpumpe mit einem pumpengehäuse und zwei zweiflügeligen drehkolben - Google Patents
Drehkolbenpumpe mit einem pumpengehäuse und zwei zweiflügeligen drehkolbenInfo
- Publication number
- EP1797327A1 EP1797327A1 EP05783062A EP05783062A EP1797327A1 EP 1797327 A1 EP1797327 A1 EP 1797327A1 EP 05783062 A EP05783062 A EP 05783062A EP 05783062 A EP05783062 A EP 05783062A EP 1797327 A1 EP1797327 A1 EP 1797327A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- rotary
- rotary piston
- piston
- pump
- pistons
- 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.)
- Granted
Links
- 230000002093 peripheral effect Effects 0.000 claims abstract description 48
- 238000007789 sealing Methods 0.000 claims abstract description 27
- 230000004323 axial length Effects 0.000 claims abstract description 11
- 239000011248 coating agent Substances 0.000 claims description 13
- 238000000576 coating method Methods 0.000 claims description 13
- 238000010073 coating (rubber) Methods 0.000 claims description 6
- 230000007704 transition Effects 0.000 claims description 6
- 239000007787 solid Substances 0.000 description 8
- 239000007788 liquid Substances 0.000 description 7
- 239000002245 particle Substances 0.000 description 7
- 238000007790 scraping Methods 0.000 description 5
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 5
- 230000010349 pulsation Effects 0.000 description 4
- 238000005086 pumping Methods 0.000 description 4
- 230000018109 developmental process Effects 0.000 description 3
- 239000000463 material Substances 0.000 description 3
- 238000004891 communication Methods 0.000 description 2
- 238000006073 displacement reaction Methods 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 101100289200 Caenorhabditis elegans lite-1 gene Proteins 0.000 description 1
- 229910001208 Crucible steel Inorganic materials 0.000 description 1
- 229910001315 Tool steel Inorganic materials 0.000 description 1
- 230000001154 acute effect Effects 0.000 description 1
- 238000000354 decomposition reaction Methods 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000002349 favourable effect Effects 0.000 description 1
- 210000003608 fece Anatomy 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 230000012447 hatching Effects 0.000 description 1
- 230000003993 interaction Effects 0.000 description 1
- 230000009191 jumping Effects 0.000 description 1
- 239000010871 livestock manure Substances 0.000 description 1
- 229920000136 polysorbate Polymers 0.000 description 1
- 229910001220 stainless steel Inorganic materials 0.000 description 1
- 239000010935 stainless steel Substances 0.000 description 1
- 230000001550 time effect Effects 0.000 description 1
- 238000004804 winding Methods 0.000 description 1
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
- 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
- Rotary piston pump with a pump housing and two double-lobed rotary pistons
- the present invention relates to a rotary piston pump with a pump housing and with two double-leaf rotary pistons, wherein the pump housing on the one hand a Medium ⁇ inlet and opposite a medium outlet and ei ⁇ NEN interior has, in cross section in wesentli chen the contour of an oval with two each other suddenly ⁇ lying semicircles having the radius R whose centers have the distance A, wherein the rotary pistons are rotatably supported in opposite directions on two parallel axes, wherein the one axis through the one Halb Vietnamesemit ⁇ teltician and the other axis through the other Haib circle center , Wherein each rotary piston in its rotation on the one hand in the field of semicircles dich ⁇ tend along the housing along and sealingly abuts against the other piston, each rotary piston in two diametrically opposite circumferential regions each over a circumferential angular range ⁇ an outer contour with the constant radius R has about its axis, each rotary piston in its other peripheral areas each have a steady, einriffswinkel
- a rotary lobe pump of the type mentioned is known from US 1 361 423 A.
- This rotary lobe pump which is intended as a fire-extinguishing pump in the first place, 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 pistons, with curves and transition slopes, in order to ensure that a volume of water within the inner space does not abruptly upon rotation of the pistons, but rather steadily and with a certain transitional phase is separated from the volume of water in the reservoir. This is intended to reduce vibrations during operation of the rotary piston pump.
- the outlet Since the inlet is moderately large, the outlet must be correspondingly narrower aus ⁇ out to ensure in each position of the rotary piston still a seal between the inlet side and outlet side.
- the disadvantage here is due to the relatively narrow outlet here to a high flow resistance for the pumped by the pump water, which reduces the pumping efficiency.
- the rotary pistons used in this rotary piston pump are designed to be straight in their axial direction.
- EP 0 283 755 A1 discloses an apparatus for distributing inhomogeneous liquids, in particular manure.
- 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 half ter a partitioned by intermediate walls in a plurality of ge, each containing a rotary piston pair on the type of Roots rotors containing delivery chambers housing. All pumping rooms are in open communication with each other on their liquid feed side and are each provided with a separate outlet on their liquid outlet side. It is essential in this Vor ⁇ direction that 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 Dreh ⁇ piston pair of the associated pumping chamber.
- the two outlet channels are alternately separated and connectable to the delivery chamber by their respective rotating rotary pistons.
- Vorrich ⁇ device is achieved that particularly strong pulsations arise during the rotation of the rotary piston, which are here ge ⁇ desired to promote the inhomogeneous liquids through the plurality of outlet openings and the anschaul ⁇ ble discharge lines, without causing Blockages occur due to solids entrained in the liquids or foreign bodies.
- the Dreh ⁇ pistons seen in their axial direction are formed geradlinig duri ⁇ fend.
- Another rotary lobe pump is known from EP 0 599 333 A1.
- the rotary pistons each have a radius at their radially outer ends which is smaller than the radius of the semicircles forming the housing contour.
- the center point of the radius of the outer ends of the rotary pistons is offset outwards at a radial distance from the axis about which the relevant rotary piston is rotatable. From this it follows that each radially outer end of the rotary pistons only along a line-shaped sealing contour on the housing long strokes when the rotary pistons are rotated.
- circular piston pumps are known in the prior art, for example from DE 100 22 097 C1.
- Characteristic of rotary piston pumps are rotary pistons which have an outer contour over a relatively large peripheral area 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 circular piston of a rotary piston pump that the radially outer end region of each rotary piston merges at its leading and trailing ends in each case via an acute-angled edge into a concave contour region running in the direction of the associated axis of rotation.
- the acute-angled edges are subject to particularly high levels of wear during the operation of a centrifugal piston pump.
- a sufficiently large gap space between the two rotary pistons must be kept free in order to allow the medium to drain off and to flow in the area of the cavitation, in particular if the medium is a non-compressible medium, such as a liquid.
- the acute-angled edges of the rotary piston are chamfered, so that the piston wing circumference is reduced and a flow of the medium from the cavitation or an inflow of the medium into the cavitation is more easily possible. In this case, however, a reduction in the delivery rate of the pump must be accepted.
- DE 198 02 264 C1 shows a rotor pump with a pump housing, with a pair of rotors which can be rotatably driven in opposite directions, which each have a helix extending obliquely to the associated shaft, which seals the rotors during the rotation of the rotors circulate adjacent to the inside of the wall of the pump housing and on the other rotor.
- the oblique displacement vanes reduce the pulsations in the pumped medium, but are only applied to the pump housing along a dense line.
- 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 Pumpenge ⁇ housing and a low-pulsation promotion be achieved and cavitation and associated gap currents avoided ⁇ become the.
- the rotary lobe pump is a good Have efficiency and low wear and be inexpensive to manufacture and in operation.
- both the medium inlet and the medium outlet of the pump housing has a substantially rectangular cross section, each having two paraxial and two mutually perpendicular thereto edges, and
- the new Drehkol ⁇ benpumpe invention combines several advantages in itself. Due to the circumferential area with the constant radius R, a planar seal is achieved between the rotary pistons and the pump housing, which is wear-sensitive to a much lesser extent than a line-shaped 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 pumps according to the invention. At the same time, no cavitations occur in the rotary piston pump according to the invention, because due to the absence of acute-angled edges no Ein ⁇ grip angle 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] 3 ensures a steady seal between the suction side and pressure side of the pump in each position of the rotary piston ge by their surface sealing contact with the pump housing and unwanted medium back flows zwi ⁇ rule rotary piston and housing through despite the large Inlet and outlet sections and avoided despite the turning of the rotary piston.
- 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 Kreiskolben ⁇ pumps.
- a first axis-parallel edge of the medium inlet sses and of the medium outlet in each case essentially at the level of one axis and a second axis-parallel edge of the medium inlet. lasses and the medium outlet in each case substantially in
- a further measure for achieving the largest possible inlet and outlet cross-section is that, viewed in the axial direction of the rotary piston, a width of the medium inlet and the medium outlet respectively 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, depending on the particular requirements of the application.
- the angle of rotation ⁇ is up to 60 °.
- the largest possible circumferential area with the constant radius R is desirable.
- the circumferential area 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.
- the circumferential angular range ⁇ of the circumferential region with the constant radius R is at least as great as the angle of rotation of the turned 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 runs over its entire length in the peripheral region with the constant radius R.
- the inlet and outlet can advantageously have a width which corresponds to the full axial length of the rotary piston, without the desired continuous sealing between the inlet side and the outlet side of the pump being lost.
- the distance A be 1.3 to 1.7 times, preferably 1 , 5 times, is as large as the radius R.
- a further development of the rotary piston pump according to the invention provides that the rotary pistons, viewed in cross-section, each form a sequence of three convex contour regions in each of its two remaining peripheral regions, which are between the two peripheral regions with the constant radius R, with two each convex contour areas depending on a concave contour area.
- This contouring provides a geometrically favorable opportunity for educa- Development of 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 a cavitation.
- the invention proposes that the rotary pistons have a transition in the form of an obtuse-angled edge, as viewed in cross-section, at the beginning and at the end of their two circumferential regions with the constant radius to the respective subsequent peripheral region.
- the obtuse-angled edge forms a scraping edge, with the forward side of the rotary piston, with its surface region directly adjoining the scraping edge, enclosing the inner circumference of the housing at a significantly less acute angle.
- the scraping edges in their interaction with the inner circumferential surface of the housing ensure that solid particles in the medium to be conveyed in the direction of piston rotation largely remain in front of the rotary pistons and are transported further by them, without becoming trapped between the housing inner circumference 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.
- the invention proposes that the rotary pistons are provided with a coating or support which is resistant to the medium at 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 they do not have any acute-angled edges which hinder a coating or support.
- a material can be used per se for the rotary pistons which is not resistant to the medium to be conveyed, because it is protected by the coating or support against attack by the medium. This is the use of schengünsti ⁇ gerem material, eg. As of cast steel or tool steel an ⁇ point of stainless steel, possible.
- the coating or overlay is preferably formed by a rubber coating.
- a rubber coating offers - in terms of protecting the turntable against attacks, the medium to be för ⁇ medium 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 unwanted backflow against the desired conveying direction of the rotary piston pump are further reduced, which improves the efficiency of the pump.
- FIG. 1 shows a rotary piston pump in cross-section, partly in front view, with two rotatably extending in its axial direction rotary pistons
- Figure 4 left a conventional rotary piston pump and right a rotary piston pump according to the invention in comparison, each in a partial cross-section, and
- FIG. 1 shows a rotary-piston pump 1 which has a housing 10 and two double-lobed rotary pistons 2 arranged therein.
- the pump housing 10 delimits an inner space 10 'which, in the example shown in FIG. 1, has an oval-shaped inner contour 12 in cross section.
- the inner contour 12. Is formed by a respective semicircular contour section 12 mutually facing ends by two straight Kon ⁇ turabête 12.2 are interconnected.
- an inlet 11 through which a medium to be conveyed in the flow direction 28 enters the housing 10 of the rotary piston 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 delimited by a respective upper edge 11.1 and lower edge 11.2 running perpendicular to the plane of the drawing and by two side edges 11.3 extending at right angles thereto and parallel to the plane of the drawing.
- the outlet 11 ' is correspondingly delimited by a respective upper edge 11.1' and lower edge 11.2 'extending perpendicularly to the plane of the drawing, and by two side edges 11.3' extending at right angles thereto and parallel to the plane of the drawing.
- Seen in the direction of flow 28 of the medium 'in front of and behind the rotary lobe pump 1 usually lines for the guidance of the medium are arranged, which are not darge here are.
- the two rotary pistons 2 in the interior 10 'of the housing 10 are rotatably supported around two axes 20 parallel to one another and perpendicular to the plane of drawing of FIG.
- 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 Konturab ⁇ sections 12.1 of the inner contour 12 together.
- each rotary piston 2 has two diametrically opposite circumferential regions 21 whose radius R measured from the axis 20 coincides with the radius R of the semicircular sections 12. 1 of the inner contour 12.
- these peripheral regions 21 with the constant radius R extend over a respective peripheral angle range ⁇ of the associated rotary piston 2, the circumferential angle range ⁇ in each case being approximately 40 °.
- each rotary piston 2 rests against the semi-circular section 12.1 of the inner contour 12 of the housing 10, forming a planar seal, when the rotary piston 2 moves along the section 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 an only line-shaped sealing.
- the contour of the rotary pistons 2 is continuous both in the peripheral regions 21 with the constant radius R and in the two other peripheral regions 22 lying between them, and in particular without acute-angled edges, whereby volume inclusions or cavitations between the two rotary pistons 2 in each Verwindungs ⁇ position are avoided relative to each other.
- 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.
- the two rotary pistons 2 are designed as coiled pistons. This means that the two rotary pistons 2 seen in their Axialrich ⁇ direction, that are perpendicular to the plane of the Fi ⁇ gur 2, opposite to each other in rotation.
- Figure 1 is the
- FIG. 2 shows an enlarged view of only the front side of a single coiled rotary piston 2 for a rotary piston pump according to FIG. 1.
- the rotary piston 2 shown in FIG. 2 it has a peripheral region 21 with a constant radius at the very top and at the very bottom R, measured from the axis 20 about which the rotary piston 2 is rotatable.
- each circumferential region 21 extends with the constant radius R over a circumferential angular range ⁇ of approximately 24 °.
- the transition from a peripheral region 21 to an adjacent circumferential 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 J3 on. In the example shown in FIG. 2, the angle J3 is about 150 °.
- the obtuse-angled edges 26, which form the leading edges during operation, ie during rotation of the rotary piston 2, have a function as scraper edges in cooperation with the pump housing (not shown in FIG. 2). In this way, trapping of solid particles which are contained in the medium to be conveyed is largely avoided between the outer circumference of the rotary pistons 2 and the inner periphery of the pump housing which is not shown in FIG.
- 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 as viewed from the circumferential region 21.
- FIG. 2 also shows a technical possibility of mounting the rotary piston 2 on a shaft 23, which is rotatable about the axis 20.
- a piston carrier body 24 with a cylindri ⁇ basic shape is mounted rotationally fixed on the shaft 23.
- At its outer circumference carries the piston support body 24 an outwardly vor ⁇ spring jumping spring 24 '.
- a piston core 25 is arranged rotationally fixed, which has a bore whose inner diameter with a clearance fit corresponds to the outer diameter of the piston carrier body 24.
- the piston core 25 has, on its inner circumference, a groove 25 ', which extends radially outwards and runs in the axial direction, which, in the assembled state, as represented by FIG. 2, receives the spring 24'.
- FIG. 3 shows the rotary-piston pump 1 from FIG. 1 in a perspective view, wherein a housing cover is omitted and the viewer's right half of the housing 10 of the rotary-piston pump 1 is only indicated in dashed lines in order to separate the two in the FIG housing 10 arranged rotary piston 2 to make completely visible.
- the coiled design of the rotary piston 2 is particularly clear.
- the circumferential 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 highlighted in FIG. 3 by a hatching. Between the peripheral regions 21 are the remaining peripheral regions 22, the contour of which has already been explained with reference to FIG.
- Each transition from one circumferential region 21 to an adjacent peripheral region 22 is formed by an obtuse-angled edge 26 in each case.
- the two rotary pistons 2 are mutually rotatable about their mutually parallel axes 20 in the sense of the rotary arrows 29, for which purpose a drive, which is not shown here, 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 at the level 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 side, here facing away from the observer, the pump housing 10 has its outlet 11 ', which likewise has a rectangular outline.
- An upper edge delimiting the outlet 11 ' is concealed here by the upper rotary piston 2; down the outlet 11 'is limited by a lower edge 11.2'.
- the rotary pistons 2 can, as shown in FIG. 3, be provided with a coating or support 3, in particular a rubber coating, on their outer surfaces which come into contact with the medium to be conveyed by the rotary piston pump 1, in order to directly attack the conveyed medium To prevent 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 the event of wear or damage, the coating or support 3 can be renewed, wherein the remaining rotary piston 2 can continue to be used.
- FIG. 3 In the event of wear or damage, the coating or support 3 can be renewed, wherein the remaining rotary piston 2 can continue to be used.
- FIG. 4 shows, for the purpose of a direct comparison with each other on the left, a conventional rotary lobe pump and, on the right, a rotary lobe 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 Dreh ⁇ piston 2 may also be two or four wings. As the left part of Figure 4 illustrates, this rotary piston 2, regardless of the number of its wings, only with a circumferentially very narrow, practically only line-shaped region 21 in sealing contact Ab ⁇ section 12.1 of the inner contour 12 of the housing 10 at , in the example shown here over a circumferential angle ⁇ of only about 3 °. This results in a very acute-angled, wedge-shaped gap between the peripheral region 22 of the rotary piston 2 and the section 12.1 of the inner contour 12 of the housing 10, seen here in direction of rotation 29 of the rotary piston 2 side of the rotary piston 2, here with a gap angle of only about 5 °.
- the rotary-piston pump is equipped with a rotary piston 2 of the type already described above with reference to FIGS. 1 to 3.
- This rotary piston 2 projects beyond a circumferentially relatively large angular range ⁇ of approximately 50.degree.
- This region 21 extends in the circumferential direction to both sides each bounded by an obtuse edge 26; This is followed, viewed in the circumferential direction, on both sides by the further peripheral region 22.
- FIG. 5 shows a single rotary piston 2 from the rotary piston pump shown in FIG. 3 in a perspective view.
- the rotary piston 2 according to FIG. 5 is rotatable about its axis of rotation 20.
- the peripheral regions 21 pointing upwards and downwards in FIG. 5 have a constant radius R (see FIG. 2) and, during operation of the rotary piston pump, make surface-sealing contact with the semicircular sections 12.1 of the inner contour 12 of the housing 10 um.
- 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.
- the remaining peripheral regions 22 also consist of three convex regions 22.1 and two each. because intervening concave areas 22. 2 together.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Details And Applications Of Rotary Liquid Pumps (AREA)
- Details Of Reciprocating Pumps (AREA)
- Reciprocating Pumps (AREA)
Description
Claims
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 (de) | 2004-08-05 | 2005-08-02 | Drehkolbenpumpe mit einem pumpengehäuse und zwei zweiflügeligen drehkolben |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1797327A1 true EP1797327A1 (de) | 2007-06-20 |
EP1797327B1 EP1797327B1 (de) | 2008-12-31 |
Family
ID=35355649
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP05783062A Active EP1797327B1 (de) | 2004-08-05 | 2005-08-02 | Drehkolbenpumpe mit einem pumpengehäuse und zwei zweiflügeligen drehkolben |
Country Status (5)
Country | Link |
---|---|
US (1) | US20090123319A1 (de) |
EP (1) | EP1797327B1 (de) |
AT (1) | ATE419464T1 (de) |
DE (2) | DE102005017575A1 (de) |
WO (1) | WO2006015766A1 (de) |
Families Citing this family (15)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
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 (en) * | 2011-08-03 | 2013-02-07 | Ramos Rolando Nico M | Piston with replaceable and/or adjustable surfaces |
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 |
DE102022120550A1 (de) | 2022-08-15 | 2024-02-15 | Börger GmbH | Pumpengehäuse für eine Drehkolbenpumpe |
Family Cites Families (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US704224A (en) * | 1902-01-11 | 1902-07-08 | P H & F M Roots Company | Rotary pump. |
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 |
DE19802264C1 (de) * | 1998-01-22 | 1998-11-26 | Boerger Gmbh | Rotorpumpe |
-
2005
- 2005-04-16 DE DE102005017575A patent/DE102005017575A1/de not_active Withdrawn
- 2005-08-02 EP EP05783062A patent/EP1797327B1/de active Active
- 2005-08-02 AT AT05783062T patent/ATE419464T1/de not_active IP Right Cessation
- 2005-08-02 DE DE502005006392T patent/DE502005006392D1/de active Active
- 2005-08-02 WO PCT/EP2005/008348 patent/WO2006015766A1/de active Application Filing
- 2005-08-02 US US11/659,128 patent/US20090123319A1/en not_active Abandoned
Non-Patent Citations (1)
Title |
---|
See references of WO2006015766A1 * |
Also Published As
Publication number | Publication date |
---|---|
DE502005006392D1 (de) | 2009-02-12 |
US20090123319A1 (en) | 2009-05-14 |
WO2006015766A1 (de) | 2006-02-16 |
DE102005017575A1 (de) | 2006-03-16 |
EP1797327B1 (de) | 2008-12-31 |
ATE419464T1 (de) | 2009-01-15 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
EP1797327A1 (de) | Drehkolbenpumpe mit einem pumpengehäuse und zwei zweiflügeligen drehkolben | |
DE10327574B4 (de) | Laufrad für eine Kraftstoffpumpe | |
DE3212363A1 (de) | Selbstanlaufende fluegelkolbenpumpe | |
DE19539162C2 (de) | Radialrad für eine geschlossene Kreiselpumpe | |
DE1553031A1 (de) | Drehkolbenpumpe fuer zaehfluessige Medien | |
DE102014212920A1 (de) | Schaufelpumpe | |
DE3313612A1 (de) | Rotationspumpe | |
DE1653921C3 (de) | Rotationskolbenpumpe | |
DE69723488T2 (de) | Seitenkanalpumpe | |
DE102008045440B4 (de) | Drehkolben einer Drehkolbenpumpe und Drehkolbenpumpe | |
DE2523298A1 (de) | Rotationsverdraengerpumpe bzw. -motor | |
EP2766608A1 (de) | Kreiselpumpe für feststoffe enthaltende flüssigkeiten und spaltabdichtung | |
DE19626211C2 (de) | Flügelzellenpumpe | |
DE10040711C2 (de) | Flügelzellenpumpe | |
DE102006003272B4 (de) | Kraftstoffpumpe mit einem dualen Fließkanal | |
DE10200579B4 (de) | Selbstansaugende Kreiselpumpe | |
EP1448895A1 (de) | Drehkolbenpumpe | |
DE3108507C2 (de) | ||
DE2857227C2 (de) | Mehrflutige Flüssigkeitsringgaspumpe | |
WO2009019101A1 (de) | Verdrängerpumpe | |
DE102006036439A1 (de) | Förderaggregat | |
EP0363420B1 (de) | Pumpe | |
EP0995906A1 (de) | Motorgetriebene Doppelpumpe der Kreiselpumpenbauart | |
DE102007037666A1 (de) | Flügelzellenpumpe mit verringerter Flächenpressung der Flügel | |
DE3243067A1 (de) | Innenlaeuferzahnradoelpumpe fuer kraftfahrzeugverbrennungsmotoren |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
PUAI | Public reference made under article 153(3) epc to a published international application that has entered the european phase |
Free format text: ORIGINAL CODE: 0009012 |
|
17P | Request for examination filed |
Effective date: 20070117 |
|
AK | Designated contracting states |
Kind code of ref document: A1 Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC NL PL PT RO SE SI SK TR |
|
17Q | First examination report despatched |
Effective date: 20070925 |
|
DAX | Request for extension of the european patent (deleted) | ||
GRAP | Despatch of communication of intention to grant a patent |
Free format text: ORIGINAL CODE: EPIDOSNIGR1 |
|
GRAS | Grant fee paid |
Free format text: ORIGINAL CODE: EPIDOSNIGR3 |
|
GRAA | (expected) grant |
Free format text: ORIGINAL CODE: 0009210 |
|
AK | Designated contracting states |
Kind code of ref document: B1 Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC NL PL PT RO SE SI SK TR |
|
REG | Reference to a national code |
Ref country code: GB Ref legal event code: FG4D Free format text: NOT ENGLISH Ref country code: CH Ref legal event code: EP |
|
REF | Corresponds to: |
Ref document number: 502005006392 Country of ref document: DE Date of ref document: 20090212 Kind code of ref document: P |
|
REG | Reference to a national code |
Ref country code: IE Ref legal event code: FG4D Free format text: LANGUAGE OF EP DOCUMENT: GERMAN |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: FI Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20081231 Ref country code: PL Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20081231 Ref country code: SI Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20081231 Ref country code: LV Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20081231 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: LT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20081231 Ref country code: RO Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20081231 Ref country code: EE Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20081231 Ref country code: ES Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20090411 |
|
REG | Reference to a national code |
Ref country code: IE Ref legal event code: FD4D |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: PT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20090601 Ref country code: IS Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20090430 Ref country code: CZ Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20081231 Ref country code: SE Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20090331 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: SK Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20081231 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: DK Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20081231 Ref country code: IE Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20081231 |
|
PLBE | No opposition filed within time limit |
Free format text: ORIGINAL CODE: 0009261 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT |
|
26N | No opposition filed |
Effective date: 20091001 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: BG Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20090331 |
|
BERE | Be: lapsed |
Owner name: BORGER G.M.B.H. Effective date: 20090831 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: MC Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20090831 |
|
REG | Reference to a national code |
Ref country code: CH Ref legal event code: PL |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: LI Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20090831 Ref country code: CH Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20090831 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: BE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20090831 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: GR Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20090401 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: AT Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20090802 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: LU Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20090802 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: HU Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20090701 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: TR Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20081231 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: CY Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20081231 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: FR Payment date: 20110818 Year of fee payment: 7 Ref country code: GB Payment date: 20110727 Year of fee payment: 7 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: IT Payment date: 20110812 Year of fee payment: 7 Ref country code: NL Payment date: 20110818 Year of fee payment: 7 |
|
REG | Reference to a national code |
Ref country code: NL Ref legal event code: V1 Effective date: 20130301 |
|
GBPC | Gb: european patent ceased through non-payment of renewal fee |
Effective date: 20120802 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: NL Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20130301 |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: ST Effective date: 20130430 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: IT Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20120802 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: GB Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20120802 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: FR Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20120831 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: DE Payment date: 20230929 Year of fee payment: 19 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R082 Ref document number: 502005006392 Country of ref document: DE Representative=s name: SCHULZE HORN, KATHRIN, DE |