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EP3765201B1 - Rotor d'un séparateur centrifuge et séparateur centrifuge - Google Patents

Rotor d'un séparateur centrifuge et séparateur centrifuge Download PDF

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Publication number
EP3765201B1
EP3765201B1 EP19714111.2A EP19714111A EP3765201B1 EP 3765201 B1 EP3765201 B1 EP 3765201B1 EP 19714111 A EP19714111 A EP 19714111A EP 3765201 B1 EP3765201 B1 EP 3765201B1
Authority
EP
European Patent Office
Prior art keywords
spacers
rotor
disc
discs
plates
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.)
Active
Application number
EP19714111.2A
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German (de)
English (en)
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EP3765201A1 (fr
Inventor
Markus LÜERSMANN
Eike Stitterich
Tom Klaver
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.)
Hengst SE and Co KG
Original Assignee
Hengst SE and Co KG
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Application filed by Hengst SE and Co KG filed Critical Hengst SE and Co KG
Publication of EP3765201A1 publication Critical patent/EP3765201A1/fr
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Publication of EP3765201B1 publication Critical patent/EP3765201B1/fr
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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B04—CENTRIFUGAL APPARATUS OR MACHINES FOR CARRYING-OUT PHYSICAL OR CHEMICAL PROCESSES
    • B04B—CENTRIFUGES
    • B04B5/00—Other centrifuges
    • B04B5/12—Centrifuges in which rotors other than bowls generate centrifugal effects in stationary containers
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B04—CENTRIFUGAL APPARATUS OR MACHINES FOR CARRYING-OUT PHYSICAL OR CHEMICAL PROCESSES
    • B04B—CENTRIFUGES
    • B04B7/00—Elements of centrifuges
    • B04B7/08—Rotary bowls
    • B04B7/12—Inserts, e.g. armouring plates
    • B04B7/14—Inserts, e.g. armouring plates for separating walls of conical shape
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B04—CENTRIFUGAL APPARATUS OR MACHINES FOR CARRYING-OUT PHYSICAL OR CHEMICAL PROCESSES
    • B04B—CENTRIFUGES
    • B04B5/00—Other centrifuges
    • B04B5/005—Centrifugal separators or filters for fluid circulation systems, e.g. for lubricant oil circulation systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M13/00—Crankcase ventilating or breathing
    • F01M13/04—Crankcase ventilating or breathing having means for purifying air before leaving crankcase, e.g. removing oil
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B04—CENTRIFUGAL APPARATUS OR MACHINES FOR CARRYING-OUT PHYSICAL OR CHEMICAL PROCESSES
    • B04B—CENTRIFUGES
    • B04B5/00—Other centrifuges
    • B04B5/12—Centrifuges in which rotors other than bowls generate centrifugal effects in stationary containers
    • B04B2005/125—Centrifuges in which rotors other than bowls generate centrifugal effects in stationary containers the rotors comprising separating walls
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M13/00—Crankcase ventilating or breathing
    • F01M13/04—Crankcase ventilating or breathing having means for purifying air before leaving crankcase, e.g. removing oil
    • F01M2013/0422—Separating oil and gas with a centrifuge device

Definitions

  • the present invention relates to a rotor of a centrifugal separator, the rotor having a central shaft on which a stack of plates made up of a plurality of identical plates is arranged, the shaft having an engagement contour on its outer circumference for non-rotatable, axially displaceable engagement with a counter-contour on the inner circumference of the plates of the stack of plates, wherein the engagement contour and the counter-contour can be brought into engagement with one another in a plurality of rotational positions spaced apart from one another in the circumferential direction, and wherein each plate has spacers spaced apart from one another in the circumferential direction of the plates, each of which separates two adjacent plates at an axial distance, forming an intermediate flow gap with a predeterminable gap dimension keep from each other.
  • the invention also relates to a centrifugal separator.
  • the document EP 3 124 120 A1 shows an oil separator configured to separate oil mist from a gas.
  • the oil separator includes a rotor. This rotor has multiple cutting disks stacked along the axis line of a spindle. Each of the separator disks is in the form of a truncated cone plate member and is formed with concave-convex ribs extending radially from the center of rotation on outer peripheral side parts corresponding to the inclined surfaces of the truncated cone.
  • the concavo-convex ribs include first convex portions and second convex portions, the first convex portions on the outer peripheral side parts having a convex shape on the front surface side and a concave shape on the back surface side, and the second convex portions on the outer peripheral side parts include a convex shape on the back and a concave shape on the front. This allows stacks of cutting discs with form a predetermined distance between the individual cutting disks without the need for separate spacers.
  • the document US 779 099 A shows a centrifugal separator with a rotor, the rotor having a central shaft on which a stack of plates made up of several identical plates is arranged, the shaft having an engagement contour on its outer circumference for non-rotatable, axially displaceable engagement with a counter-contour on the inner circumference of the plates of the stack of plates having.
  • the engagement contour and the counter-contour can be brought into engagement with one another in a plurality of rotational positions spaced apart from one another in the circumferential direction.
  • the plates are corrugated as seen in the plate peripheral direction, with the corrugations each holding two adjacent plates at an axial distance from one another, with the formation of intermediate flow channels with a definable cross section.
  • the corrugated plates are designed in such a way that with different twisted positions of adjacent plates relative to one another in the plate stack, at least two different axial distances with different cross sections of the flow channels between the adjacent plates can be adjusted.
  • the plates here have the shape of a truncated cone and the inclined, radially outer part of the plates is designed as a closed surface.
  • the inner circumference of the radially inner, flat area of the plates is provided with the counter-contour to the contour of engagement of the central shaft.
  • Radially outside of the counter-contour are distributed in the circumferential direction several flow openings through which a gas to be cleaned flows axially during operation of the rotor and from where the gas is then deflected radially outwards into the flow gaps between the adjacent plates.
  • An arrangement of spacer webs running over the lower side of the obliquely aligned area of the plates is used here to space the plates from one another.
  • the document EP 2 349 578 B1 describes a separator disk adapted to be included in a disk pack of a centrifuge rotor.
  • the separator disc has a tapered shape and extends about an axis of rotation and along a tapered rotating symmetrical surface along the axis of rotation.
  • the separator plate has an inner surface and an outer surface.
  • the separating disc is made of a material, the separating disc being configured in a way that it has a clearance between the separating disc and an adjacent separating disc in the disc pack and thus includes first protrusions extending outwardly from the tapered rotating symmetrical surface, and second projections extending inwardly from the tapered rotating symmetrical surface.
  • Each first and second projection defines a contact zone adapted to contact an adjacent separator disk in the disk pack.
  • the contact zones of the first projections are offset with respect to the contact zones of the second projections, seen in a direction normal to the outer face.
  • the first and second projections are sequentially provided in a peripheral direction of the separator disk. What is important here is that the tapered shape and the projections of the separator disc were provided by pressing a blank of the material against a tool part having a shape corresponding to the tapered shape with the projections of the pressed separator disc.
  • the document EP 2 334 439 B1 shows a disk pack for a centrifuge rotor of a centrifugal separator, which is designed for the separation of components in a medium supplied, the disk pack having a multiplicity of separating plates which are present one on top of the other in the plate pack.
  • Each separator disc extends about an axis of rotation and has a cone-like shape with an inner surface and an outer surface along the axis of rotation.
  • Each separating disk is made from at least one material, with the separating disks in the stack of disks being prestressed against one another with a prestressing force.
  • the separating discs have a plurality of first separating discs, each of which has a number of spacer elements.
  • Each separating plate has at least one section without spacer elements.
  • the first separating discs are polarly positioned in such a way that the spacer elements of one separating disc abut the portion of an adjacent separating disc. It is essential here that the spacer elements have a number of pairs of spacer elements, the pairs each having a first spacer element which extends away from the outer surface and a second spacer element which extends away from the inner surface, the first and second spacers are offset in relation to each other as viewed in a normal direction with respect to the outer surface and sequentially in a peripheral direction of the first separator disc be provided that the prestressing force causes an abutment force between the spacer elements and the adjacent separating disk and an elastic deformation of the section of at least the separating disks, and that this elastic deformation ensures an increase in the abutment force between the spacer elements and the adjacent separating disk during rotation of the disk pack.
  • a disadvantage of most of the known rotors and plates described above is that the axial distance between adjacent plates in the stack of plates is fixed at a single value, which is determined by the height of the spacer webs or the first and second projections or the spacer elements on the plates is predetermined. If a different axial distance between adjacent plates in the stack of plates is desired or required, it is necessary to manufacture new plates with spacer webs or first and second projections or spacers of a different, smaller or larger axial height. However, such production is unfavorable and, in particular, uneconomical with regard to the necessary investment in tools and the differentiation of parts when assembling the stack of plates.
  • US 779 099 A Although two different disc distances can be set, only relatively narrow flow channels, but no intermediate flow gaps, are provided between the adjacent discs.
  • the object of the present invention is therefore to create a rotor of the type mentioned at the outset, which avoids the disadvantages mentioned and in which it is possible in a technically simple and economically favorable manner to use different distances and thus different widths of intermediate flow gaps between the to realize plates in a stack of plates.
  • a corresponding centrifugal separator is to be created.
  • the solution to the first part of the task relating to the rotor is achieved according to the invention with a rotor of the type mentioned at the beginning, which is characterized in that the spacers of the plates are designed and arranged in such a way that with different rotational positions of adjacent plates relative to one another in the plate stack there are at least two different axial distances with different gap dimensions of the flow gap between the adjacent ones plates are adjustable and that the circumferentially spaced twisted positions, in which the engagement contour and the counter-contour can be brought into engagement with each other, are in two superimposed angular grids that are offset relative to one another in the circumferential direction by an offset angle, with the two angular grids each having a uniform matching grid angular spacing , where the screen angle spacing is an integer fraction of 360° and the offset angle is less than half the screen angle spacing.
  • the invention advantageously enables stacks of plates to be created from mutually identical plates with at least two different plate spacings in the plate stack, with the respective plate spacing only depending on the relative twisted position of the adjacent plates. Since only one design of plates is required, the tooling costs are advantageously kept low, which results in good economics in the manufacture of plate stacks and rotors for centrifugal separators. In addition, the axial distance between two immediately adjacent plates can be changed here even with a small angular offset by the aforementioned offset angle.
  • each plate has first and second spacers and that the first and second spacers differ in terms of their height and/or their radial position on the plate.
  • These spacers are easy to produce and the axial plate spacing can be changed simply by placing two directly adjacent plates on the central shaft, rotated relative to one another by the grid angle spacing or by the offset angle.
  • first and second spacers are formed by two different humps or beads formed or stamped into the plates, each forming an elevation on one side of the plate and a depression on the other side of the plate.
  • Such spacers can advantageously be produced by simply pressing or embossing, for example.
  • the spacers which are spaced apart from one another in the circumferential direction of the plate, are each designed as individual humps or as a radially running row of a plurality of humps.
  • each plate has first and second spacers and that the first and second spacers are formed by webs or nubs that are attached to or formed on the plates and form elevations.
  • the webs or knobs forming the first spacers be arranged on the top side of the plate, that the webs or knobs forming the second spacers be arranged on the bottom side of the plate and that the webs or knobs forming the first spacers be arranged relative to the webs or nubs forming the second spacers are offset in the circumferential direction of the plate.
  • the axial plate spacing can be easily changed by placing two directly adjacent plates rotated by the screen angle spacing on the central shaft, with the upper and lower side spacers of two directly adjacent plates either meeting and causing a larger axial plate spacing or not meeting and bring about a smaller axial disc distance.
  • a further rotor configuration provides that the webs or knobs forming the first spacers are arranged on the top side of the plate, the webs or knobs forming the second spacers are arranged on the underside on the plate, the webs or knobs forming the first spacers on the the webs or knobs forming the second spacer are arranged congruently and that the angular spacing of the spacers spaced apart from one another in the circumferential direction of the plates corresponds to twice the grid angle spacing.
  • the axial plate spacing can be easily changed by placing two directly adjacent plates on the central shaft, rotated by the grid angle spacing or the offset angle.
  • the webs or knobs forming the first spacers, arranged on the top side of the plate, and the webs or knobs forming the second spacers, arranged on the underside of the plate, are identical to one another.
  • the plates within the plate stack of the rotor have a smaller axial distance from one another with a smaller gap in a region of the rotor close to the inflow and a greater axial distance from one another with a larger gap in a region of the rotor remote from the inflow. In this way, in particular, a more uniform distribution of a volume flow of a fluid medium to be treated in the rotor over the plurality of flow gaps can be achieved.
  • the engagement contour and the counter-contour should be in two to sixteen, preferably six to twelve, in the circumferential direction of the central shaft and the plate can be brought into engagement with one another in twisted positions spaced apart from one another.
  • the number of twisted positions in which the central shaft and the plates can be brought into engagement with one another can also be greater than the aforementioned numbers, in which case the grid angle spacing then becomes correspondingly smaller. This can be expedient, for example, if more than two different axial disc distances are to be adjustable.
  • the disks of the rotor are preferably press-stamped parts made from sheet metal or injection-moulded parts made from plastic. Both types of plates mentioned can be produced comparatively easily and inexpensively and can be provided with the necessary spacers, both of which preferably take place in one operation.
  • the engagement contour on the outer circumference of the shaft be formed by a number of n teeth running in the longitudinal direction of the shaft and projecting radially outwards and that the counter-contour on the inner circumference of the plates be formed by a number of n or 2 xn to the teeth matching, radially outwardly facing recesses is formed.
  • the number n is preferably between 2 and 8, preferably 3 to 6, in order not to make the production of the engaging and counter-contours too complicated.
  • the number n also depends on the forces to be absorbed during operation of the rotor and acting in the circumferential direction of the rotor between the plates and the central shaft.
  • the centrifugal separator according to the invention is an oil mist separator for the crankcase ventilation gas of an internal combustion engine and can advantageously serve to effectively separate oil mist and oil droplets from the crankcase ventilation gas of the internal combustion engine.
  • the discs In a rotor of such a centrifugal separator, the discs have a very small distance from one another, in practice, for example, between about 0.3 and 0.5 mm.
  • the plates can then be designed, for example, so that they form a first distance of 0.3 mm between them in a first relative twisted position and a second distance of 0.5 mm between them in a second relative twisted position.
  • the plates and their spacers can also be designed in such a way that, in a third rotational position relative to one another, they form a third distance between them, for example of 0.4 mm. In this way, needs-based, different gap dimensions between the mutually identical discs of the rotor can be easily adjusted during rotor production.
  • the drawings show a rotor 1 of a centrifugal separator, which is otherwise not shown here, in a first embodiment.
  • the rotor 1 has a central shaft 2 on which a stack of plates 3 made up of several identical plates 30 is arranged.
  • the plates 30 each have the known shape of a truncated cone shell and can be made of sheet metal or plastic.
  • the shaft 2 has an engagement contour 21 on its outer circumference for non-rotatable, axially displaceable engagement with a counter-contour 31 on the inner circumference of the plates 30 of the plate stack 3, the engagement contour 21 here having the shape of a six-pointed star.
  • the engagement contour 21 and the counter-contour 31 can be brought into engagement with one another in a plurality of relative rotational positions spaced apart from one another in the circumferential direction by a grid angle distance a, here of 60°.
  • the plates 30 have spacers 4, 5, which in the stack of plates 3 hold two adjacent plates 30 at a distance from one another, forming the flow gap 34 between them with a predetermined gap dimension.
  • each plate 30 has two such different first and second spacers 4, 5 spaced apart from one another in the circumferential direction of the plates 30 that with different rotational positions of adjacent plates 30 relative to one another in the plate stack 3 there are two different distances with different gap dimensions h 1 , h 2 of the flow gap 34 between the adjacent plates 30 can be produced, as can be seen in particular in FIG.
  • the two different first and second spacers 4, 5 are formed or stamped here by two different ones in the plates 30, each on one side of the plate, here the underside, an increase and on the other side of the plate, here the upper side, forming a depression, arranged in pairs one behind the other in the radial direction.
  • the first spacers 4 and the second spacers 5 are spaced apart from one another by an angular distance ⁇ of 60°.
  • This angular distance ⁇ is therefore identical to the grid angle distance ⁇ of the engaging and counter-contours 21, 31.
  • the humps forming the first and second spacers 4, 5 differ here both in their height and in their radial position on the plate 30.
  • the humps forming the first spacers 4 have a greater axial depth and are located somewhat further outwards as seen in the radial direction.
  • the humps forming the second spacers 5 have a smaller axial depth and are located somewhat further inward, viewed in the radial direction, than the humps forming the first spacers 4 .
  • the two adjacent Plate 30 has a smaller distance with a gap dimension h 1 of the intermediate flow gap 34.
  • the two adjacent plates 30 have a larger one Distance with a gap dimension h 2 of the intermediate flow gap 34.
  • the identical plates 30 within the plate stack 3 of the rotor 1 can therefore have different distances from one another with different gap dimensions h 1 , h 2 of the flow gaps 34 .
  • This can be used advantageously, for example, to place the plates 30 at a smaller axial distance from one another with a smaller gap dimension h 1 in a region of rotor 1 close to the inflow, and to place the plates 30 at a greater axial distance from one another with a larger gap h 1 in a region of rotor 1 remote from the inflow Arranging the gap dimension h 2 in order to even out the flow through the plate stack 3 .
  • the Figures 4 to 7 show the rotor 1 in a second embodiment. What differs from the first embodiment of the rotor 1 is that the humps forming the first and second spacers 4, 5 are smaller and in the form of radially extending rows of humps, each with four humps. In this way, more points of contact are formed between the respectively adjacent plates 30 in the plate stack 3, which benefits its dimensional stability during operation at high speeds.
  • the humps forming the first and second spacers 4, 5 differ both in their height and in their radial position on the plate 30.
  • the humps forming the first spacers 4 have a greater axial depth and are located somewhat further outwards as seen in the radial direction .
  • the protuberances forming the second spacers 5 have a smaller axial depth and are located somewhat further inward as seen in the radial direction.
  • This angular distance ⁇ is therefore identical to the grid angle distance ⁇ of the engaging and counter-contours 21, 31.
  • the two adjacent plates 30 have a smaller one Distance with a gap dimension h 1 of the intermediate flow gap 34.
  • the rotor 1 agrees with the Figures 4 to 7 with the embodiment according to the Figures 1 to 3 match, so reference is made to their description.
  • the Figures 8 to 11 show the rotor 1 in a third embodiment.
  • the first and second spacers 4, 5 are now formed by webs which are attached to the plates 30 or formed thereon and form elevations.
  • the spacers 4, 5 formed by the webs here run in a straight line in the radial direction.
  • the spacers 4, 5 can also be curved.
  • the webs forming the first spacer 4, here three pieces, are arranged on the upper side on the plate 30 and the webs forming the second spacer 5, also three pieces, are arranged on the underside on the plate 30.
  • the webs forming the first spacers 4 are offset relative to the webs or knobs forming the second spacers 5 in the circumferential direction of the plate 30 .
  • the angular distance ⁇ between the three webs forming the first spacers 4 is 120° in each case here.
  • the angular spacing ⁇ of the three webs forming the second spacers 5 is also 120° here.
  • the angular distance between in each case a first spacer 4 and a second spacer 5 within the plate 30 is 60°. This angle of 60° corresponds to the grid angle distance ⁇ of the different relative rotational positions of the plate 30 to the central shaft 10, in which the two can be brought into engagement with one another by means of the engagement contour 21 and the counter-contour 31.
  • the gap dimension h 1 corresponds to the height of the individual spacers 4, 5 formed by the webs, which are identical to one another here.
  • the second and third plates 30 seen from above are arranged in a relative twisted position in the stack of plates 3, in which the first spacers 4 of one plate 30, here the lower plate, are congruent with the second spacers 5 of the other plate 30, here the upper plate, then have the two adjacent plates 30 have a larger spacing with a gap dimension h 2 of the intermediate flow gap 34.
  • the gap dimension h 2 here corresponds to the added height of the spacers 4 and 5 formed by the webs lying one on top of the other.
  • the Figures 12 to 15 show the rotor 1 in a fourth embodiment.
  • the first and second spacers 4, 5 are formed by webs which are attached or formed on the plates 30 and form elevations.
  • the webs forming the first spacer 4, here three pieces, are arranged on the upper side on the plate 30 and the webs forming the second spacer 5, also three pieces, are arranged on the underside on the plate 30.
  • the webs on the upper side forming the first spacers 4 are arranged congruently with the webs on the lower side forming the second spacers 5 .
  • the angular distance ⁇ between the three webs forming the first spacers 4 is 120° in each case here.
  • the angular spacing ⁇ of the three webs forming the second spacers 5 is also 120° here.
  • the angular distance ⁇ between each two spacers 4, 5 corresponds here to twice the grid angle distance ⁇ of the different relative rotational positions of the plate 30 to the central shaft 10, in which the two can be brought into engagement with one another by means of the engagement contour 21 and the counter-contour 31.
  • the gap dimension h 1 corresponds to the height of the individual through the spacers 4, 5, which are identical to one another here.
  • the two plates 30 are arranged in a relative rotational position to one another in the plate stack 3, in which the first spacers 4 of one plate 30, here the lower plate, are congruent with the second spacers 5 of the other, here the upper plate 30, then the two adjacent plates 30 have a larger axial distance with a gap dimension h 2 of the intermediate flow gap 34.
  • the gap dimension h 2 here corresponds to the added height of the superimposed spacers 4 and 5 formed by the webs.
  • the rotor 1 agrees with the Figures 12 to 15 with the embodiment according to the Figures 8 to 11 match, so reference is made to their description.
  • the Figures 16 to 20 show plate 30 and the rotor 1 in a further embodiment.
  • the first and second spacers 4, 5 are formed by webs which are attached or formed on the plates 30 and form elevations.
  • the webs forming the first spacer 4, here three pieces, are arranged on the upper side on the plate 30 and the webs forming the second spacer 5, also three pieces, are arranged on the underside on the plate 30.
  • the webs on the upper side forming the first spacers 4 are arranged congruently with the webs on the lower side forming the second spacers 5 .
  • the angular distance ⁇ between the three webs forming the first spacers 4 is 120° in each case here.
  • the angular spacing ⁇ of the three webs forming the second spacers 5 is the same and is also 120° here.
  • the counter-contour 31 is changed.
  • two angular grids are provided which are superimposed and offset relative to one another in the circumferential direction by an offset angle ⁇ .
  • the two angle grids each have a uniform matching grid angle distance ⁇ , here 60°.
  • the screen angle distance ⁇ can also have a different value; however, it always corresponds to an integer fraction of 360°.
  • the offset angle ⁇ is less than half the screen angle distance a; here the offset angle ⁇ is 15°.
  • the spacers 4, 5 of two plates 30 adjacent to one another in the plate stack 3 can either be positioned congruently to one another axial distance between the two plates 30 with a larger gap h 2 between them, or positioned at two different distances from one another in the circumferential direction in non-congruent relation to one another in order to produce an axial distance between the two plates 30 with a smaller gap h 1 between them .
  • the circumferentially adjacent spacers 4, 5 of two axially adjacent plates 30 in the plate stack 3 are only separated by the offset angle ⁇ , ie by 15° in the example shown.
  • the circumferentially adjacent spacers 4, 5 of two axially adjacent plates 30 in the stack of plates 3 can also be spaced apart by the grid angle distance a, here 60°, or by an angle ⁇ - ⁇ , i.e. 45° here. Great flexibility in designing the stack of plates 3 is thus achieved here.
  • the two plates 30 are arranged in a relative rotated position in the stack of plates 3, in which the spacers 4, 5 of the two plates 30 are not congruent with one another, but rotated relative to one another out of alignment are, then these two adjacent plates 30 have a smaller axial distance with a gap dimension h 1 of the intermediate flow gap 34.
  • the two plates 30 are arranged in a relative rotational position to one another in the plate stack 3, in which the first spacers 4 of one plate 30, here the lower plate, are congruent with the second spacers 5 of the other, here upper plate 30, then the two adjacent plates 30 have a larger axial distance with a gap dimension h 2 of the intermediate flow gap 34.
  • the distance between the teeth of the engagement contour 21 in the circumferential direction of the shaft 2 is 60° in each case, ie it corresponds to the grid angle distance a explained above.
  • the distance between the teeth of the engagement contour 21 in the circumferential direction of the shaft 2 is 120° in each case, ie it corresponds to twice the grid angle distance a explained above.
  • the number of teeth forming the engagement contour 21 on the shaft 2 has no influence on the number of possible relative engagement positions of the central shaft 2 and plates 30 .
  • rotors 1 with plate stacks 30 can be formed with plates 30 that are completely identical to one another and central shafts 2 that are identical, the plates 30 of which have different axial distances from one another and which therefore provide different gap dimensions h for the flow gaps 34 .

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Centrifugal Separators (AREA)

Claims (17)

  1. Rotor (1) d'un séparateur centrifuge, ledit rotor (1) présentant un arbre (2) central sur lequel est agencée une pile de disques (3) composée de plusieurs disques (30) identiques, ledit arbre (2) présentant sur sa circonférence extérieure un contour de prise (21) pour entrer en prise de manière résistante à la torsion et déplaçable dans l'axe avec un contre-contour (31) sur la circonférence intérieure des disques (30) de la pile de disques (3), ledit contour de prise (21) et ledit contre-contour (31) pouvant être amenés en prise l'un avec l'autre dans plusieurs positions de rotation espacées l'une de l'autre dans le sens de la circonférence, et chaque disque (30) présentant des cales (4, 5) espacées l'une de l'autre dans le sens de la circonférence des disques et qui maintiennent respectivement deux disques (30) voisins à distance axiale l'un de l'autre, d'une taille de fente (h) prédéfinissable en formant une fente de flux (34) située entre les deux,
    caractérisé en ce
    que les cales (4, 5) des disques (30) sont conçues et agencées de sorte qu'à l'aide de différentes positions de torsion de disques (30) voisins l'un de l'autre, l'un par rapport à l'autre dans la pile de disques (3), au moins deux distances axiales peuvent être réglées à des mesures de fente différentes (h1, h2) de la fente de flux (34) entre les disques (30) voisins, et que les positions de torsion espacées les unes des autres dans le sens circonférentiel, dans lesquelles le contour de prise (21) et le contre-contour (31) peuvent être amenés en prise l'un avec l'autre, se trouvent dans deux trames angulaires superposées l'une à l'autre et décalées l'une par rapport à l'autre d'un angle de décalage (δ) dans le sens circonférentiel, les deux trames angulaires présentant chacune un écart angulaire de trame (α) uniforme et constant , ledit écart angulaire de trame (α) correspondant à une fraction entière de 360 ° et ledit angle de décalage (δ) étant inférieur à la moitié de l'écart angulaire de trame (a).
  2. Rotor selon la revendication 1, caractérisé en ce que chaque disque (30) présente des premières et des deuxièmes cales (4, 5), et que lesdites premières et deuxièmes cales (4, 5) se distinguent l'une de l'autre par leur hauteur et/ou par leur position radiale sur le disque (30).
  3. Rotor selon la revendication 2, caractérisé en ce que les premières et les deuxièmes cales (4, 5) sont constituées par deux bosses ou moulures distinctes réalisant une élévation sur l'un des côtés du disque et une dépression sur l'autre côté du disque, moulées ou estampées dans les disques (30).
  4. Rotor selon la revendication 3, caractérisé en ce que les cales (4, 5) espacées l'une de l'autre dans le sens circonférentiel du disque (30) sont réalisées en tant que bosses individuelles ou en tant que rangée de plusieurs bosses s'étirant dans le sens radial.
  5. Rotor selon la revendication 1, caractérisé en ce que chaque disque (30) présente des premières et des deuxièmes cales (4, 5), et que lesdites premières et deuxièmes cales (4, 5) sont constituées par des barrettes ou boucles formant des élévations, et appliquées ou formées sur les disques (30).
  6. Rotor selon la revendication 5, caractérisé en ce que les barrettes ou boucles constituant les premières cales (4) sont agencées sur la partie supérieure du disque (30), que les barrettes ou boucles constituant les deuxièmes cales (5) sont agencées sur la partie inférieure du disque (30) et que les barrettes ou boucles constituant les premières cales (4) sont décalées dans le sens circonférentiel du disque (30) par rapport aux barrettes ou boucles constituant les deuxièmes cales (5).
  7. Rotor selon la revendication 5, caractérisé en ce que les barrettes ou boucles constituant les premières cales (4) sont agencées sur la partie supérieure du disque (30), que les barrettes ou boucles constituant les deuxièmes cales (5) sont agencées sur la partie inférieure du disque (30), que les barrettes ou boucles constituant les premières cales (4) sont agencées de manière congruente par rapport aux barrettes ou boucles constituant les deuxièmes cales (5) et que l'écart angulaire (β) des cales (4, 5) espacées l'une de l'autre dans le sens circonférentiel des disques (30) correspond à deux fois l'écart angulaire de trame (α).
  8. Rotor selon l'une des revendications 5 à 7, caractérisé en ce que les barrettes ou boucles constituant les premières cales (4) et agencées sur la partie supérieure du disque (30), et les barrettes ou boucles constituant les deuxièmes cales (5) et agencées sur la partie inférieure du disque (30) sont identiques l'une à l'autre.
  9. Rotor selon l'une quelconque des revendications 1 à 8, caractérisé en ce qu'au sein de la pile de disques (3) d'une première réalisation de rotor, tous les disques (30) présentent l'un par rapport à l'autre un premier écart axial limité, d'une mesure de fente réduite (h1), et qu'au sein de la pile de disques (3) d'une deuxième réalisation du rotor avec disques (30) identiques à ceux de la première réalisation de rotor, tous les disques (30) présentent un deuxième écart axial l'un de l'autre plus important, d'une mesure de fente plus élevée (h2).
  10. Rotor selon l'une quelconque des revendications 1 à 8, caractérisé en ce que les disques (30) présentent, au sein de la pile de disques (3) du rotor (1), des écarts axiaux différents.
  11. Rotor selon la revendication 10, caractérisé en ce que les disques (30) au sein de la pile de disques (3) du rotor (1) présentent, dans une zone du rotor (1) proche du flux entrant, un écart axial réduit entr'eux, d'une mesure de fente réduite (h1), et dans une zone du rotor (1) éloignée du flux entrant, un écart axial supérieur entr'eux, avec une mesure de fente (h2) plus élevée.
  12. Rotor selon l'une quelconque des revendications 1 à 11, caractérisé en ce que le contour de prise (21) et le contre-contour (31) peuvent être amenés en prise l'un avec l'autre dans deux à seize, de préférence six à douze positions de torsion espacées l'une de l'autre dans le sens circonférentiel de l'arbre central (2) et des disques (30).
  13. Rotor selon l'une quelconque des revendications 1 à 12, caractérisé en ce que les disques (30) sont des pièces découpées par pression, en tôle métallique, ou des pièces moulées par injection en matière plastique.
  14. Rotor selon l'une quelconque des revendications 1 à 13, caractérisé en ce que le contour de prise (21) sur la circonférence extérieure de l'arbre (2) est constitué par un nombre n de dentures dans le sens longitudinal de l'arbre (2) et en saillie de manière radiale vers l'extérieur, et que le contre-contour (31) sur la circonférence intérieure du disque (30) est constitué par un nombre n ou 2 x n cavités correspondant aux dentures et dirigées dans le sens radial vers l'extérieur.
  15. Rotor selon la revendication 14, caractérisé en ce que le nombre n se situe entre 2 et 8, de préférence entre 3 et 6.
  16. Séparateur centrifuge, caractérisé en ce qu'il présente un rotor (1) selon l'une quelconque des revendications 1 à 15.
  17. Séparateur centrifuge selon la revendication 16, caractérisé en ce qu'il est un séparateur de brouillard d'huile pour le gaz de ventilation du carter d'un moteur à combustion interne.
EP19714111.2A 2018-03-12 2019-03-11 Rotor d'un séparateur centrifuge et séparateur centrifuge Active EP3765201B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102018105586.2A DE102018105586A1 (de) 2018-03-12 2018-03-12 Rotor eines Zentrifugalabscheiders und Zentrifugalabscheider
PCT/EP2019/055958 WO2019175077A1 (fr) 2018-03-12 2019-03-11 Rotor d'un séparateur centrifuge et séparateur centrifuge

Publications (2)

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EP3765201A1 EP3765201A1 (fr) 2021-01-20
EP3765201B1 true EP3765201B1 (fr) 2022-03-09

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US (1) US11453015B2 (fr)
EP (1) EP3765201B1 (fr)
CN (1) CN112203773B (fr)
DE (1) DE102018105586A1 (fr)
WO (1) WO2019175077A1 (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102019120023A1 (de) * 2019-07-24 2021-01-28 Hengst Se Separatorteller für einen Ölnebelabscheider und Ölnebelabscheider
EP3821984B1 (fr) * 2019-11-14 2022-06-29 Alfdex AB Empilement de disque, unité de rotor, séparateur centrifuge, procédé de fourniture d'empilement de disque et procédé de fourniture d'unité de rotor
CN114315081B (zh) * 2022-03-10 2022-06-17 定州市四丰环保科技有限公司 一种固液分离机的辊子和固液分离机
CN116181448B (zh) * 2022-10-27 2025-05-06 苏州恩都法汽车系统股份有限公司 一种堆叠体及离心式分离器
CN117181459B (zh) * 2023-11-06 2024-02-02 江苏赛德力制药机械制造有限公司 一种碟片数量可调的双锥碟片复合式卧螺沉降离心机

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Publication number Priority date Publication date Assignee Title
US779099A (en) * 1903-07-20 1905-01-03 Gustaf T Rennerfelt Centrifugal cream-separator.
SE316422B (fr) * 1964-04-14 1969-10-20 Ceskoslovenska Akademie Ved
JPS5775164A (en) * 1980-10-29 1982-05-11 Toshiba Corp Centrifugal clarifier
DE19705704C1 (de) * 1997-02-14 1998-07-02 Suedmo Schleicher Ag Teller für die Schleudertrommel einer Zentrifuge mit Distanzhaltern und Verfahren zur Herstellung
DE102004042888A1 (de) * 2004-09-04 2006-03-23 Westfalia Separator Ag Selbstentleerender Separator mit Tellerpaket
EP2015871B1 (fr) * 2006-05-11 2017-04-26 GEA Mechanical Equipment GmbH Séparateur à trois phases avec un disque d'épluchage et des ouvertures de sortie de matières solides
SE532500C2 (sv) * 2008-07-16 2010-02-09 Alfa Laval Corp Ab Centrifugal separator
SE532915C2 (sv) * 2008-09-30 2010-05-04 Alfa Laval Corp Ab Skivpaket för centrifugrotor
SE532914C2 (sv) 2008-09-30 2010-05-04 Alfa Laval Corp Ab Skivpaket för en centrifugrotor
SE532912C2 (sv) 2008-09-30 2010-05-04 Alfa Laval Corp Ab Separeringsskiva för en centrifugrotor samt skivpaket
SE536671C2 (sv) * 2012-04-23 2014-05-13 3Nine Ab Koniska skivelement till en rotor för centrifugalseparatorerjämte rotorer innehållande sådana skivelement
EP2664385B1 (fr) * 2012-05-14 2017-03-01 Alfa Laval Corporate AB Pile de disques pour un séparateur centrifuge
EP3124120B1 (fr) * 2014-03-27 2020-02-26 Tokyo Roki Co., Ltd. Séparateur d'huile
DE102015119616A1 (de) 2015-11-13 2017-05-18 Hengst Se & Co. Kg Rotor eines Zentrifugalabscheiders

Also Published As

Publication number Publication date
CN112203773B (zh) 2022-05-17
EP3765201A1 (fr) 2021-01-20
DE102018105586A1 (de) 2019-09-12
US11453015B2 (en) 2022-09-27
CN112203773A (zh) 2021-01-08
WO2019175077A1 (fr) 2019-09-19
US20210046490A1 (en) 2021-02-18

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