EP1857680A2 - rotor de pompe - Google Patents

rotor de pompe Download PDF

Info

Publication number
EP1857680A2
EP1857680A2 EP06010218A EP06010218A EP1857680A2 EP 1857680 A2 EP1857680 A2 EP 1857680A2 EP 06010218 A EP06010218 A EP 06010218A EP 06010218 A EP06010218 A EP 06010218A EP 1857680 A2 EP1857680 A2 EP 1857680A2
Authority
EP
European Patent Office
Prior art keywords
rotor
pockets
rotor shaft
shaft
assembly according
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
EP06010218A
Other languages
German (de)
English (en)
Other versions
EP1857680A3 (fr
EP1857680B1 (fr
Inventor
Antony Mark Brown
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.)
Hilge GmbH and Co KG
Original Assignee
Grundfos Management AS
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 Grundfos Management AS filed Critical Grundfos Management AS
Priority to EP06010218.3A priority Critical patent/EP1857680B1/fr
Priority to PL06010218T priority patent/PL1857680T3/pl
Priority to ES06010218.3T priority patent/ES2622876T3/es
Priority to DK06010218.3T priority patent/DK1857680T3/en
Publication of EP1857680A2 publication Critical patent/EP1857680A2/fr
Publication of EP1857680A3 publication Critical patent/EP1857680A3/fr
Application granted granted Critical
Publication of EP1857680B1 publication Critical patent/EP1857680B1/fr
Active 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
    • 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
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0057—Driving elements, brakes, couplings, transmission specially adapted for machines or pumps
    • F04C15/0061—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
    • F04C15/0073—Couplings between rotors and input or output shafts acting by interengaging or mating parts, i.e. positive coupling of rotor and shaft
    • 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

Definitions

  • the invention relates to a rotor assembly for a pump, in particular for a rotary piston pump.
  • Rotary pumps usually have two parallel-lying rotor shafts, which are coupled in their rotational movement with each other and each carry a rotatable piston or a gear at one axial end.
  • the pistons or gears mesh with each other and form a positive displacement pump. It is important for these pumps that the pistons run synchronously.
  • both the piston and the transmission elements which couple the two shafts rotatably connected to the rotor shafts rotatably connect. At the same time an accurate adjustment of the elements on the shafts is required to ensure the synchronous running of the two pistons so that they rotate into each other.
  • the rotor assembly according to the invention for a pump in particular for a rotary piston pump, has at least one rotor shaft and a rotor attached thereto.
  • the rotor forms the piston in the rotary piston pump, which preferably engages with the piston of a second rotor shaft.
  • the rotor has a recess into which the rotor shaft engages.
  • the rotor shaft For rotationally fixed attachment of the rotor to the rotor shaft, the rotor shaft according to the invention on the outer circumference at least one cross-section circular-segment-shaped pocket.
  • the cross-sectionally circular-shaped pocket forms a cylinder-segment-shaped recess whose diameter or central axis preferably extends parallel to the longitudinal or rotational axis of the rotor shaft.
  • Opposite is formed on the inner circumference of the recess of the rotor a corresponding, circular cross-section shaped pocket. That is, this pocket also forms a cylinder-segment-shaped recess whose longitudinal or central axis preferably extends parallel to the longitudinal or rotational axis of the rotor.
  • the longitudinal or rotational axis of the rotor is identical to the longitudinal or rotational axis of the rotor shaft.
  • the two opposite, circular segment-shaped pockets preferably together form a circular-cylindrical recess or a circular-cylindrical hole which extends parallel to the longitudinal axis of the rotor shaft between the inner circumference of the recess and the outer circumference of the rotor shaft.
  • In these so opposite pockets is a corresponding in cross-section, preferably circular, d. H. circular cylindrical connecting element used. This connecting element produces the positive, rotationally fixed connection between rotor and rotor shaft.
  • the circular segment-shaped cross-sectional areas of the pockets on the outer circumference of the rotor shaft and on the inner circumference of the recess of the rotor are preferably dimensioned such that they together form a Form circular section.
  • the two pockets are semicircular in cross section, so that the pockets on the outer circumference of the rotor shaft and on the inner circumference of the recess of the rotor each have a semi-cylindrical shape, which together define a cylindrical recess into which a cylindrical connecting element can be used.
  • the pockets in the rotor or in the outer circumference of the rotor shaft are preferably milled there, so that they can be formed there with high accuracy at the desired angular position.
  • the cylindrical connecting element can then be used only suitable if the pockets on the inner circumference of the rotor and the outer circumference of the rotor shaft are exactly opposite each other, d. H. the rotor is in a predetermined angular position with respect to the rotor shaft. By correspondingly close fit, a backlash-free, positive connection between rotor and rotor shaft can be achieved here.
  • both the central and longitudinal axes of the pockets on the rotor shaft and on the rotor and the longitudinal axis of the circular cross-section connecting element extend parallel to the axis of rotation of the rotor shaft and thus of the rotor.
  • the pockets on the outer circumference of the rotor shaft are arranged corresponding to the pockets on the inner circumference of the recess of the rotor in the same angular positions, so that always one pocket on Outer circumference of the rotor shaft of a pocket on the inner circumference of the recess exactly opposite, so that these two pockets together form a circular cross-section, ie a total circular cylindrical receiving opening for a connecting element.
  • a connecting element is used in each case. In this way, a more resilient, positive connection between the rotor and the rotor shaft is provided, via which larger torques can be transmitted.
  • the plurality of pockets on the rotor shaft and the corresponding, opposite pockets on the rotor are preferably arranged distributed irregularly over the circumference.
  • the connecting elements are glued in the pockets on the rotor and / or in the pockets on the rotor shaft.
  • the fasteners are secured in the pockets so that they can not slip out or come loose. So a durable connection between rotor and rotor shaft can be created.
  • the connecting elements may be designed to be spreadable in their diameter direction. This makes it possible to easily insert the connecting elements in the opposite pockets and then to spread so that they tense in the pockets. So then a firm connection between rotor and rotor shaft is created. At the same time this allows an automatic accurate alignment or adjustment of the opposite pockets during spreading of the connecting element.
  • the rotor is then automatically aligned and fixed in the defined, predetermined angular position with respect to the rotor shaft. Also, the exact centering can be done by spreading the fasteners.
  • the connecting elements may be formed so that their spread is reversible to them can be solved again, so that to be able to remove the rotor from the rotor shaft, for example, for maintenance or replacement of wearing parts.
  • the connecting elements are preferably made of two axially arranged cylindrical bodies and at least one expansion element located axially between the cylinder bodies, wherein the two cylinder bodies are mutually axially adjustably connected to each other. This can be done for example by a screw which connects the two cylinder body together. If the two cylinder body to be moved toward each other by adjusting the adjusting element, such as a screw, the spreading element located between them can be spread.
  • At least one of the two cylinder body of a connecting element is preferably fixedly connected to the rotor and / or the rotor shaft, preferably non-rotatably connected to the rotor and / or the rotor shaft.
  • the rotationally fixed connection can be made for example by a positive engagement or by clamping or gluing.
  • the invention relates to a rotor assembly, which may in particular also be designed according to the preceding description, in which at least one rotor shaft and a rotatably connected thereto drive or driven pinion is provided.
  • a rotor assembly is also intended in particular for use in a rotary piston pump in which a plurality of rotor shafts must be coupled together in their rotational movement.
  • a first pinion is preferably arranged non-rotatably on a driven rotor shaft and arranged on a second, parallel rotor shaft, a second, meshing with the first pinion pinion, so that one rotor shaft is driven by the other.
  • the drive pinion has a central recess with a conical inner peripheral surface. This inner circumferential surface extends conically around the longitudinal or rotational axis of the rotor shaft and the drive pinion.
  • the drive shaft has a corresponding conical outer peripheral surface, wherein the conical inner peripheral surface and the conical outer peripheral surface for fixing the drive pinion on the rotor shaft with each other in engagement or in abutment are. In this way, the drive pinion is rotatably held on the rotor shaft.
  • a cylindrical contact surface adjoining the smaller diameter end of the conical inner peripheral surface is formed in the recess of the rotor, and the rotor shaft has a corresponding cylindrical contact surface which adjoins the smaller diameter end of the conical outer peripheral surface.
  • the drive pinion is further axially displaced relative to the rotor shaft, so that the conical inner peripheral surface runs onto the corresponding conical outer circumferential surface and thus the drive pinion is fixed firmly, in particular rotationally fixed on the rotor shaft.
  • the rotor assembly as described above is preferably part of a rotary piston pump, which preferably has two rotor assemblies as described above.
  • the rotor assembly according to the invention is particularly suitable for use in a rotary piston or rotary piston pump, as for example in the sectional view in Fig. 1 is shown.
  • rotary piston pumps have in their interior two mutually parallel rotor assemblies 2 and 4, which via pinion 6 and 8 are engaged with each other.
  • the rotor assembly 2 is driven via its shaft end 10 by a motor, not shown.
  • the shafts of the rotor assemblies 2 and 4 are each connected to a rotor or rotary pistons 12, 14, which mesh with each other and thus form a positive displacement pump.
  • the invention relates to the rotor assemblies 2 and 4 and there the attachment of the rotors 12 and 14 to the rotor shafts 16, 18. Further, the invention relates to the attachment of the pinion 6 and 8 on the rotor shafts 16, 18. If below the further embodiments of these fasteners only will be described with reference to one of the two rotor assemblies 2 and 4, it is understood, however, that the configuration is selected according to the respective other rotor assembly.
  • FIGS. 2 to 4 show a first embodiment according to the invention of the attachment of the rotor 12 to the rotor shaft 16.
  • the rotor 12 is connected to the rotor shaft 16 at a shaft end, in such a way that it is plugged onto the rotor shaft in the direction of the axis of rotation or rotation.
  • the rotor 12 has in its interior, concentric with the longitudinal or rotational axis X, a recess 20, into which the rotor shaft 16 engages with its shaft end 22.
  • At the outer periphery of the shaft end 22 are formed semicircular or semi-cylindrical pockets 24 whose longitudinal axes and peripheral surfaces extend parallel to the rotation axis X.
  • pockets 26 are formed on the inner circumference, which also have a semi-circular cross-section or a semi-cylindrical shape and their central axes extend parallel to the axis of rotation X.
  • the pockets 26 are arranged on the inner periphery of the recess 20 so that they are arranged around the longitudinal axis X at the same angular positions as the pockets 24 so that at the desired angular position of the rotor 12 with respect to the rotor shaft 16 is always a pocket 24 a pocket 26th exactly opposite.
  • a cylindrical recess formed in the plane of contact between the inner circumference of the recess 20 and the outer circumference of the shaft end 22 is always formed by a pocket 24 together with a pocket 26, into which a cylindrical or roller-shaped connecting element 28 is inserted.
  • the connecting elements 28 produce a positive connection between the rotor shaft 16 and the rotor 12, which enables a torque transmission from the rotor shaft 16 to the rotor 12.
  • the defined orientation of the rotor 12 in the radial direction of the rotor shaft 16 can also be done by the connecting elements 28, since they are distributed over the entire circumference of the rotor shaft 16 and the shaft end 22 and with appropriate fit the rotor 12 without play in the radial direction of the Fix shaft end 22.
  • a fixing screw 30 which is screwed into a front-side threaded bore 32 in the direction of the longitudinal axis X in the shaft end 22 and thus secures the rotor 12 in the axial direction of the rotor shaft 16.
  • the head of the fixing screw 30 engages over the peripheral edge of the recess 20.
  • the connecting elements 28 according to the embodiment shown in FIGS. 2 to 4 are solid roller bodies made of steel, for example. For additional security, these can be glued in the pockets 24 and 26. Furthermore, it is also possible to additionally apply an adhesive between the outer circumference of the shaft end 22 and the inner circumference of the recess 20.
  • FIGS. 5 to 8 An alternative connection between rotor 14 and rotor shaft 18 will be described with reference to FIGS. 5 to 8.
  • the shaft end 22 is formed with the pockets 24 as described above with reference to the first embodiment.
  • the recess 20 with the pockets 26 is formed identical to the first embodiment according to the foregoing description.
  • This second embodiment differs only in the configuration of the connecting elements 28, which are designed here as clamping or clamping elements and will be described in more detail with reference to FIGS. 7 and 8.
  • These connecting elements 28 can be tensioned after insertion into the pockets 24 and 26, so that they expand in the radial direction and thus generate a clamping force between the rotor 12, 14 and the associated rotor shaft 16, 18.
  • a complete fixation of the rotor 12, 14 on the rotor shaft 16, 18 can be achieved, and it can be dispensed with the fixing screw 30, which can also be arranged in addition.
  • the connecting elements 28 according to the second embodiment are also circular in cross-section, that is, they are generally circular-cylindrical or barrel-shaped. They are formed by two axially spaced cylinder bodies 34, which are interconnected by a screw 36. In this case, the screw 36 penetrates the one cylinder body 34 through a hole 38 without thread and engages in the other cylinder body 34 in a thread 40 a. By turning the Screw 36 can thus be the cylinder body 34 in the axial direction towards each other and moved apart.
  • a ring 42 is arranged, which does not come into contact with the adjacent cylinder bodies 34 at the axial end faces.
  • the ring 42 has centrally on the outer circumference a projection 44 which is bevelled or gripped on the cylinder bodies 34 facing sides. Accordingly, the end faces of the cylinder body 34, which face the projection 44, are chamfered such that between the cylinder bodies 34 and the projection 44 annular grooves are formed, which widen outwardly. In these grooves clamping rings 46 are arranged.
  • the pinion or drive pinion 6 has a conical, central recess 48, with which the pinion 6 to a corresponding, d. H. inclined at the same angle, conical contact surface 50 is placed on the rotor shaft 16.
  • a cylindrical contact surface 52 connects, wherein the conical contact surface 50 is separated from the contact surface 52 by a recess 54.
  • a cylindrical contact surface 56 is formed on the inner periphery of the recess 48 at the tapered end of the conical inner peripheral surface, which has substantially the same diameter as the cylindrical contact surface 52.
  • This embodiment of the connection between the pinion 6 and the rotor shaft 16 facilitates the alignment of the pinion 6 in a certain angular position with respect to the longitudinal axis X during assembly. This alignment is required because the rotors 12 and 14 must be arranged at a certain angle to each other and rotate each other.
  • the pinion 6 can first be pushed onto the rotor shaft such that initially only the cylindrical contact surfaces 52 and 56 come to rest. In this position, the pinion 6 is aligned in the radial direction on the rotor shaft 16, but can still be moved in the axial direction along the longitudinal axis X and in the circumferential direction. When the desired angular orientation is achieved, the pinion 6 is further displaced in the axial direction toward the shaft end 22, so that the conical inner surface of the recess 48 comes to rest on the conical bearing surface 50 of the rotor shaft 16.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
EP06010218.3A 2006-05-18 2006-05-18 Rotor de pompe Active EP1857680B1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
EP06010218.3A EP1857680B1 (fr) 2006-05-18 2006-05-18 Rotor de pompe
PL06010218T PL1857680T3 (pl) 2006-05-18 2006-05-18 Zespół wirnika
ES06010218.3T ES2622876T3 (es) 2006-05-18 2006-05-18 Conjunto de rotor
DK06010218.3T DK1857680T3 (en) 2006-05-18 2006-05-18 rotor module

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP06010218.3A EP1857680B1 (fr) 2006-05-18 2006-05-18 Rotor de pompe

Publications (3)

Publication Number Publication Date
EP1857680A2 true EP1857680A2 (fr) 2007-11-21
EP1857680A3 EP1857680A3 (fr) 2008-02-20
EP1857680B1 EP1857680B1 (fr) 2017-02-22

Family

ID=37057411

Family Applications (1)

Application Number Title Priority Date Filing Date
EP06010218.3A Active EP1857680B1 (fr) 2006-05-18 2006-05-18 Rotor de pompe

Country Status (4)

Country Link
EP (1) EP1857680B1 (fr)
DK (1) DK1857680T3 (fr)
ES (1) ES2622876T3 (fr)
PL (1) PL1857680T3 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN118110667A (zh) * 2024-04-26 2024-05-31 德帕姆(杭州)泵业科技有限公司 一种用于泵用转子防松压盖的结构

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2635552A (en) * 1949-01-31 1953-04-21 Bump Pump Co Sanitary pump assemblage
EP0101345A1 (fr) * 1982-07-22 1984-02-22 BENDIX France Compresseur volumétrique à vis
EP0287797A2 (fr) * 1987-03-13 1988-10-26 Leybold Aktiengesellschaft Pompe à vide à deux arbres munie d'une transmission de synchronisation
US4940394A (en) * 1988-10-18 1990-07-10 Baker Hughes, Inc. Adjustable wearplates rotary pump
CA2079729A1 (fr) * 1992-10-02 1994-04-03 Nicholas Verhoeven Parois rainurees de corps de pompe destinees a l'elimination des depots fibreux
JPH09137731A (ja) * 1995-11-16 1997-05-27 Tochigi Fuji Ind Co Ltd スクリュ式過給機
DE10322501A1 (de) * 2003-05-19 2004-12-09 Peter Schnabl Drehkolbenpumpe

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2635552A (en) * 1949-01-31 1953-04-21 Bump Pump Co Sanitary pump assemblage
EP0101345A1 (fr) * 1982-07-22 1984-02-22 BENDIX France Compresseur volumétrique à vis
EP0287797A2 (fr) * 1987-03-13 1988-10-26 Leybold Aktiengesellschaft Pompe à vide à deux arbres munie d'une transmission de synchronisation
US4940394A (en) * 1988-10-18 1990-07-10 Baker Hughes, Inc. Adjustable wearplates rotary pump
CA2079729A1 (fr) * 1992-10-02 1994-04-03 Nicholas Verhoeven Parois rainurees de corps de pompe destinees a l'elimination des depots fibreux
JPH09137731A (ja) * 1995-11-16 1997-05-27 Tochigi Fuji Ind Co Ltd スクリュ式過給機
DE10322501A1 (de) * 2003-05-19 2004-12-09 Peter Schnabl Drehkolbenpumpe

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
"ROTACNI OBJEMOVA CERPADLA" ANNOUNCEMENT SIGMA GROUP, XX, XX, Januar 2004 (2004-01), Seiten 1-6, XP000962380 *

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN118110667A (zh) * 2024-04-26 2024-05-31 德帕姆(杭州)泵业科技有限公司 一种用于泵用转子防松压盖的结构

Also Published As

Publication number Publication date
DK1857680T3 (en) 2017-05-08
PL1857680T3 (pl) 2017-09-29
EP1857680A3 (fr) 2008-02-20
EP1857680B1 (fr) 2017-02-22
ES2622876T3 (es) 2017-07-07

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