EP1624189B1 - Pompe à pistons rotatifs - Google Patents

Pompe à pistons rotatifs Download PDF

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Publication number
EP1624189B1
EP1624189B1 EP05015840A EP05015840A EP1624189B1 EP 1624189 B1 EP1624189 B1 EP 1624189B1 EP 05015840 A EP05015840 A EP 05015840A EP 05015840 A EP05015840 A EP 05015840A EP 1624189 B1 EP1624189 B1 EP 1624189B1
Authority
EP
European Patent Office
Prior art keywords
housing
pistons
rotary
piston
rotary 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.)
Not-in-force
Application number
EP05015840A
Other languages
German (de)
English (en)
Other versions
EP1624189A1 (fr
Inventor
Heinz Deyen
Hugo 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 EP1624189A1 publication Critical patent/EP1624189A1/fr
Application granted granted Critical
Publication of EP1624189B1 publication Critical patent/EP1624189B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0042—Systems for the equilibration of forces acting on the machines or pump
    • F04C15/0049—Equalization of pressure pulses
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C11/00—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations
    • F04C11/001—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations of similar working principle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • 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

Definitions

  • the invention relates to a rotary lobe pump for inhomogeneous liquids, in particular manure, comprising a housing with an inlet opening and an outlet opening, in the interior of which four cooperating rotary pistons for an opposite circulation for conveying the liquid from the housing inlet to the housing outlet opening are accommodated on two shafts, wherein the interior of the pump housing is divided into two separate, each containing a pair of cooperating rotary piston, the same delivery chambers, which are connected to each other at the inlet opening and the outlet opening of the housing, wherein the two rotary pistons of a delivery chamber in their angular position relative to the other Conveying space are offset, wherein between the rotary piston of a shaft co-rotating plates or discs are arranged.
  • Such a rotary pump is known as a high-pressure blower (US 693 609), wherein the discs or rings are formed as seals and have the same diameter.
  • a further known rotary lobe pump of this type (US Pat. No. 4,907,954) is used in a compressor of gases for damping noises and vibrations.
  • throttle disks should produce a pressure equalization between the combs and thus have a damping effect on compressible fluids (gases) during the compression by return flow from the pressure line.
  • compressible fluids gases
  • overflowing from one chamber to another is detrimental.
  • the throttle disks are each part of both piston segments, d. H. physically there are no discs.
  • Two-shaft rotary lobe pumps with non-twisted piston profile along the axis of rotation have a more or less pulsating conveying mode, irrespective of piston geometry and number of teeth.
  • the displacement per unit time is not constant, but it is depending on the engagement position of the two pistons per angular degree more or less promoted.
  • the frequency of the pulsation is four times the speed.
  • the accelerations of the liquid column cause pressure fluctuations, which affect vibrations in the pump and the pipeline.
  • Rotary lobe pumps are used in many cases under abrasive operating conditions and are therefore subject to increased wear.
  • the wing outer contour is exposed to increased wear.
  • multi-bladed rotary pistons in which the piston vanes have small radii of curvature therefore have a higher leakage rate when worn than double-leaf rotary pistons, so that double-wing rotary pistons have a longer service life.
  • CMOS 84 32 974 Known in DGM 84 32 974 is a way to Pulsationsminderung rotary lobe pumps.
  • the pump is divided into two pumps with the same delivery volume, the suction and pressure sides are connected.
  • the Pulsationsminderung is achieved by the phase position of the second pump is offset such that the minimum and maximum of the flow rate compensate each.
  • the succeeds by angularly mounted mounting of the rotary piston of the second pump chamber. For a 2-bladed rotary piston, the angular offset is 45 °.
  • this embodiment requires that the required for the separation of the two pump chambers center plate must be attached to the housing parts of the two pump chambers, so that the replacement of pistons without simultaneous disassembly of the center plate is not possible.
  • the center plate is replaced by two co-rotating center plate elements connected to the pistons. Two different versions can be realized.
  • the rotating center plates consist of circular discs. Both disks are each clamped between the end faces of adjacent rotary pistons.
  • the large disc has the same outer diameter as the pistons.
  • the small disc has an outer diameter like the root circle of the pistons. Both discs run with a small gap both to the housing and against each other.
  • the so-called blow hole - the space between the outer diameter of the small disc - and the housing inner diameter is closed by a fixed web, which has approximately the contour of a rotary piston towards the pump room, but in its dimensions is designed so that at a suitable position the rotary piston can be removed from the shaft without hindrance.
  • the rotating center plates are provided with an outer contour which coincides with the piston contour.
  • the rotating center plates are positioned with respect to their angular position in the middle between the angular positions of two adjacent pistons and thus largely cover the blow hole between the two pump chambers, which - in the absence of center plate - the pressure side would connect directly to the suction side.
  • the housing loop of 180 ° on the suction and pressure side has been increased by 22.5 ° in order to achieve a complete closure of the blow hole in all angular positions.
  • FIG. 1 shows a plan view of a housing 12 of a piston pump according to the invention. It can be seen passing through the housing 12 waves 13 and 14. On the shaft 13 sit the piston 15 and 17 and the middle plate 19th
  • Figure 3 shows in the cross-sectional view of the position of the two pistons 15 and 16 to each other.
  • Figure 4 shows the two middle plate elements, once in plan view and left thereof in side view.
  • the fixed part 30 of the middle elements can be seen in a side view both in plan view and on the left side thereof.
  • Such an element 30 is located only in the lower region, which can be seen from FIG. 5b.
  • Figure 6 shows again essential parts of an embodiment according to the invention with disk-shaped center plates 19 and 20, in a perspective view.
  • Figure 8 shows only the pistons and the piston-shaped center plates in a diagrammatic arrangement to illustrate the spatial position of this part to each other.
  • FIG. 9 shows, on an enlarged scale, the range indicated in FIG. 7, in order to make the conditions prevailing there better understandable.
  • There are the gore-shaped ones To recognize blow holes, resulting between the piston 18 and the plate 20, and between the plate 20 and the piston 16 arise.
  • the corresponding gore-shaped areas are indicated at 40 and 41. In the contours of the middle plates selected according to FIGS. 7 and 8, these residual blow holes can not be completely avoided.
  • FIG. 10 shows an embodiment in which the center plates 19 and 20 are designed such that even these remaining blow holes 40 and 41 can be avoided.
  • the outer contour of the middle plates 19 and 20 in the head area is expanded in a circular arc and in the areas which are closer to the through hole of the middle plates 19 and 20, designed accordingly.
  • 400 denotes the corresponding head region of the plates 19 and 20.
  • the radially smallest extent has the disc 19 at its periphery in the area 194 and on both sides of this area are convex portions 195 and 196 with the corresponding radii.
  • the region 192 of the maximum extent of the disc 19 over a certain Angle range (would be optimal for a two-bladed piston 45 °) has been increased.
  • the envelope of the piston outer contour is equal to the diameter of the housing half shell.
  • the convex portions 195 and 196 are the effects of this measure when rolling the pistons on the pitch circle (corresponds to the center distance).
  • the concave portions 191 and 193 have negative effects for rotary pistons since they generate pulsations and increase the risk of cavitation if they are made too large. In the case of the narrow slices 19 and 20 compared to the pistons, however, this can be accepted.
  • the disk 19 shown there begins with the peripheral region 192, then it can be stated that over a angular range 400 of approximately 45 ° there is a positive curvature of the outer contour.
  • This region 192 is followed by another region 191 of positive curvature, and as it proceeds further counterclockwise, it leads to a region of negative curvature.
  • This in turn is followed by the region 194, which corresponds to the region of the disc with the lowest radial extent.
  • the circumferentially further configurations of the discs 19 and 20 are thus made such that the two discs 19 and 20 mesh with each other during their rotation about their axes, without that blowholes occur.
  • FIG. 10 is shown in an exploded view of a rotating center plate with a circular arc-shaped enlarged head portion together with the adjacent components (piston and housing), in which the remaining blow holes are closed.
  • FIG. 11 A spatial representation in Fig. 11 illustrates the assembly of housing, rotary piston and rotating center plates.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)

Claims (3)

  1. Pompe à pistons rotatifs pour liquides non homogènes, en particulier pour lisier, comportant un carter de pompe (12) avec un orifice d'entrée et un orifice de sortie, dans l'espace intérieur duquel sont logés quatre pistons rotatifs (15, 17 ; 16, 18) disposés sur deux arbres (13, 14), coopérant ensemble pour une rotation en sens inverse afin d'assurer le transport du liquide depuis l'orifice d'entrée jusqu'à l'orifice de sortie du carter, où l'espace intérieur du carter de la pompe est divisé en deux chambres de transport séparées, identiques, dont chacune loge une paire de pistons rotatifs coopérant ensemble et qui sont reliées entre elles à l'orifice d'entrée et à l'orifice de sortie du carter, où les deux pistons rotatifs de l'une des chambres de transport présentent une position angulaire décalée par rapport aux deux pistons rotatifs de l'autre chambre de transport, et, où entre les pistons rotatifs (15, 17, respectivement 16, 18) d'un arbre (13, respectivement 14) sont disposés des plaques ou disques (19, respectivement 20) tournant ensemble avec les pistons, caractérisée en ce que le diamètre de l'un des disques (19) correspond au diamètre extérieur des pistons (15, 16, 17, 18) tandis que le diamètre de l'autre disque (20) correspond au diamètre des noyaux de pistons.
  2. Pompe à pistons rotatifs pour liquides non homogènes, en particulier pour lisier, comportant un carter de pompe (12) avec un orifice d'entrée et un orifice de sortie, dans l'espace intérieur duquel sont logés quatre pistons rotatifs (15, 17 ; 16, 18) disposés sur deux arbres (13, 14), coopérant ensemble pour une rotation en sens inverse afin d'assurer le transport du liquide depuis l'orifice d'entrée jusqu'à l'orifice de sortie du carter, où l'espace intérieur du carter de la pompe est divisé en deux chambres de transport séparées, identiques, dont chacune loge une paire de pistons rotatifs coopérant ensemble et qui sont reliées entre elles à l'orifice d'entrée et à l'orifice de sortie du carter, où les deux pistons rotatifs de l'une des chambres de transport présentent une position angulaire décalée par rapport aux deux pistons rotatifs de l'autre chambre de transport, et, où entre les pistons rotatifs (15, 17, respectivement 16, 18) d'un arbre (13, respectivement 14) sont disposés des plaques ou disques (19, respectivement 20) tournant ensemble avec les pistons, caractérisée en ce que les disques (19, 20) présentent pour l'essentiel le même contour que les pistons (15, 16, 17, 18).
  3. Pompe à pistons rotatifs selon la revendication 2 caractérisée en ce que la forme du périmètre des disques (19, 20) se prolonge, après la zone d'étendue radiale maximale (192) des disques par rapport aux arbres (13, 14), de part et d'autre par une zone concave (191, 193) (courbures positives) après laquelle le rayon des disques correspond au rayons des zones convexes (courbures négatives) de part et d'autre des zones (194) d'étendue radiale minimale des disques.
EP05015840A 2004-08-03 2005-07-21 Pompe à pistons rotatifs Not-in-force EP1624189B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102004037561A DE102004037561A1 (de) 2004-08-03 2004-08-03 Drehkolbenpumpe

Publications (2)

Publication Number Publication Date
EP1624189A1 EP1624189A1 (fr) 2006-02-08
EP1624189B1 true EP1624189B1 (fr) 2007-06-06

Family

ID=35241144

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05015840A Not-in-force EP1624189B1 (fr) 2004-08-03 2005-07-21 Pompe à pistons rotatifs

Country Status (3)

Country Link
EP (1) EP1624189B1 (fr)
AT (1) ATE364136T1 (fr)
DE (2) DE102004037561A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE202010011626U1 (de) 2010-08-20 2010-10-21 Hugo Vogelsang Maschinenbau Gmbh Drehkolbenpumpe
DE202010015439U1 (de) 2010-11-16 2012-02-17 Hugo Vogelsang Maschinenbau Gmbh Drehkolbenpumpe und Gehäuse-Halbschale für selbige
US9732749B2 (en) 2009-09-08 2017-08-15 Hugo Vogelsang Maschinenbau Gmbh Rotary piston pump having converging inlet and outlet openings for conveying a fluid medium containing solids

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US693609A (en) * 1901-04-11 1902-02-18 Omar Stevens Rotary pump or force-blast blower.
US2028414A (en) * 1933-05-19 1936-01-21 Fairbanks Morse & Co Fluid displacement device
DE629654C (de) * 1934-04-01 1936-05-08 Carl Jaeger Drehkolbenmaschine mit ellipsenaehnlichen, aufeinander ablaufenden zylindrischen Kolben
US2382042A (en) * 1943-02-24 1945-08-14 E D Etnyre & Co Positive displacement gear pump
DE8432974U1 (de) * 1984-11-10 1985-02-14 Hugo Vogelsang Faß- und Maschinenbau GmbH, 4572 Essen Drehkolbenpumpe fuer inhomogene fluessigkeiten, insbesondere guelle
DE3707722A1 (de) 1987-03-11 1988-09-29 Alois Boerger Rotorpumpe, insbesondere fuer die foerderung von feststoffe enthaltenden fluessigkeiten
US4907954A (en) * 1987-11-20 1990-03-13 Tomasz Slupski Multiple lobed piston pump with angularly and axially displaced segments and throttle valve
DE4330085A1 (de) 1993-09-06 1995-03-09 Hugo Vogelsang Maschinenbau Gm Rotationskolben für Verdrängerpumpen nach dem Roots-Prinzip für inkompressible Medien
IT1298608B1 (it) 1998-03-09 2000-01-12 Gruppo Bertolaso Spa Macchina tappatrice

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9732749B2 (en) 2009-09-08 2017-08-15 Hugo Vogelsang Maschinenbau Gmbh Rotary piston pump having converging inlet and outlet openings for conveying a fluid medium containing solids
DE202010011626U1 (de) 2010-08-20 2010-10-21 Hugo Vogelsang Maschinenbau Gmbh Drehkolbenpumpe
WO2012022784A2 (fr) 2010-08-20 2012-02-23 Hugo Vogelsang Maschinenbau Gmbh Pompe à pistons rotatifs
US9127673B2 (en) 2010-08-20 2015-09-08 Hugo Vogelsang Maschinenbau Gmbh Rotary lobe pump having inlet and outlet aligned with gearbox casing
DE202010015439U1 (de) 2010-11-16 2012-02-17 Hugo Vogelsang Maschinenbau Gmbh Drehkolbenpumpe und Gehäuse-Halbschale für selbige
WO2012066026A2 (fr) 2010-11-16 2012-05-24 Hugo Vogelsang Maschinenbau Gmbh Pompe à piston rotatif et demi-coque de boîtier pour ladite pompe

Also Published As

Publication number Publication date
DE102004037561A1 (de) 2006-03-16
EP1624189A1 (fr) 2006-02-08
ATE364136T1 (de) 2007-06-15
DE502005000805D1 (de) 2007-07-19

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