EP2616640A2 - Pompe à pistons rotatifs et pistons rotatifs - Google Patents

Pompe à pistons rotatifs et pistons rotatifs

Info

Publication number
EP2616640A2
EP2616640A2 EP11757838.5A EP11757838A EP2616640A2 EP 2616640 A2 EP2616640 A2 EP 2616640A2 EP 11757838 A EP11757838 A EP 11757838A EP 2616640 A2 EP2616640 A2 EP 2616640A2
Authority
EP
European Patent Office
Prior art keywords
recess
rotary piston
driver
rotary
pump
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
Application number
EP11757838.5A
Other languages
German (de)
English (en)
Other versions
EP2616640B1 (fr
Inventor
Paul Krampe
Harald Vogelsang
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.)
Hugo Vogelsang Maschinenbau GmbH
Original Assignee
Hugo Vogelsang Maschinenbau GmbH
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 Hugo Vogelsang Maschinenbau GmbH filed Critical Hugo Vogelsang Maschinenbau GmbH
Publication of EP2616640A2 publication Critical patent/EP2616640A2/fr
Application granted granted Critical
Publication of EP2616640B1 publication Critical patent/EP2616640B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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
    • 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
    • F04C2/00—Rotary-piston machines or pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C19/00—Sealing arrangements in rotary-piston machines or engines
    • F01C19/005—Structure and composition of sealing elements such as sealing strips, sealing rings and the like; Coating of these elements
    • 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
    • F04C13/00—Adaptations of machines or pumps for special use, e.g. for extremely high pressures
    • F04C13/001—Pumps for particular liquids
    • 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
    • F04C13/00—Adaptations of machines or pumps for special use, e.g. for extremely high pressures
    • F04C13/005—Removing contaminants, deposits or scale from the pump; Cleaning
    • 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
    • F04C2210/00—Fluid
    • F04C2210/24—Fluid mixed, e.g. two-phase fluid
    • 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
    • F04C2240/00—Components
    • F04C2240/20—Rotors

Definitions

  • the present invention relates to a rotary piston pump for conveying fluids, in particular liquids loaded with solids, comprising a housing and at least one pair of interlocking rotary pistons arranged inside the housing, wherein a rotary piston each has at least one recess formed on its circumferential surface and / or at least one Having formed on an end surface recess.
  • the invention further relates to a rotary piston for a rotary piston pump for conveying fluids, in particular solids laden liquids.
  • Rotary lobe pumps of the abovementioned type are used for conveying any liquid, but in particular also for conveying sludge, wastewater, dirty water, process water, thick matter, bilge water, faeces, liquid manure, chemicals or animal feed.
  • the known rotary lobe pumps are self-priming and dry running insensitive.
  • the operating principle is based on the fact that the rotary piston pump operating as a positive displacement pump controls the fluid transport by means of the at least two rotary pistons on one wall of the Housing causes along the pump inlet to the pump outlet, while the at least two rotary pistons in the middle of the housing fluid-tight lie against each other and rotate in a counter-rotating manner with each other.
  • cavities are formed between two adjacent piston tips and the housing wall, in which the fluid is guided along the housing wall from the pump inlet to the pump outlet.
  • the gap between a piston tip and the housing wall is designed to be as small as possible.
  • this leads to an increased load on the surface of the piston tip or the housing wall, in particular in solids laden liquids. It occurs in the operation that solid wedged between the piston tip and the housing wall. Depending on the nature of the solid, this can cause damage to the surfaces.
  • the tightness of the pump decreases, there is more reflux and the performance of the pump decreases.
  • a maintenance of the pump possibly with replacement of the housing wall or the piston is due.
  • the present invention has the object to provide a rotary lobe pump and a rotary piston, which have an increased wear ßbe Onemaschine.
  • the invention solves the underlying task in a rotary piston pump of the type mentioned by at least one driver in the at least one Recess arranged and set up for detecting solids. It has been found that the accumulation of solids in the recesses of the rotary piston is significantly improved when a driver is inserted into the recess. Thus, although the available volume in the recess of the rotary piston decreases, the driver positively contributes to detect larger amounts of solids and to direct into the recess. In this case, the solids are at least partially pressed by nach Kohlenden solids in the recess.
  • the driver is preferably made of a wear-resistant material, so that the driver also has a certain resistance against penetrating solids, which in turn have a high strength.
  • the driver is made of hardened steel. Damage to the driver as a result of such solid body is associated with significantly less effort in maintenance as a damage to the rotary piston or the housing wall.
  • the driver according to the invention is preferably arranged interchangeable in the recess.
  • a gap is formed between a boundary of the at least one recess and the at least one driver.
  • the gap is thus defined on the one hand by the type of boundary and on the other hand by the shape of the driver. The smaller the driver compared to the size of the recess, the greater will usually be the distance between the driver and the boundary at least in a part-section of the boundary.
  • the gap is advantageously configured to receive solids captured by the driver. From the point at which the solids captured by the driver enter the gap, they are preferably pressed into the depth of the recess by subsequent solids.
  • the gap has wedge-shaped widened sections. It has been found to be particularly advantageous not to uniformly shape the gap along its entire length.
  • the wedge-shaped widened portion is arranged between the driver and the boundary of the recess, that in the direction of rotation of the rotary piston of the rotary piston pump solids first pass into a wide portion of the wedge-shaped portion to then be driven between the ever more tapered flanks of the wedge-shaped portion.
  • the at least one recess is formed as a groove and has a cross-section which is substantially rectangular and / or at least partially conically tapered towards the bottom of the recess, or at least partially conically widened towards the bottom of the recess.
  • a rectangular configuration of the cross-section of the recess can be realized time-consuming and cost-effectively for manufacturing-technical aspects.
  • a design of the side surfaces of the recess that tapers towards the bottom of the recess favors the penetration of solids into the depth of the recess, while a conically widened course of the side surfaces of the recess towards the bottom of the recess makes it more difficult for solids to escape from the recess.
  • the cleanability is hampered by an extended to the bottom of the recess towards conical shape.
  • An optimum embodiment of the recess results in the interaction of the recess with the driver inserted into the recess and may vary from case to case.
  • the at least one driver is formed according to a first preferred alternative as a flat body, wherein the height of the flat body is less than or equal to the depth of the at least one driver receiving recess.
  • the fact that the flat body has a lower height than it does the receiving recess it can be prevented that the flat body itself gets into frictional contact with the housing wall and thus damage it. At the same time, this ensures that solids also settle above the driver even in compacted form. As a result, the driver itself is protected against further wear. Achieved a rotary piston in the rotary lobe pump this condition, however, is also the disadvantage in To accept that the driver can no longer perceive his actual function, namely to increase the mass of solids in the recess, can no longer be perceived.
  • the first preferred alternative is advantageously further developed in that one or more wedge-shaped recesses are provided on at least one side surface of the at least one driver, which faces the boundary of the recess.
  • the wedge-shaped recesses at least partially define a wedge-shaped widened portion between the boundary of the recess and the driver.
  • the driver preferably has an optimized for the individual main application of the rotary piston pump distribution, arrangement and shaping of the wedge-shaped recesses.
  • the wedge-shaped recesses preferably extend both in the radial and in the tangential direction (with the driver inserted into the rotary piston). This embodiment supports the displacement of solids in the depth of the recess by nach Wegende solids.
  • the at least one driver has adjacently arranged projections, between each of which a gap is formed.
  • the preferably formed as a flat body driver with the plurality of protrusions preferably works in a similar manner as a comb.
  • the projections which may be cylindrical or polygonal, preferably extend from the bottom of the recess in the direction of the surface of the piston and define wedge-shaped widened portions, each extending between the edge of a recess and two adjacent projections.
  • the at least one driver is designed as a dowel pin, threaded pin or cap screw.
  • a plurality of drivers are adjacent and reversibly releasably secured in the at least one recess.
  • a gap is formed between adjacent carriers.
  • the drivers are designed as elements with a cylindrical, elliptical, or polygonal cross section, which can be arranged and fastened separately in the recess.
  • these elements are arranged so that solid bodies are detected and accumulated between adjacent elements.
  • the embodiment of the invention with a plurality of drivers per recess for example as a dowel pin, threaded pin or cap screw, or other elements explained above, is particularly preferred for use on the peripheral surface of obliquely extending, also referred to as helical piston rotary piston.
  • the possibility of positioning the individual carriers in the recess in a position-fitting and precise manner brings with it clear manufacturing advantages over individually manufactured flat bodies, precisely because the latter have to be formed exactly on the course of the coiled circumferential surface of the piston.
  • the one or more drivers designed as cap screws which are fastened in the one or more exceptions, have no expansion section, and / or are respectively screwed into a threaded bore, the thread of which extends in the screwed state up to a head bearing surface of the screw , in this way, the clamping length of the screw connection is minimized.
  • the applied tension is effected to the smallest possible proportion by means of the longitudinal expansion of the screw. This implies, conversely, that the screws by turning a few degrees already solvable.
  • the loosening can be effected advantageously by means of loose-fitting, if the screw heads no longer allow a key engagement, for example due to damage or contamination.
  • the at least one driver is designed as a helical spring, which is arranged at least for the most part within the recess, wherein the longitudinal axis of the helical spring is arranged parallel to the base of the recess.
  • the longitudinal axis of the helical spring is arranged parallel to the base of the recess.
  • the turns of the helical spring are aligned by the horizontal arrangement of the coil spring in the recess so that the detected solids are guided along the turns in the interior of the recess.
  • the helical spring is preferably elastically deformable in the radial direction in addition to elasticity in the longitudinal direction of the helical spring. In this way, the coil spring may partially extend outside the recess.
  • the coil spring is largely disposed within the recess and extends only with a smaller part outside the recess, the coil spring is elastically deformed upon impact of the coil spring in a tangential manner on the housing wall and displaced into the interior of the recess.
  • the rotary pistons on a wing each have a sealing line along which the rotary pistons occupy a minimum distance to an inner wall of the housing of the rotary piston pump.
  • a plurality of recesses are adjacent to the sealing surface in the peripheral surface, preferably in parallel, wherein preferably elastically deformable sealing bodies are provided as carriers, which extend partially outside the recess in the direction of the housing wall.
  • the carriers formed as elastically deformable sealing bodies also take up or contact a minimal distance from the housing inner wall. In this way, each further sealing lines are formed by means of the elastically deformable sealing body.
  • the elastically deformable sealing bodies are preferably designed to be displaced in contact with the oppositely arranged other rotary piston into the interior of the recess and to return to the original position after the displacement. Moreover, the elastically deformable sealing bodies are also preferably arranged to retreat in front of solids acting on them, so that the solids pass past the displaced sealing bodies into the depth of the recess by being pressed in by subsequent solids.
  • the embodiment with trained as elastic sealing bodies drivers also offers the advantage that in an arrangement of the sealing body receiving recesses immediately adjacent the sealing line additional sealing lines are provided, provided that the distance of the piston surface of the housing inner wall at the location of the recess with the elastic sealing bodies is not greater than the amount by which the sealing body outside ßer devis the receiving recess extending.
  • the invention solves its underlying object in a rotary piston of the type mentioned above with at least one recess formed on its peripheral surface and / or at least one recess formed on its end face by arranged at least one driver in the at least one recess and set up for detecting solids is.
  • a rotary piston of the type mentioned above with at least one recess formed on its peripheral surface and / or at least one recess formed on its end face by arranged at least one driver in the at least one recess and set up for detecting solids is.
  • the invention further relates to a method for sealing a rotary piston against an inner wall of the housing of a rotary piston pump, comprising the steps: Conveying a fluid, in particular a liquid loaded with solids by means of a rotary piston pump, and detecting solids from the delivered fluid by means of one or more drivers which are arranged in one or more recesses of the rotary piston.
  • FIG. 2 shows a cross-sectional view through a driver for the rotary piston according to the invention
  • FIG. 3a shows a perspective view of an alternative driver for the rotary piston according to the invention
  • FIG. 3b is a perspective view of another alternative driver for the rotary piston according to the invention.
  • Figure 4 is a perspective view of another alternative of a driver for the rotary piston according to the invention.
  • Fig. 5 is a sectional view of a detail of the rotary piston according to the invention in a preferred embodiment
  • Fig. 6 is a sectional view of an alternative embodiment of the rotary piston according to the invention.
  • FIG. 7 is a sectional view of a detail of a further alternative of the rotary piston according to the invention.
  • Fig. 8 is a sectional view of a detail of another alternative Austechnologyu form of the rotary piston according to the invention;
  • 9 is a perspective view of a rotary piston according to another preferred embodiment of the present invention.
  • FIG. 10 is a perspective view of a further preferred embodiment of the rotary piston according to the invention.
  • Fig. 1 still another embodiment of a rotary piston according to the invention
  • FIG. 12 is a partial view of a rotary piston pump according to the invention.
  • FIG. 13 is a sectional view through the rotary pump of FIG. 12; FIG. and
  • FIG. 14 is a detail view of the illustration of FIG. 12th
  • FIG. 1 shows a rotary piston according to the invention in accordance with a first preferred embodiment.
  • the rotary piston 1 has three inclined wings, each having a tip section 3.
  • the rotary piston 1 has a peripheral surface 5, an upper end face 7 and a lower end face 9.
  • a recess 1 1 extends from the upper end face 7 to the lower end face 9 and is adapted to receive a drive shaft.
  • recesses 13 are provided in each tip section 3 of the wing.
  • a carrier designed as a flat body 15 is arranged in the recess 13 shown on the left in FIG. 1.
  • a substantially uniformly formed gap 19 is formed between the flat body 15 and a boundary of the recess 13, a substantially uniformly formed gap 19 is formed.
  • a recess 13 is shown, in which a plurality of screws 17 designed as drivers are used.
  • the screws 17 are screwed with a minimum clamping length in each case a thread in the bottom of the recess 13. Due to the minimum clamping length, the screws 17 are still solvable even with damage and strong deformation of the key engagement.
  • a gap is formed, which, however, is not uniform.
  • the wedge-shaped widened portions 21 are adapted to hold solids, which were detected by the drivers, and to receive in the recess.
  • FIGS. 2 to 4 show various embodiments of drivers for the rotary piston 1 according to the invention.
  • Fig. 2 is a cross section of a trained as a flat body 15 driver is shown.
  • the viewing direction corresponds to an inserted driver substantially a radial direction with respect to the axis of rotation of the rotary piston.
  • the flat body 15 has a base body 23.
  • a plurality of wedge-shaped recesses 25 are introduced into the opposite side surfaces of the main body 23.
  • the wedge-shaped recesses 25 are designed to wedge solid.
  • FIG. 3 a shows a three-dimensional view of a driver designed as a flat body 15 according to an alternative embodiment.
  • the driver shown in Fig. 3a, as well as the driver shown in Figure 2 has a base body 23.
  • the main body 23 of FIG. 3a has a substantially trapezoidal cross-section.
  • Two opposite side surfaces 26 are aligned conically to each other.
  • An upper side 27, which faces the housing wall when the driver is inserted, is wider than a lower side 29 of the driver, which in the inserted state faces the base of the recess receiving it.
  • In the side surfaces of the base body 23 of the flat body 15 a plurality of wedge-shaped recesses 25 are introduced.
  • the wedge-shaped recesses are offset from each other to ensure a maximized size of the wedge-shaped recess.
  • the flat body 15 according to FIG. 3 a like the flat body according to FIG. 4, is designed to be fastened along an axis 30 by means of fastening means (not shown) in the recess
  • the driver shown in Figure 3b differs from the driver shown in Figure 3a, that the side surfaces 26 of the base body 23, in which the wedge-shaped recesses 25 are inserted offset from each other, are aligned parallel to each other, which alternatively by a rectangular cross-section or a paralle - Logrammed cross section of the body is achieved. Furthermore, two arranged on the top 27 counterbores 28 for receiving a corresponding screw head are shown in Figure 3b.
  • the piston shown in FIG. 3b is for use in the peripheral surface of a rotary piston such as, for example, according to FIG. 1 or 9 optimized. It is wound along its longitudinal direction, in order to ensure optimum adaptation to the likewise wound recess in the peripheral surface of such a rotary piston.
  • a further embodiment of a driver is shown, which is designed as a flat body 15.
  • the flat body 15 from FIG. 4 has a base body 23, from which a plurality of projections 31 extend on the upper side 27 of the base body.
  • the projections 31 are arranged substantially parallel to each other and extend in the direction of the housing wall of the rotary piston pump when the rotary piston is inserted.
  • the protrusions 31 may optionally be arranged at an angle to each other to form V-shaped or A-shaped gaps 33 between adjacent protrusions 31, which is advantageous for the detection of solids.
  • a projection 31 is advantageously formed as part of a screw, which is screwed along the axis 30 through the base body 23 into the base of the recess for the driver into it.
  • Figs. 5 to 8 show various advantageous embodiments of the driver receiving recesses.
  • a recess 13 is shown with a substantially rectangular cross-section.
  • the recess 13 is optionally provided in the circumferential surface 5, or one of the end surfaces 7, 9 and has two substantially parallel side surfaces 35.
  • the depth of the recess 13 in the rotary piston 1 is slightly larger than the height of the driver 15 or 17 to be received in the recess. If the driver 15, 17 is arranged at maximum depth in the recess 13, the driver 15, 17 preferably lies with one Bottom of the base 37 of the recess 13 at.
  • a gap 19 is shown in each case, the see between the boundary of the recess 13 and the driver 15, 17 is formed.
  • a recess 13 is shown, which does not have a completely rectangular cross-section. Instead, the cross section of the recess 13 of FIG. 6 is only partially rectangular. Starting from the surface 5, 7, 9, the cross section of the recess 13 initially tapers conically towards the base 37 of the recess and then assumes a rectangular shape.
  • the cross-section of the recess 13 shown in FIG. 7 is, viewed from the surface 5, 7, 9, initially substantially conically widened and only at the beginning conclusion formed rectangular in the direction of the base 37 of the recess.
  • the cross-section of the recess 13 in accordance with FIG. 8 is essentially completely conically widened towards the bottom of the recess 37.
  • FIG. 7 and 8 are particularly preferred for dogs with a substantially cylindrical cross-sectional profile, such as elastically deformable sealing bodies 39 or horizontally disposed coil springs 51 (see Fig. 14).
  • drivers designed as flat bodies 15 or screws 17 can also be arranged in recesses 13 according to FIG. 7 or 8 or further, correspondingly designed geometries.
  • Figs. 9 to 1 1 further preferred embodiments of the rotary piston 1 according to the invention with further preferred arrangements of the recesses shown.
  • Fig. 9 shows a three-lobed rotary piston 1 with three tip sections 3 on each wing and an otherwise comparable to FIG. 1 interpretation.
  • recesses 41 are arranged on each wing in addition to the circumferentially arranged recesses 13 with drivers 17 on the front side 7 (and optionally also on the lower front side 9) ,
  • drivers can be arranged in an analogous manner as to the recesses 13 on the peripheral surface, which are formed as a screw 17 or as a flat body 15 or as further inventive driver.
  • the recesses 41 shown in Fig. 9 are arranged substantially radially tapered on the axis of the recess 1 1.
  • the recesses 41 are preferably to be arranged outside the radial line, and / or at an angle to the radial line.
  • a two-lobed rotary piston 1 is shown, which in each case has a tip section 3 on the two wings.
  • the two-lobed rotary piston 1 according to FIG. 10 has straight running wings.
  • a recess 13 is arranged in each case in the region of the sealing line, which extends in the peripheral surface 5 from below the upper end face 7 to just above the lower end face 9.
  • recesses 41 are arranged on each wing.
  • the recesses 41 have as well as the recesses 13 on a (not shown) longitudinal axis.
  • FIG. 10 provides that the axes of the recesses 13 and 41 - considered for a respective wing - do not intersect. In this way it is possible to bring the length of the recesses 13, 41 up to the edge of the respective surface, without the recesses 13, 41 colliding with each other.
  • driver in the recesses 13, 41 reference is made to the above explained to Figs. 1 to 9.
  • FIG. 1 a further embodiment of a rotary piston 1 according to the invention is shown.
  • the rotary piston 1 according to FIG. 1 1 is also a double-winged piston with a straight piston profile.
  • the rotary piston 1 according to FIG. 11 once again has tip sections 3 on the piston wings, a peripheral surface 5, as well as an upper and a lower end face 7, 9.
  • the end face 7 on each wing of the rotary piston 1 two recesses 41 arranged in a substantially radial orientation.
  • the recesses 41 on the end face 7 are each executed in a single row, whereas on the peripheral surface 5 of the piston 1 according to FIG.
  • a multi-row recess 43 is provided.
  • the rotary piston pump 10 has a rotary piston 1 according to the invention, which is rotatably arranged within a housing.
  • the housing has a semi-cylindrical section 45. Within the section 45, an inner wall 47 is formed concentrically with the rotary piston 1.
  • Cavities are formed between the rotary piston 1 and the housing inner wall 47 during rotation of the rotary piston 1, within which fluid is transported from a pump inlet to a pump outlet.
  • a cavity is bounded in each case by the surface of the inner wall 47 on the one hand and by the peripheral surface 5 of the rotary piston 1 on the other hand.
  • the distance of the rotary piston 1 of the housing section 45 is to be kept as minimal as possible.
  • a sealing function is preferably formed in a sealing portion 49.
  • FIG. 13 is a sectional view through the piston of FIG. 12.
  • a recess 41 is provided in each case.
  • a driver is used in the lower recess 41 shown in Fig. 13.
  • the driver has a substantially cylindrical cross-section.
  • Either the driver is designed as an elastically deformable sealing body 39, or as a helical spring 51.
  • the elastically deformable sealing body 39 allows a better sealing, whereas the driver designed as a helical spring 51 has a higher capacity for detecting solids.
  • the sealing portion 49 of the rotary piston 1 has a first sealing line 53.
  • the clear width between the peripheral surface 5 of the rotary piston 1 and the inner surface 47 of the housing section 45 is minimal along the sealing line 53, ideally approximately equal to 0.
  • Right and left of the sealing line 53 are two drivers, which are arranged within a respective recess 13 , along a line 55, also communicate with the inner wall 47 of the housing section 45, or occupy a minimal distance from the inner wall 47.
  • the lines 55 are also formed as sealing lines.
  • the sealing lines are aligned substantially parallel to the first sealing line 53. The tightness and thus the efficiency of the rotary piston 1 of the rotary piston pump 10 is improved by means of the additional sealing lines 55.

Landscapes

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

Abstract

L'invention concerne une pompe à pistons rotatifs (10) destinée à refouler des fluides, en particulier des liquides chargés de corps solides, ladite pompe présentant un carter (45) et au moins une paire de pistons rotatifs (1) s'engrenant l'un dans l'autre et agencés dans le carter (45), un piston rotatif (1) comportant respectivement au moins un évidement (13, 43) réalisé sur sa surface périphérique (5) et/ou au moins un évidement (41) réalisé sur une surface frontale (7, 9). L'invention concerne en particulier une pompe à pistons rotatifs, présentant au moins un élément d'entraînement (15, 17, 39, 51) agencé dans le ou les évidements (13, 41, 43) et prévu pour détecter des corps solides. L'invention concerne également un piston rotatif pour une pompe à pistons rotatifs (10) destinée à refouler des fluides, en particulier des liquides chargés de corps solides, ledit piston rotatif comportant au moins un évidement (13, 43) réalisé sur sa surface périphérique (5) et/ou au moins un évidement (41) réalisé sur une surface frontale (7, 9).
EP11757838.5A 2010-09-13 2011-09-13 Pompe à pistons rotatifs et pistons rotatifs Active EP2616640B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE202010012494U DE202010012494U1 (de) 2010-09-13 2010-09-13 Drehkolbenpumpe und Drehkolben
PCT/EP2011/065798 WO2012034985A2 (fr) 2010-09-13 2011-09-13 Pompe à pistons rotatifs et pistons rotatifs

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EP2616640A2 true EP2616640A2 (fr) 2013-07-24
EP2616640B1 EP2616640B1 (fr) 2020-07-08

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EP11757838.5A Active EP2616640B1 (fr) 2010-09-13 2011-09-13 Pompe à pistons rotatifs et pistons rotatifs

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US (1) US20130209300A1 (fr)
EP (1) EP2616640B1 (fr)
CN (1) CN103221638A (fr)
DE (1) DE202010012494U1 (fr)
ES (1) ES2812504T3 (fr)
WO (1) WO2012034985A2 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2971776A2 (fr) * 2013-03-15 2016-01-20 Eaton Corporation Rotor feuilleté à faible inertie
DE102014117166B4 (de) * 2014-11-24 2016-07-07 Netzsch Pumpen & Systeme Gmbh Drehkolbenpumpe, verfahren zur fixierung von drehkolben einer drehkolbenpumpe und verfahren zur demontage von drehkolben einer drehkolbenpumpe
WO2016116251A1 (fr) * 2015-01-23 2016-07-28 Robert Bosch Gmbh Compresseur de suralimentation pour un moteur

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DE3707722A1 (de) * 1987-03-11 1988-09-29 Alois Boerger Rotorpumpe, insbesondere fuer die foerderung von feststoffe enthaltenden fluessigkeiten
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DE102005017575A1 (de) * 2004-08-05 2006-03-16 Börger GmbH Drehkolbenpumpe mit einem Pumpengehäuse und zwei zweiflügeligen Drehkolben
GB2429751A (en) 2005-08-31 2007-03-07 Alfa Laval Corp Ab Axially removable flanged wearplate for lobe pump
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DE102008045440B4 (de) * 2008-09-02 2017-02-09 Börger GmbH Drehkolben einer Drehkolbenpumpe und Drehkolbenpumpe

Also Published As

Publication number Publication date
DE202010012494U1 (de) 2011-12-15
ES2812504T3 (es) 2021-03-17
WO2012034985A3 (fr) 2013-04-25
EP2616640B1 (fr) 2020-07-08
WO2012034985A2 (fr) 2012-03-22
CN103221638A (zh) 2013-07-24
US20130209300A1 (en) 2013-08-15

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