EP2672123A1 - Roue cellulaire, en particulier pour un système de suralimentation à ondes de pression - Google Patents

Roue cellulaire, en particulier pour un système de suralimentation à ondes de pression Download PDF

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Publication number
EP2672123A1
EP2672123A1 EP12171157.6A EP12171157A EP2672123A1 EP 2672123 A1 EP2672123 A1 EP 2672123A1 EP 12171157 A EP12171157 A EP 12171157A EP 2672123 A1 EP2672123 A1 EP 2672123A1
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EP
European Patent Office
Prior art keywords
sleeve
cellular wheel
sealing
sleeves
end faces
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
EP12171157.6A
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German (de)
English (en)
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EP2672123B1 (fr
Inventor
Karl Merz
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.)
MEC LASERTEC AG
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MEC LASERTEC AG
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 MEC LASERTEC AG filed Critical MEC LASERTEC AG
Priority to EP12171157.6A priority Critical patent/EP2672123B1/fr
Priority to HUE12171157A priority patent/HUE034654T2/en
Priority to ES12171157.6T priority patent/ES2647277T3/es
Priority to US13/903,586 priority patent/US9562435B2/en
Priority to JP2013111750A priority patent/JP6154664B2/ja
Publication of EP2672123A1 publication Critical patent/EP2672123A1/fr
Application granted granted Critical
Publication of EP2672123B1 publication Critical patent/EP2672123B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B33/00—Engines characterised by provision of pumps for charging or scavenging
    • F02B33/32—Engines with pumps other than of reciprocating-piston type
    • F02B33/42—Engines with pumps other than of reciprocating-piston type with driven apparatus for immediate conversion of combustion gas pressure into pressure of fresh charge, e.g. with cell-type pressure exchangers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04F—PUMPING OF FLUID BY DIRECT CONTACT OF ANOTHER FLUID OR BY USING INERTIA OF FLUID TO BE PUMPED; SIPHONS
    • F04F13/00—Pressure exchangers

Definitions

  • the present invention relates to a cellular wheel made of metal, with an outer sleeve lying coaxially to a rotation axis, an inner sleeve coaxial with the outer sleeve, at least one between the outer sleeve and inner sleeve coaxial with these intermediate sleeve arranged between successive sleeves, radially aligned with the axis of rotation, with adjacent sleeves joined lamellae, with the outer sleeve cross-over and with the outer sleeve joined outer sealing sleeves with a sealing profile for a labyrinth seal, and with a lying in the axis of rotation drive shaft.
  • downsizing is the substitution of a large-volume engine with a displacement-reduced engine.
  • the engine power should be kept high by charging the engine.
  • the goal is to achieve the same performance with small-volume engines as with large-volume engines, as with naturally aspirated engines of the same performance.
  • Recent findings in the field of downsizing have shown that the best results can be achieved, especially with very small gasoline engines with a displacement of 2 liters or less with a pressure wave charging system.
  • the rotor In a pressure wave supercharger, the rotor is designed as a cellular wheel and is enclosed by an air and exhaust housing with a common jacket.
  • the development of modern pressure wave chargers for charging small engines leads to cell wheels with a diameter of the order of 100 mm or less.
  • cell wall thicknesses of 0.4 mm or less are desired.
  • At the high exhaust gas inlet temperatures of about 1000 ° C come as materials for the feeder virtually only high-temperature alloys in question.
  • the production of dimensionally stable and high-precision cellular wheels with a small cell wall thickness is today hardly possible or associated with considerable additional costs.
  • a cellular wheel of the type mentioned is in WO 2010/057319 Al disclosed.
  • the temperature changes occurring in rapid succession in the interior of the cell wheel in the region of the end faces of the cell wheel lead to periodically strongly fluctuating thermal expansions and contractions of the disks in the radial direction with temperature differences of 200 to 300 ° C.
  • arranged between successive sleeves and joined to the sleeves slats are exposed to high load changes with a vibration frequency in the order of twice the speed of the cell wheel, which under continuous thermal stress to cracking near the joints between Slats and sleeves can lead to the end faces of the cellular wheel and in consequence to the breaking out of fin parts and the failure of the cell wheel.
  • the invention is based on the object, simple and inexpensive to manufacture a cellular wheel of the type mentioned while avoiding cracking in the joining region between fins and sleeves with the required precision.
  • Another object of the invention is to provide a suitable for use in a pressure wave supercharger for supercharging internal combustion engines, in particular for supercharging small gasoline engines with a displacement in the order of 2 liters or less, suitable cellular wheel.
  • mechanically stable cell wheels with a cell wall thickness of 0.5 mm or less should be able to be produced under operating conditions without a tendency to crack formation in the joining region between lamellae and sleeves.
  • At least the outer sleeve, the inner sleeve and / or the intermediate sleeve or, in the case of more than one intermediate sleeve, at least one of the intermediate sleeves has cut-outs extending from both end faces of the cellular wheel between adjacent lamellae.
  • the incisions are preferably rotationally symmetrical.
  • the outer sleeve and the inner sleeve are formed without cuts.
  • an incision is present on the left and right of a lamella, or there is preferably always an incision between two adjacent lamellae.
  • the incisions arranged in the intermediate sleeve thereby provide an edge strip for the corresponding lamella which is designed to be elastically movable with respect to the intermediate sleeve and other edge strips and advantageously compensates for the deformation of the lamellae resulting from temperature fluctuations by a movement of the edge strip in a substantially radial direction.
  • the edge strips can also be referred to as tabs.
  • two adjacent incisions form one of the corresponding sleeve associated edge strips, wherein a single edge strip is assigned in each case a single lamella.
  • Such an edge strip is elastically movable relative to the corresponding sleeve and to adjacent edge strips.
  • the incisions are preferably distributed uniformly over the circumference of the relevant sleeve. Another distribution depending on the arrangement of the slats is also conceivable.
  • cuts are present between all adjacent lamellae.
  • an incision may be provided after every second or third lamella.
  • the sleeve in question in the edge region of the feeder is thus divided into edge strips, so that adjacent edge strips in the radial direction are mutually displaceable.
  • the lamellae, together with the edge strips joined with the lamellae can expand and contract in the radial direction from their original position in the sleeve, so that the thermal expansions and contractions of the lamellae occurring in rapid succession in the radial direction result in less stress build-up and degradation
  • fast load changes in the slats in the area of their joints with the outer, inner and / or intermediate sleeves and with this measure material damage can be avoided.
  • the recess can have a round or elliptical cross-section perpendicular to the central axis in plan view.
  • the extent of the recess is preferably in the range 1 to 2 mm.
  • the inner sleeve is seated on a coaxially arranged to this, joined to the drive shaft flange sleeve and the outer sleeve has from both end faces of the cellular wheel outgoing incisions between adjacent lamellae.
  • a remote from the end faces of the cellular wheel peripheral edge of the outer sealing sleeves extends beyond the cuts by a measure and the outer sealing sleeves are joined only in the incision projecting area with the outer sleeve.
  • the sealing profile of the outer sealing sleeves has a sealing surface aligned with the end faces of the cellular wheel, and the outer sealing sleeves form, with the outer sleeve, an annular gap open at the end faces of the cellular wheel.
  • the inner sleeve of both end faces of the cell wheel outgoing incisions between adjacent lamellae is hereby joined with the flange sleeve between adjacent lamellae between opposed incisions.
  • the inner sleeve is joined to the drive shaft and the intermediate sleeve or, in the case of two or more intermediate sleeves, at least one of the intermediate sleeves has incisions extending between both end faces of the cellular wheel between adjacent lamellae.
  • the sealing profile of the outer sealing sleeves on a flush with the end faces of the cellular wheel sealing surface and in the inner sleeve are fitted with the inner sleeve inner sealing sleeves arranged with a sealing profile with an aligned with the end faces of the cell wheel sealing surface for a labyrinth seal.
  • the sealing sleeves are joined only in the region of the remote from the end faces of the cellular wheel end with the outer and inner sleeve and form with the outer and inner sleeves open at the end faces of the cellular wheel annular gap.
  • the sealing surface of the sealing profile and the annular gap adjacent to the sealing surface between the sealing sleeve and outer or inner sleeve are decisive for the tightness of a labyrinth seal between the end faces of the cell wheel and the control surfaces of the gas and air housings facing one another in a pressure wave loader.
  • the pressure waves acting periodically on the end faces of the cellular wheel also lead to high gas pressures in the area of the labyrinth seals.
  • the annular gap adjoining the sealing surface of the sealing profile prevents, with a slight local pressure reduction when the gas flows into the annular gap, an escape of gas through the gap formed between the sealing surface and the opposing control surface and thus a pressure loss which reduces the power of the pressure wave supercharger.
  • spacer elements arranged distributed over the circumference of the sealing sleeves can protrude from the side of the sealing sleeves facing the outer or inner sleeve in the region of the end faces of the cellular wheel.
  • the spacer elements can be distributed over the circumference of the outer or inner sleeve on the side facing the sealing sleeve side of the outer or inner sleeve.
  • the above-described embodiment of the sealing sleeves with the outer and inner sleeves forming an annular gap at the end faces of the cellular wheel also leads to smaller centrifugal forces and thus to a higher dimensional stability of the cellular wheel with a correspondingly improved seal.
  • the length of the incisions in the outer sleeve, the inner sleeve or the intermediate sleeve or in more than one intermediate sleeve in at least one of the intermediate sleeves is in the range of about 10% to 30% of the length of the cellular wheel, i. the distance between the two end faces of the cellular wheel.
  • the outer sleeve, the inner sleeve, the intermediate sleeve / s, the fins and the sealing sleeves are made of sheet metal with a thickness of less than 0.5 mm.
  • the drive shaft has two coaxial with the drive shaft and arranged spaced-apart annular webs with a peripheral surface as bearing surfaces for the inner sleeve and at least one of the annular webs is joined to the inner sleeve.
  • the remote from the end faces of the cellular wheel end of the inner sealing sleeves is joined to one of the annular webs.
  • the inner sealing sleeve on the hot gas side i. be joined on the side of the exhaust housing, at the end face of the cellular wheel with a lid.
  • the hot gas side near ring web can be joined with a lid.
  • the drive axle can be kept at a relatively low temperature under operating conditions of a pressure wave supercharger, so that the axial play of the enclosed between gas and air housing cellular wheel to maintain a minimum clearance of about 0.03 to 0.05 mm over the entire speed range can be set smaller in the cold operating state.
  • the drive shaft is designed as a hollow shaft with a tubular end part, a conical intermediate part and a tubular shaft part with a receptacle for a to be connected to a motor drive coupling.
  • tubular end part and the conical intermediate part expediently have openings arranged symmetrically over the circumference, which also allow an air circulation corresponding cooling effect.
  • the coupling piece preferably has a coupling axis with longitudinal ribs, which engage in insertion of the coupling piece into the receptacle of the tubular shaft part in longitudinal grooves in the receptacle.
  • the inventive cellular wheel is preferably used in a pressure wave supercharger for supercharging internal combustion engines, in particular gasoline engines with a displacement of preferably 2 liters or less.
  • cellular wheel 10 of a pressure wave supercharger not shown in the drawing consists of a concentric with a rotation axis y of the cellular wheel 10 outer sleeve 12, a concentric with the outer sleeve 12 inner sleeve 14 and a between the outer sleeve 12 and the inner sleeve 14 concentrically arranged to these intermediate sleeve 18th
  • the outer annular space between the intermediate sleeve 18 and the outer sleeve 12 and the inner annular space between the intermediate sleeve 18 and the inner sleeve 14 are divided by radially arranged to the rotation axis y strip-shaped fins 16 into a plurality outer cells 20 and a plurality of inner cells 22.
  • the outer sleeve 12, the intermediate sleeve 18, the inner sleeve 14 and the fins 16 have a uniform Wall thickness of z. B. 0.4 mm and consist of a highly heat-resistant metallic material, for. Inconel 2.4856.
  • the said parts have in the direction of the rotation axis y an equal length L corresponding to the length of the cellular wheel 10 and extend between two perpendicular to the axis of rotation y end faces 11 of the cellular wheel 10.
  • Fig. 1 and 4 illustrated cellular wheel 10 is according to the FIGS. 2 and 3 connected by a flange sleeve 15 with a drive shaft 13.
  • the flange sleeve 15 is aligned concentrically with the drive shaft 13 and welded thereto.
  • the axis of rotation of the drive shaft 13 corresponds to the axis of rotation y of the placed on the flange sleeve 15 cellular 10th
  • 12 incisions 26 are arranged in the outer sleeve 12 between joints 17 of adjacent lamellae 16 with the outer sleeve. These cuts 26 extend parallel to the slats 16 and extend from each end face 11 of the cellular wheel 10 over a length e of z. B. 15 mm. The cuts 26 terminate in a circular recess 28 with a diameter f of z. B. 2 mm. In addition, the at least one intermediate sleeve 16 could also be provided with corresponding cuts.
  • the arrangement of the outer sealing sleeves 24 is made of the 4 and 6 seen.
  • the outer sealing sleeve 24 has a length g of z. B. 20 mm.
  • the outer sealing sleeve 24 is in a perpendicular to the axis of rotation y outwardly projecting, the sealing profile 30 forming annular flange with the aligned with the end face 11 of the cellular wheel 10 sealing surface 32 having a width h of z. B. 1.5 mm over.
  • the outer sealing sleeve 24 is seated substantially form-fitting manner on the outer sleeve 12 and projects with a free peripheral edge 25, the circular recesses 28 at the ends of the incisions 26 by a dimension m of eg 5 mm and is via two circumferential welds 34, 36 joined to the outer sleeve 12.
  • incisions 26 are arranged in the inner sleeve 14 between joints 17 of adjacent fins 16 with the inner sleeve 14. These cuts 26 extend parallel to the slats 16 and extend from each end face 11 of the cellular wheel 10 over a length e of z. B. 15 mm. The cuts 26 terminate in a circular recess 28 with a diameter f of z. B. 2 mm.
  • optional cuts 26 can be arranged in the at least one intermediate sleeve.
  • the fins 16 are usually rectangular strips of constant thickness. Since the highest mechanical stresses and thus an increased cracking tendency occur in the vicinity of the joining zone, the lamellae may have a material thickening 19 in the region of their longitudinal edges ( FIGS. 7 and 8 ).
  • the area of the lamellae 16 delimited by the two parallel longitudinal edges can be flat or, as viewed in the direction of the longitudinal axis of the lamellae 16, curved to increase its dimensional stability on one or both sides or be provided with a bead.
  • the inner sleeve 14 whose inner diameter and length is matched to the outer diameter and the length of the flange 15, with the previously with the inner sleeve 14 with a longitudinal edge positionally joined and projecting radially outwardly with the free longitudinal edge fins 16 of both end faces 11 forth with the incisions 26 and at the ends thereof provided with the circular recesses 28. Subsequently, the thus processed inner sleeve 14 is placed with the radially outwardly projecting fins 16 in the axial direction y coaxially on the flange sleeve 15 and welded thereto by means of an NC-controlled laser beam between the fins 16 in the region between the opposing recesses 28.
  • the weld can be continuous from recess to recess or only extend over a length of 3 to 5 mm after each recess 28.
  • To achieve optimum tightness can also be in a short distance of z. B. 2 to 3 mm to the recess 28 a transverse to the adjacent Slats 16 extending transverse weld seam are set.
  • the transverse weld seam at their ends by parallel to the slats 16 extending longitudinal welds of z. B. 3 to 5 mm are added to a U-shaped weld.
  • the intermediate sleeve 18 whose inner diameter and length is matched to the formed by the free longitudinal edges of the inner sleeve 14 radially outwardly projecting fins 16 outer diameter and the length of the inner sleeve 14, with the previously with the intermediate sleeve 18 with a Longitudinal edge positioned exactly joined and with the free longitudinal edge radially outwardly projecting slats 16 in the axial direction y coaxial and accurate position on the free longitudinal edges of the inner sleeve 14 radially outwardly projecting slats 16 set.
  • the intermediate sleeve 18 is welded by means of a laser beam by means of a blind seam with the free end edges of the underlying fins 16 of the inner sleeve 14 to form the inner cells 22.
  • the outer sleeve 12 whose inner diameter and length is matched to the outer diameter formed by the free longitudinal edges of the radially outwardly projecting from the intermediate sleeve 18 lamella 16 and the length of the intermediate sleeve 18, in the axial direction y coaxial with the free longitudinal edges of set of the inner sleeve 14 radially outwardly projecting fins 16.
  • the outer sleeve 12 is welded by means of a blind seam with the free end edges of the underlying fins 16 of the intermediate sleeve 18 to form the outer cells 20.
  • the outer sleeve 12 is provided by both end faces 11 ago with the incisions 26 and at the ends thereof with the circular recesses 28.
  • the outer sealing sleeves 24 are placed on the outer sleeve 12 and connected thereto.
  • the above-described joints are preferably designed as welding seams produced by means of a laser or electron beam, in particular with a laser beam. However, the joints can also be soldered.
  • the cutting of the cuts 26 and the recesses 28 is also preferably carried out by means of a laser or electron beam, in particular with a laser beam.
  • cellular wheel 10 of a pressure wave supercharger consists of a concentric with a rotation axis y of the cellular wheel 10 outer sleeve 12, a concentric with the outer sleeve 12 inner sleeve 14 and a between the outer sleeve 12 and the inner sleeve 14 concentrically arranged to these intermediate sleeve 18th
  • the outer annular space between the intermediate sleeve 18 and the outer sleeve 12 and the inner annular space between the intermediate sleeve 18 and the inner sleeve 14 are divided by radially arranged to the rotation axis y strip-shaped fins 16 into a plurality outer cells 20 and a plurality of inner cells 22.
  • the outer sleeve 12, the intermediate sleeve 18, the inner sleeve 14 and the fins 16 have a uniform wall thickness of z. B. 0.4 mm and consist of a highly heat-resistant metallic material, for. Inconel 2.4856.
  • the said parts have in the direction of the rotation axis y an equal length L corresponding to the length of the cellular wheel 10 and extend between two perpendicular to the axis of rotation y end faces 11 of the cellular wheel 10.
  • cellular wheel 10 is the inner sleeve 14 according to Fig. 10 directly connected to a drive shaft 13.
  • the drive shaft 13 is arranged as a hollow shaft with two spaced-apart from a tubular end portion 46 radially protruding ring lands 38, 40 configured. End surfaces 42, 44 of the annular webs 38, 40 are concentric with the drive shaft 13 aligned inner sleeve 14, wherein only the drive side further away annular web 38 with the inner sleeve 14 z. B. is joined by means of a circumferential laser weld seam.
  • the axis of rotation of the drive shaft 13 corresponds to the axis of rotation y of the inner sleeve 14 or of the cell wheel 10 placed on the drive shaft 13.
  • the tubular end part 46 of the drive shaft 13 is adjoined by a conical intermediate part 48, which merges into a substantially tubular shaft part 50 with a receptacle 52 for a coupling piece 54 to be connected to a motor drive.
  • the coupling piece 54 has a coupling axis 56 with longitudinal ribs 58 which engage upon insertion of the coupling piece 54 into the receptacle 52 of the tubular shaft part 50 in corresponding longitudinal grooves 60 in the receptacle 52 ( Fig. 11 ).
  • Fig. 10 are provided in the tubular end portion 46 of the drive shaft 13 between the two ring lands 38, 40 symmetrically about the circumference arranged first openings 62.
  • second openings 64 are also provided symmetrically over the conical peripheral surface. The openings 62, 64 serve to reduce weight and also have an air circulation with appropriate cooling effect.
  • FIGS. 15 and 16 show a further embodiment of the cellular wheel 10.
  • the cellular wheel 10 for example, on the drive shaft 13 after FIG. 2 or after FIG. 10 be used.
  • 18 incisions 26 are arranged in the intermediate sleeve 18 between joints 17 adjacent lamellae 16 with the intermediate sleeve.
  • this is the one embodiment in which the incisions 26 are arranged exclusively in the intermediate sleeve 18 and the outer sleeve 12 and the inner sleeve 14 have no cuts.
  • the following description can also be applied to the embodiment described above with the incisions in the outer sleeve 12 and / or intermediate sleeve 18 and / or inner sleeve 14.
  • These cuts 26 in the intermediate sleeve 18 are parallel to the slats 16 and extend starting from each end face 11 of the cellular wheel 10 and the intermediate sleeve 18 over a length of z. B. 15 mm.
  • the incisions 26 end in a circular recess 28 with a diameter of z. B. 2 mm.
  • FIGS. 18 and 19 schematically show a section in the direction of the rotation axis y seen.
  • Fig. 19 represents the state of the FIGS. 15 and 16 in which the fins 16 and also parts of the intermediate sleeve 18 are deformed due to the temperature changes described below.
  • Fig. 18 shows an operating state in which the cellular wheel 10 is in the axial direction over its entire length at a substantially constant operating temperature. Under these conditions, there is thus no difference in the thermal expansion of the lamellae 16 in the radial direction over the entire length of the cellular wheel 10.
  • Fig. 15, 16 and 19 show an operating state in which the fins 16 in a one of an end face 11 of the cellular wheel 10 to a depth of about 15 to 20 mm extending edge region of the cellular wheel 10 by 200 to 300 ° C higher temperature than in an inner region of the cell wheel 10. Under these conditions, the higher temperature of the fins 16 in the edge region in comparison to the fins in the interior of the cellular wheel 10 leads to a greater thermal expansion.
  • the intermediate sleeve 18 in the edge region of the cellular wheel 10 in edge strips 18 a, 18 b divided so that adjacent edge strips 18 a, 18 b in the radial direction are mutually displaceable.
  • the in the Fig. 15, 16 and 19 shown operating state results from the rapid periodic temperature increases on the hot gas side of the cellular wheel 10.
  • the arrangement of the incisions 26 thus a deformation of the fins 16 in the radial direction allows, which largely prevents the stresses in the region of the fins 16.
  • the lamella 16a is assigned to an edge strip 18a of the intermediate sleeve 18 formed by incisions 26 provided on the left and right of the lamella 16a.
  • an edge strip 18 a protruding from the base body of the intermediate sleeve 18 is formed by the notches 26.
  • the lamella 16a is firmly connected to the edge strip 18a via the joint 17. With an increase in temperature, the blade deformed 16a in the radial direction in the front region over the edge strip 18 a and this deformation can be compensated by a movement of the edge strip 18 a in the direction of the rotation axis y. In the lamella 16a itself there is no voltage or a greatly reduced voltage.
  • the lamella 16b is in this case connected to an edge strip 18b, with deformation of the lamella 16b of the corresponding edge strip 18b deformed.
  • the edge strip 18 b is provided by two left and right of the blade 16 b extending into the intermediate sleeve 18 cuts 26.
  • Each slat 16 a, 16 b can thus together with the edge strip 18 a, 18 b contracted from its original position in the intermediate sleeve 18 in the radial direction, without causing temperature-induced, rapid load changes in rapid succession compressive stresses in the slats 16th in the region of their joints 17 with the outer and inner sleeves 12, 14 and dismantle and can lead to material damage.
  • the arrangement of the outer sealing sleeves 24 is made of the Fig. 12, 14th and 15 seen.
  • the cylindrical outer sealing sleeves 24 have a width of z. B. 20 mm.
  • At both end faces 11 of the cellular wheel 10 have in the FIGS. 20 to 22 illustrated outer sealing sleeves 24 a radially outwardly projecting sealing profile 30 with an aligned with the end face 11 of the cellular wheel 10 sealing surface 32 having a width d3 of z. B. 1.5 mm for a labyrinth seal.
  • the outer sealing sleeve 24 is seated in a substantially remote from the end face 11 of the cellular wheel 10 area on the outer sleeve 12 and is joined in this area via a circumferential weld 34 with the outer sleeve 12.
  • the outer sealing sleeve 24 with a wall thickness d1 of eg 0.25 mm has a thickness-reduced area 23 with a thickness d2 of, for example, 0.13 mm and thus a radial distance to the outer sleeve 12, so that from the end faces 11 of the cellular wheel 10 to the joining region of the outer sealing sleeve 24 with the outer sleeve 12 between the sealing sleeve 24 and outer sleeve 12, an open at the end faces 11 of the cellular wheel 10 annular gap 66 results.
  • the sealing sleeve 24 below the sealing profile 30 radially inwardly projecting lugs as a spacer 68 with a height d4 of, for example, 0.13 mm.
  • spacer 68 six spacers 68 are arranged distributed uniformly over the circumference of the sealing profile 30 of the sealing sleeve 24.
  • first inner sealing sleeve 70 is shown in the inner sleeve 14 in the FIGS. 23 to 25 shown first inner sealing sleeve 70 and a in the FIGS. 26 to 28 illustrated second inner sealing sleeve 72 is inserted.
  • the first inner sealing sleeve 70 is arranged on the hot gas side, the second inner sealing sleeve 72 on the cold gas side of the cellular wheel 10.
  • the inner sealing sleeves 70, 72 have a radially inwardly projecting sealing profile 74 in the form of an annular web with an aligned with the end face 11 of the cell wheel sealing surface 75 with a width of z. B. 1.5 mm. In an area extending from the end faces 11 of the cellular wheel 10 in the inner sleeve 14 of z. B.
  • the inner sealing sleeves 70, 72 have a reduced thickness region 73 and thus a radial distance from the inner sleeve 14 so that starting from the end faces 11 of the cellular wheel 10, starting between inner sealing sleeve 70, 72 and inner sleeve 14 at the end faces 11 of the cellular wheel 10 open annular gap 66 results.
  • the inner sealing sleeves 70, 72 of the inner sleeve 14 are substantially form-fitting, extending to the respective closer annular web 38, 40 at the tubular end portion 46 of the drive shaft 13 and are connected to the corresponding annular web 38, 40 by means of a circumferential weld seam joined.
  • the annular webs 38, 40 on the tubular end portion 46 of the drive shaft 13 are joined to the inner sleeve 14 by means of a circumferential weld.
  • the sealing profile 74 is welded on the drive side of the farther end face 11 of the cellular wheel 10, ie on the hot gas side, with an inner sleeve 14 closing outer cover 78.
  • the annular web 38 further away from the drive side is welded to the tubular end part 46 of the drive shaft 13 with an inner cover 80 closing the inner sleeve 14 in the interior of the cellular wheel 10.
  • inner sealing sleeves 70, 72 To stabilize the mutual position of inner sealing sleeve 70, 72 and inner sleeve 14, the inner sealing sleeves 70, 72 on the outside over the sealing profile 74 radially outwardly projecting lugs as spacers 68 to the inner sleeve 14.
  • spacers 68 are arranged uniformly distributed over the circumference of the inner sealing sleeve 70, 72.
  • outer sealing sleeves 24 indicated values for the dimensions d1, d2, d3 and d4 also apply to those in the Fig. 23 to 28 shown inner sealing sleeves 70, 72nd
  • the wall thickness a1 of the outer sleeve 12 is for example 0.25 mm and the thickness a2 of the thickness-reduced portion 23, for example, 0.13 mm.
  • the annular gap width between inner sealing sleeves 70, 72 and the inner sleeve 14 can be increased by reducing the inner diameter of the inner sleeve 14 while the outer diameter remains the same, with the protrusions for the outer sleeve 12 for a1 and a2 also applying to the inner sleeve 14.
  • the inner sleeve 14 is provided with the slats 16, which are positioned precisely with a longitudinal edge and project radially outwardly with the free longitudinal edge.
  • the intermediate sleeve 18 is then welded by means of a blind seam with the free end edges of the underlying slats 16 of the inner sleeve 14 to form the inner cells 22. Subsequently, the intermediate sleeve 18 is provided from both end faces 11 forth with the incisions 26 and at the ends thereof with the circular recesses 28.
  • the outer sleeve 12 whose inner diameter and length is matched to the outer diameter formed by the free longitudinal edges of the radially outwardly projecting from the intermediate sleeve 18 lamella 16 and the length of the intermediate sleeve 18, in the axial direction y coaxial with the free longitudinal edges of of the Intermediate sleeve 14 set radially outwardly projecting fins 16.
  • the outer sleeve 12 is welded by means of a blind seam with a laser beam with the free end edges of the underlying slats 16 of the intermediate sleeve 18 to form the outer cells 20.
  • the outer sealing sleeves 24, whose inner diameter is matched to the outer diameter of the outer sleeve 12, are coaxially placed in the axial direction y on the outer sleeve 12 and joined with this.
  • the inner sealing sleeves 70, 72, whose outer diameter is matched to the inner diameter of the inner sleeve 14, coaxially inserted in the axial direction y on the inner sleeve 14 and joined with this and with the annular webs 38, 40 at the tubular end portion 46 of the drive shaft 13.
  • the inner and the outer cover 80, 78 are inserted and joined with the annular web 38 on the tubular end portion 46 and with the annular web 74 on the hot gas side sealing sleeve 70.
  • the above-described joints are preferably designed as welding seams produced by means of a laser or electron beam, in particular with a laser beam. However, the joints can also be soldered.
  • the cutting of the cuts 26 and the recesses 28 is also preferably carried out by means of a laser or electron beam, in particular with a laser beam, wherein a minimum cutting width of about 15 microns is achieved.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Supercharger (AREA)
  • Sealing Using Fluids, Sealing Without Contact, And Removal Of Oil (AREA)
EP12171157.6A 2012-06-07 2012-06-07 Roue cellulaire, en particulier pour un système de suralimentation à ondes de pression Active EP2672123B1 (fr)

Priority Applications (5)

Application Number Priority Date Filing Date Title
EP12171157.6A EP2672123B1 (fr) 2012-06-07 2012-06-07 Roue cellulaire, en particulier pour un système de suralimentation à ondes de pression
HUE12171157A HUE034654T2 (en) 2012-06-07 2012-06-07 Cellular wheel, mainly for pressure waves
ES12171157.6T ES2647277T3 (es) 2012-06-07 2012-06-07 Rueda celular, en particular para un sobrealimentador por ondas de presión
US13/903,586 US9562435B2 (en) 2012-06-07 2013-05-28 Cellular wheel, in particular for a pressure wave supercharger
JP2013111750A JP6154664B2 (ja) 2012-06-07 2013-05-28 特に圧力波過給機用のセル式ホイール

Applications Claiming Priority (1)

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EP12171157.6A EP2672123B1 (fr) 2012-06-07 2012-06-07 Roue cellulaire, en particulier pour un système de suralimentation à ondes de pression

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EP2672123A1 true EP2672123A1 (fr) 2013-12-11
EP2672123B1 EP2672123B1 (fr) 2017-08-16

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DE102009023217B4 (de) * 2009-05-29 2014-08-28 Benteler Automobiltechnik Gmbh Gebaute Nabe für einen Druckwellenlader
EP2450121A1 (fr) * 2010-11-03 2012-05-09 MEC Lasertec AG Procédé de fabrication d'une roue cellulaire
CN108024725B (zh) 2015-09-21 2022-07-12 Zoll医疗公司 以胸部顺应性为指导的胸外按压
CN109899485B (zh) * 2019-04-22 2024-05-31 海盐琦安瑞精密机械有限公司 一种防滑效果好的汽车传动用涨紧轮

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US3545882A (en) * 1968-01-17 1970-12-08 Rolls Royce Pressure exchanger rotor
WO2010057319A1 (fr) 2008-11-21 2010-05-27 Mec Lasertec Ag Procédé de production d'une roue cellulaire
EP2253853A1 (fr) * 2009-05-19 2010-11-24 MEC Lasertec AG Roue cellulaire et son procédé de fabrication
EP2450121A1 (fr) * 2010-11-03 2012-05-09 MEC Lasertec AG Procédé de fabrication d'une roue cellulaire

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GB1004212A (en) * 1963-04-10 1965-09-15 Power Jets Res & Dev Ltd Improvements in or relating to pressure exchanger cell rings
US3545882A (en) * 1968-01-17 1970-12-08 Rolls Royce Pressure exchanger rotor
WO2010057319A1 (fr) 2008-11-21 2010-05-27 Mec Lasertec Ag Procédé de production d'une roue cellulaire
EP2253853A1 (fr) * 2009-05-19 2010-11-24 MEC Lasertec AG Roue cellulaire et son procédé de fabrication
EP2450121A1 (fr) * 2010-11-03 2012-05-09 MEC Lasertec AG Procédé de fabrication d'une roue cellulaire

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ES2647277T3 (es) 2017-12-20
HUE034654T2 (en) 2018-02-28
EP2672123B1 (fr) 2017-08-16
JP6154664B2 (ja) 2017-06-28
JP2013253596A (ja) 2013-12-19
US20130330200A1 (en) 2013-12-12
US9562435B2 (en) 2017-02-07

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