EP2222960B1 - Blower spiral volute with a discharge tongue that separates two axially offset discharge areas - Google Patents
Blower spiral volute with a discharge tongue that separates two axially offset discharge areas Download PDFInfo
- Publication number
- EP2222960B1 EP2222960B1 EP08852563.9A EP08852563A EP2222960B1 EP 2222960 B1 EP2222960 B1 EP 2222960B1 EP 08852563 A EP08852563 A EP 08852563A EP 2222960 B1 EP2222960 B1 EP 2222960B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- spiral
- impeller
- inflow chamber
- blower arrangement
- inflow
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Not-in-force
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/40—Casings; Connections of working fluid
- F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
- F04D29/4206—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
- F04D17/08—Centrifugal pumps
- F04D17/16—Centrifugal pumps for displacing without appreciable compression
- F04D17/165—Axial entry and discharge
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/08—Sealings
- F04D29/16—Sealings between pressure and suction sides
- F04D29/161—Sealings between pressure and suction sides especially adapted for elastic fluid pumps
- F04D29/162—Sealings between pressure and suction sides especially adapted for elastic fluid pumps of a centrifugal flow wheel
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/40—Casings; Connections of working fluid
- F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
- F04D29/4206—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
- F04D29/422—Discharge tongues
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/40—Casings; Connections of working fluid
- F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
- F04D29/4206—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
- F04D29/4226—Fan casings
- F04D29/4253—Fan casings with axial entry and discharge
Definitions
- the invention relates to a fan arrangement for turbomachines according to the preamble of claim 1.
- Blower arrangements for turbomachines in particular turbocharged or turbocharged engines are well known. These usually consist of a preferably spiral-shaped housing and at least one impeller housed therein with a plurality of impeller blades, wherein a fluid flows through the housing.
- a turbocharged engine the energy flow from the fluid to the impeller or its blades and in the case of a turbo-working machine from the impeller or its blades to the fluid takes place here.
- the fluid may be, for example, water or air.
- rule 4 for example, a mixture of the fluidic properties according to the rules 1 to 3 can be achieved.
- the housing it is customary to specify the dimensions of the housing by means of polar coordinates r, ⁇ or cylinder coordinates r, ⁇ , z.
- the origin of the radial coordinate ⁇ is then the center of the impeller, wherein the zero point of the circumferential position describing ⁇ - coordinate to the beginning of the inflow space, ie preferably the spiral or Abgrifflippe the housing is assigned.
- volume flow Q ( ⁇ ) conveyed up to the circumferential position ⁇ from the impeller or into the impeller must be adapted to the cross-section A ( ⁇ , r) of the flow channel formed by the housing, with the radial position of the cross section being of particular importance in addition to the cross-sectional area ,
- the width of the cross section A ( ⁇ , r) at the radius position r is understood by b (r).
- the volume flow Q ( ⁇ ) thus depends on the inflow or conveying surface A LR ( ⁇ ) of the impeller up to the circumferential position ⁇ .
- an envelope shape for example an envelope cylinder, is placed around the impeller. It is often assumed that the volume flow Q ( ⁇ ) is proportional to this area, ie proportional to the circumferential angle ⁇ .
- a housing or a housing arrangement in this case usually has flow channels with simple cross sections such as circle, rectangle, trapezium, etc., which form a spiral shape for guiding the fluid in the housing over the circumference of the impeller.
- This is the basis of the common name "spiral blower” or fan coil.
- the tapping of the flow takes place via a so-called spiral lip or spiral tongue, which is provided for the separation of the outflow from the inflow space.
- the fluid in particular the air, flows radially or tangentially outward perpendicular to the axis of rotation of the impeller.
- DE 19811877 C2 For example, an axial outflow of the fluid, which, however, associated with high flow losses.
- the spiral lip or spiral tongue runs parallel to the axis of rotation and often parallel to the outer edges of the blades of the impeller.
- the disadvantage of the emerging from the channels formed by the blades of the impeller fluid during periodic impingement on the spiral lip or spiral tongue a generate whistling noise.
- the document DE 310721 already an inclination of the blade edges with respect to the tapping lip.
- the publication DE 4313617 is to take a sloping tap lip, and indeed the tapped air extends radially outwardly offset over the beginning of the spiral housing.
- the document describes DE 43 31 606 a volute casing for turbomachinery in which the tongue region adjoining region has circular spiral cross sections until reaching a predetermined outer diameter. After reaching the spiral cross-section increases only in the axial direction. In two fixed semicircles a magnifying rectangle is inserted for this purpose.
- the connection of a spiral casing with swirl describes Bruno Eck in “Fans”, Springer Verlag, 5th edition, 1972, p 221 as an "asymmetrical spiral” to Oesterlein.
- the design of the housing depends on the impeller outlet.
- the publication describes US 5156524 a box spiral with discontinuities, in which the axial and radial dimensions of the spiral have cracks or inflection points in the contour.
- the publication describes Bruno Eck in “Fans”, Springer Verlag, 5th edition, 1972, p. 212 a volute that is developed inwardly such that the radial coordinates of the cross section are in part smaller than the exit radius of the impeller.
- the pamphlets DE1428191A1 and US2405048A1 disclose blowers having a volute casing in which the wall immediately adjacent to the tapping lip separates two flow-through spaces which are axially offset from each other so as to overlap one another in the region of said wall in the axial direction.
- the said wall deflects the flow in the axial direction, that is, the wall runs simultaneously in the circumferential direction and axially.
- the present invention seeks to provide a blower arrangement which eliminates the aforementioned disadvantages and in particular improves the introduction of the flow from the impeller into the collecting housing.
- the object is achieved on the basis of the features of the preamble of claim 1 by its characterizing features.
- the essential aspect of the invention is to be seen in that the first inflow space and the second inflow space are separated from one another via at least one housing wall section, that the outer edge of the at least one housing wall section facing the impeller forms a tapping lip and that the housing wall section extends in the direction of the inflow chambers and has at least one radial component.
- the spiral tap thus runs obliquely to the axis of rotation of the impeller, wherein the tap portion forming the wall portion of the spiral tap radially or radially Component to the outside, ie in the direction of the inflow space before they pass into the collection housing or in the outflow.
- the first inflow space and the second outflow space are at least partially offset axially relative to one another with respect to the axis of rotation and overlap at least partially in the area of the impeller.
- the first inflow space is gradually widened at the expense of the second inflow space, wherein the second inflow space can already form the outflow space of the spiral blower.
- the impeller thus promotes full width into the first inflow space, while the delivery into the second inflow space or outflow space is completed.
- the second inflow space or outflow space is at this point or circumferential position to the outlet channel and is then axially offset next to or radially offset from the first inflow space.
- the inventive design of the spiral tap for the separation of the two inflow spaces or of the inflow and outflow space will be referred to below as Schräglippenabgriff.
- the transition region described can also be provided to form a deflection region for a flow in the axial direction.
- the second inflow space forms, at least in sections, the outflow space for discharging the volumetric flow conveyed from the first inflow space through the volute casing.
- the incipient first inflow space of the one volute casing lies next to the second inflow space or the outflow region of the second volute casing.
- the transition regions may be different obliquely to each other, ie ⁇ 1 ⁇ ⁇ 2. It is also possible to connect the bevel lip tap with a normal spiral tap. The change from the first inflow space to the second inflow space or outflow space then takes place abruptly.
- the volumetric flow in a spiral with an oblique tap does not increase linearly in the transitional range ⁇ , but depending on the course of the transition curve between inflow and outflow space, which in the simplest case is a straight line on a cylinder surface ("enveloping cylinder around the impeller").
- This delivery volume flow Q ( ⁇ ) corresponds to a specific passage area of the volute casing A S ( ⁇ ) depending on the development rule for the speed. From the necessary surface then the geometric dimensions of the cross section can be determined.
- a delivery volume flow Q ( ⁇ ) can also be specified, and thus the circumferential position ⁇ can be determined. Furthermore, it may prove expedient to change the contour of the spiral cross-section along the circumferential coordinate ⁇ .
- a S ( ⁇ ) of the cross-section of the flow channel is constructed within the fan assembly of analytically controllable sub-elements, such as rectangles, triangles, trapezoids, semicircles and quadrants.
- the exponent can be any real number> 0.
- the tangency hyperbolic function can be used as the weighting function.
- transitions between the regions can also take place in the same way as in the strake plan for the ribs of a boat hull, the respective cross sections being subjected to the respective development rules for the contour and the transition regions simply being traversed. Very locally arise thus slightly deviate from the development rules cross sections, see also US 5156524 , As a result, edges can be sanded at unsteady points advantageous.
- the corresponding volume flow of the respective cross-sections also numerically calculable and assign the angular position of the corresponding volume flow from the impeller.
- the invention is of course also applicable to wheels whose shape deviates from the cylindrical shape, for example, frustoconical wheels or Impellers with almost any rotational body shape.
- wheels whose shape deviates from the cylindrical shape, for example, frustoconical wheels or Impellers with almost any rotational body shape.
- the spatial surface of the respective envelope shape at the exit position is required for fixing the associated spiral cross-section.
- FIG. 1a shows, for example, a simple, known from the prior art fan assembly with a housing 20 in which an impeller 10 is received.
- the impeller 10 is in this case rotatably mounted about a rotation axis 90, wherein the housing 20 surrounds the axis of rotation 90 spirally and thus forms a spiral housing 20 with a Abgriffslippe 30.
- the impeller 10 has a plurality of impeller blades 12 which are arranged concentrically around the rotation axis 90 and whose free blade end faces each preferably have the same distance from the axis of rotation 90.
- the contour of the spiral-shaped housing 20 is determined, for example, especially for rectangular spirals by the ratio of the absolute speeds C M / C U.
- Fig. 1b further shows a side view of the fan assembly along the section axis AA. From this, the parallel course of the "normal" Abgrifflippe 30 to the fan axis or axis 90 of the impeller 10 is clear.
- FIG. 2a an exemplary embodiment of a blower arrangement according to the invention is shown by way of example, the spiral housing 20 of which has a tap lip 40 running obliquely to the axis 90, which is referred to below as an oblique lip 40.
- Fig. 2c is the development of the cross section 50 of the outflow space 80 adjacent to the widening Inflow space 60 shown.
- the inflow space 60 and the outflow space 80 thus directly adjoin the free blade end faces of the impeller 10 in the region of the oblique lip 40, specifically in the radial direction relative to the axis of rotation 90.
- the inflow space 60 and the outflow space 80 thus overlap at least in the region of the tapping lip 30 and are separated by the adjoining the spiral tap housing wall portion with radial direction component.
- the described Abgriffssection will be referred to below as Schräglippenabgriff.
- Fig. 2d shows a plan view of a development 105 of the surrounding the impeller 10 Hüllzylinders.
- the angle ⁇ of the oblique lip 40 can be adapted, for example, to the angle ⁇ 'between the axial intake speed V AX and the absolute speed C at the exit from the impeller 10.
- Fig. 3a shows by way of example an impeller 10 with the associated envelope shape, for example, an enveloping cylinder 100, with different developments 110 to 170.
- the unwinds 110 to 170 of the enveloping cylinder 100a hereby have different Abgriffsvarin, namely normal tap 110, oblique tap 120, slightly more curved Tap 130, Ausströmraumtrennung 140, two variants of the Einströmigen Schräglippenabgriffes 150a, b, two variants of the two-prong Schräglippenabgriffes 160a, b and a dreiströmigen oblique lip tap 170 with outflow to two sides.
- Fig. 3b shows a further, preferably wider embodiment of the enveloping cylinder 100, which can be used for example for a drum rotor 11 and, for example, three bevel lip taps 161, 151, 152.
- the top view of the impeller 11 forming the impeller reveals that the motor 13, the drum rotor 11 in two areas 15 a, b divides. This is a typical one Design of a fan assembly for suction devices such as cooker hoods.
- the two regions 15a, b find their continuation in the development of the enveloping cylinder 161.
- the transition region 45a of the oblique lips 40a, b extends over 180 ° and is in the Fig. 3b to the right of the 360 ° point, again by means of a dotted line.
- the transition region 45b extends for example over 360 ° or over 720 °.
- Fig. 3c shows the unwinds 171, 172, 173, in which the enveloping cylinder is divided by way of example into four lip channels.
- a selected lip channel 177a, b, c per unwinds 171, 172, 172 is shown in FIG Fig. 3c each hatched.
- the outflow 49c, 49d, 49e takes place here, for example, obliquely to the unwinding 171, 172 or in the longitudinal direction to the unwinding 173, wherein the lip channels 177a, b, c each extend over 270 °, for example.
- Fig. 3d shows a schematic representation of the principle of the assignment of angular position ⁇ , lip channel area A LR ( ⁇ ) and channel cross-section 185 at the respective angular position ⁇ .
- the cross section 185 at the circumferential position ⁇ is chosen such that the also in Fig.
- Fig. 4 shows, for example, the construction of different cross-sections of the spiral channels of the fan assembly, in particular a push fan by means of simple geometric primitives such as rectangle 180, quadrant 190, triangle 185, semicircle 200, semi-ellipse 210.
- the cross section can also be designed as a free-form 240, wherein between the inlet space 220 from the impeller 10 and the axially offset outflow space or channel space 230a, b, a guide pin 250 is provided.
- FIGS. 5 to 11 each embodiments of the housing arrangement according to the invention for a pusher fan shown.
- the spiral-shaped housing is in this case, for example, impressströmig and consists for example of two half-spirals.
- the two spiral halves are therefore identical.
- Fig. 5 shows a method for developing the cross sections of a spiral half in the first to fourth region 1, 2, 3, 4 based on exemplarily selected cross sections (see hatched shapes) along the development of the enveloping cylinder 270 of width b LR over a circumferential range of ⁇ from 0 ° to 220 °.
- the fourth region 4, 290 in which the outflow from the half-spiral takes place, is arranged axially offset next to the first region 1, 280.
- Fig. 6 shows in an enlarged view the development of the cross sections 320a-e in the fourth region 4, 290 and Fig. 7 a variant of the fan assembly in which the Outlet channel 300 is deflected in the axial direction, by rotation of the cross-sections 320 ae in the fourth region 4 with increasing circumferential position ⁇ in the axial direction 310.
- a Entdraller 330 is provided by means of the flow energy can be recovered.
- FIGS. 8a to 8h are the rules underlying the development of the training in FIGS. 5 and 6 illustrated cross sections illustrates.
- FIG. 8a shows the first area 1, in which the inflow takes place in the half-spiral.
- a rectangular shape of width b ( ⁇ ) and height r H1 ( ⁇ ) is developed.
- each side of the rectangle section with the radius r K are added, wherein the axial width of the rectangle corresponds to the width b LR .
- r K ( ⁇ ), r H2 ( ⁇ ) and r HE ( ⁇ ) may vary depending on the particular embodiment, such as the diagram in FIG Fig. 8d can be seen.
- the third area 3 is in Fig. 8e, f shown.
- the radius of curvature r K ( ⁇ ) continues to increase until the outflow space reaches the fourth region 4.
- the outlet cross section is in accordance with FIG. 8h a circle.
- a section along the line AA through a double spiral housing 340 at the end of the third region 3 is shown.
- the cross section of the respective spiral of the double spiral housing 340 is composed radially outside the impeller 10 from the quarter circles 190 and the rectangle 180.
- Radially in the region of the impeller 10 is the semicircular cross-section 200, so that an entire cross section of the mold 260 is established.
- FIG. 10 A perspective sectional view through the fan assembly with a double spiral shows, for example FIG. 10 , along the section line AA according to Fig. 9 ,
- the impeller 10 is rotatably supported by a bearing 360 in the double spiral housing 340.
- the the FIG. 10 Removable cross-sectional shapes correspond to the cross-sections at the end of the third region 3, in the upper and lower spiral 260a, b.
- a top view of the in FIG. 10 shown blower arrangement is in FIG. 11 shown.
- the medium is supplied to the impeller 10, wherein the discharge of the medium via the two outlet channels 300a, b of the upper and lower spiral 260a, b takes place.
- the plan view of the transition region between the first region 1, 380 and the fourth region 4, 390 can be seen, wherein the course of the oblique lip between the first and fourth region 1, 380 and 4, 390 is provided with the symbol 370.
- the in Fig. 10 and Fig. 11 shown blower arrangement is suitable to use a single or multi-flow pusher fan for a jet sail according to DE 10300621 build.
- an S-shaped intake passage 350 could be provided to generate a pre-puff.
- Fig. 12 1 shows the development of the enveloping cylinder 440 a of a two-column blower arrangement, which is subdivided into a small secondary flow area 400 and a main flow area 410.
- the blower arrangement conveys at the outlet 450 for the secondary flow the volume flow Q N and at the outlet for the main flow 460 the volume flow Q H.
- the fan assembly further includes two oblique lips 420 and 430, which have a different oblique course, which include a different angle with the axis of rotation 90 of the impeller 10.
- the tap of the main volume flow and the shift in the axial direction in the bevel lip tap starts at position 470 and is completed at position 480. This type of tap corresponds to the position 490 of the cross section 500.
- the cross section 510 is formed at the position 490.
- the inflow cross section 520 extends almost over the entire width of the enveloping cylinder b LR .
- the separation of inflow cross section 520 and outflow cross section 530 thus extends in the axial and radial directions.
- the cross section 550 is required at the position 490.
- Fig. 13 shows a side and end view of the fan assembly with the cross sections according to Fig. 12 ,
- the two outlets of the secondary flow 450 and the main flow 460 are offset by 90 ° to each other and are each arranged axially offset from the impeller 10.
- FIG. 14 The development of an enveloping cylinder 440b which is subdivided into a conveying region 580 for the main stream and into a further conveying region 590 for two secondary streams 560a, b is, for example, the Fig. 14 refer to.
- the beginning of the inflow of the main volume flow into the region 580 or the outflow from the further delivery region 590 into the two bypass channels 610a, b takes place via two obliquely arranged oblique lips 600a, b.
- the tap of the main flow or the inflow into the further conveyor region 590 begins with a normal spiral tap 570.
- a side view and an end view of a fan assembly according to FIG. 14 are in Fig. 15 shown. From this, the outwardly extending bypass channels 610a, b and the main flow channel 620 can be clearly seen.
- Fig. 16 shows a fan assembly 630 with a in the FIGS. 12 to 15 shown tapping, which is integrated in a suction device 640 with blowout 650, preferably an extractor hood.
- a rising from a cooking fume stream W is sucked through a filter 641 in the extractor hood 640.
- the blower arrangement 630 generates the vacuum required for this in a suction chamber 642 of the extractor hood 640.
- the blower arrangement 630 conveys the main part of the filtered steam stream W as the main stream Q H into an exhaust duct 644 arranged in a chimney 643.
- a small part of the filtered steam stream W can be used as a side stream Q N are specifically directed out of the housing of the hood 640 back into the room to produce, for example, an air curtain or a front vortex Q F.
- Fig. 17a is the development of the enveloping cylinder 162 of a double-flow bevel fan according to Fig. 3b shown schematically.
- Fig. 17a shows by way of example a plurality of spiral cross sections 660a-q, wherein the cross sections 660c '- 660h or 660n - 660p the transition regions ⁇ ' in section 666 and ⁇ "in excerpt 667 are shown enlarged at least partially bug-like recesses 665 to reduce the size.
- the spiral may also extend beyond the width 668 of the enveloping cylinder, as indicated by the bone-shaped cross-section 661. This could for example be provided instead of the cross section 660l.
- FIGS. 17b to 17d In each case, a section of the transition region between a first inflow space and a second inflow space or outflow space is shown, which are separated from one another via the oblique lip 40 and the adjoining housing wall section 760a.
- FIGS. 17b to 17d several variants of the cross section 660b, 662a, 662b of the first inflow space shown.
- the impeller 10 rotatably mounted about the axis 90 conveys with the impeller blades 12 into the beginning first inflow space 660b, 662a, 662b and into the starting outflow space 660m ', 660m ", 660m"'.
- the adjoining the oblique lip 40 housing wall portion 760a in the transition region between the inflow and outflow with respect to the housing extends in the radial direction 17, and that includes an angle ⁇ smaller than 90 ° with the axis of rotation 90 a.
- the housing wall portion 760a of the oblique lip 40 at the cross section 660b at an angle ⁇ of 90 ° to the surface of the enveloping cylinder 162 and the axis of rotation 90.
- the radial orientation, ie the angle ⁇ along the oblique lip 40 with the circumferential angle ⁇ change.
- Fig. 17c . d Furthermore, alternative embodiments of the housing wall section 760b, c can be seen, which are characterized by a strong orientation in the radial direction, ie, have an angle ⁇ smaller than 90 °.
- the housing wall portion 760c of the tapered lip 40 may also have a free-formed curvature (see cross-section 662b), such as a Bezier curve. This shape can extend over the entire transitional range ⁇ of the oblique lip 40 and change comparable to a ship's bow along the circumference, which is why this Embodiment should also be referred to as a bow spiral.
- the radial orientation gradually changes due to the curvature.
- the two inflow spaces or the inflow and outflow space are thus offset both axially and radially relative to each other.
- Fig. 18a shows a helical spiral according to Fig. 3c , in a schematic plan view.
- four lip channels 690 a to d are preferably arranged, whose cross sections 680 c, e, f are shown by way of example at the edge of the helical spiral.
- a development of the enveloping cylinder 171 of the helical spiral is exemplified in FIG. 18b shown.
- Lip channel 690a between points A, B, C, D is shown with the associated channel cross-sections 680a-f.
- the inflow 700 of the fluid from the impeller 670 in the lip channel 690a and the outflow 710 from the lip channel extends obliquely to the settlement.
- FIGS. 18a, b shown blower arrangement shows Fig. 19a .
- the single-flow impeller 670 is connected to a motor 720.
- the flow Upon exiting the volute, the flow enters an annular diffuser 740 which reduces the cross-section to the exit area 750.
- the central outflow cone 730 can be fixed or rotate connected to the motor.
- Fig. 19b shows here the spatial course of the lip channel 690a and the connecting lines between the points A, B, C, D.
- the outflow in this example corresponds to that of an axial blower, so that the methods known there for the rectification and the Entdrallung the flow are applied can.
- Means of the invention Schräglippenabgriff a guidance of the fluid is avoided in a narrow peripheral area, whereby the noise level of the suction device, in particular a cooker hood can be significantly reduced.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Description
Die Erfindung betrifft eine Gebläseanordnung für Turbomaschinen gemäß dem Oberbegriff des Patentanspruches 1.The invention relates to a fan arrangement for turbomachines according to the preamble of
Gebläseanordnungen für Turbomaschinen, insbesondere Turboarbeits- oder Turbokraftmaschinen sind hinreichend bekannt. Diese bestehen üblicherweise aus einem vorzugsweise spiralförmigen Gehäuse und zumindest einem darin aufgenommenen Laufrad mit einer Vielzahl an Laufradschaufeln, wobei durch das Gehäuse ein Fluid strömt. Bei einer Turbokraftmaschine erfolgt hierbei der Energiefluss vom Fluid an das Laufrad bzw. dessen Schaufeln und bei einer Turboarbeitsmaschine vom Laufrad bzw. dessen Schaufeln an das Fluid. Das Fluid kann beispielsweise Wasser oder Luft sein.Blower arrangements for turbomachines, in particular turbocharged or turbocharged engines are well known. These usually consist of a preferably spiral-shaped housing and at least one impeller housed therein with a plurality of impeller blades, wherein a fluid flows through the housing. In a turbocharged engine, the energy flow from the fluid to the impeller or its blades and in the case of a turbo-working machine from the impeller or its blades to the fluid takes place here. The fluid may be, for example, water or air.
Derartige Gehäuse werden oftmals auch als Führungsgehäuse bezeichnet, deren strömungstechnische Ausgestaltung beispielsweise auf folgenden mathematischen Regeln basieren:
- Regel 1:
- Drallsatzes mit a = b = 0;
- Regel 2:
- Kontinuitätsgleichung mit a = b = 1;
- Regel 3:
- den Drallsatzes vorzugsweise im Einströmbereich oder im Ausströmbereich des Gehäuses und in den übrigen Fällen die Kontinuitätsgleichung;
- Regel 4:
- speziell Vorgabe für a und b, vorzugsweise zwischen 0 und 2.
- Rule 1:
- Spin set with a = b = 0;
- Rule 2:
- Continuity equation with a = b = 1;
- Rule 3:
- the set of swirls preferably in the inflow region or outflow region of the housing and in the remaining cases the equation of continuity;
- Rule 4:
- especially specification for a and b, preferably between 0 and 2.
Mittels der Regel 4 kann beispielsweise eine Mischung der strömungstechnischen Eigenschaften nach den Regeln 1 bis 3 erzielt werden.By means of
Ferner ist es üblich die Abmessungen des Gehäuses mittels Polarkoordinaten r, ϕ oder Zylinderkoordinaten r, ϕ, z anzugeben. Ursprung der radialen Koordinate ϕ ist dann die Laufradmitte, wobei der Nullpunkt der die Umfangsposition beschreibenden ϕ - Koordinate dem Anfang des Einströmraumes, d.h. vorzugsweise der Spiral- oder Abgrifflippe des Gehäuses zugeordnet ist. Der bis zur Umfangsposition ϕ vom Laufrad geförderte bzw. ins Laufrad eintretende Volumenstrom Q(ϕ) ist an den Querschnitt A(ϕ, r) des durch das Gehäuse gebildeten Strömungskanal anzupassen, wobei neben der Querschnittsfläche auch der radialen Position des Querschnittes eine besondere Bedeutung zukommt. Hierbei ergibt sich zur Beschreibung des Volumenstroms Q(ϕ) folgende Gleichung:
Dabei wird unter b(r) die Breite des Querschnittes A(ϕ, r) an der Radiusposition r verstanden. Der Volumenstrom Q(ϕ) hängt somit von der Einström- oder Förderfläche ALR(ϕ) des Laufrades bis zur Umfangsposition ϕ ab. Um das Laufrad wird hierbei eine Hüllform, z.B. ein Hüll-Zylinder gelegt. Oftmals wird angenommen, dass der Volumenstrom Q(ϕ) proportional zu dieser Fläche, also proportional zum Umfangswinkel ϕ ist. Mittels eines winkelspezifischen Förderstromes
kann der Volumenstrom Q(ϕ) für die jeweilige Winkelposition ϕ angegeben werden.In this case, the width of the cross section A (φ, r) at the radius position r is understood by b (r). The volume flow Q (φ) thus depends on the inflow or conveying surface A LR (φ) of the impeller up to the circumferential position φ. In this case, an envelope shape, for example an envelope cylinder, is placed around the impeller. It is often assumed that the volume flow Q (φ) is proportional to this area, ie proportional to the circumferential angle φ. By means of an angle-specific flow
the volume flow Q (φ) can be specified for the respective angular position φ.
Die beschriebenen Ansätze sind insbesondere den folgenden Veröffentlichungen sinngemäß zu entnehmen:
- "
Ventilatoren" von Bruno Eck, Springer Verlag, 5. Auflage, 1972 - "
Kreiselpumpen: ein Handbuch für Entwicklung, Anlagenplanung und Betrieb" von Johann Gütlich, Springer Verlag, 1999 - "
Die Kreiselpumpen" von Carl Pfleiderer, Springer Verlag, 5. Auflage, 1961 - "
Radial- und Axialpumpen: Theorie, Entwurf, Anwendung", Alexey Joakim Stepanoff, Springer Verlag, 1959
- "
Fans "by Bruno Eck, Springer Verlag, 5th edition, 1972 - "
Centrifugal pumps: a manual for development, plant design and operation "by Johann Gütlich, Springer Verlag, 1999 - "
The centrifugal pumps "by Carl Pfleiderer, Springer Verlag, 5th edition, 1961 - "
Radial and Axial Pumps: Theory, Design, Application ", Alexey Joakim Stepanoff, Springer Verlag, 1959
Stellvertretend werden hier die Verhältnisse bei einer Turboarbeitsmaschine und einem Gebläse beschrieben. Bei einer Turbokraftmaschine ist prinzipiell lediglich eine Umkehrung der Strömungsrichtung erforderlich.The conditions for a turbo-machine and a blower are described here by way of example. In a turbocharged engine, in principle only a reversal of the flow direction is required.
Ein Gehäuse bzw. eine Gehäuseanordnung weist hierbei überlicherweise Strömungskanäle mit einfachen Querschnitten wie Kreis, Rechteck, Trapez etc. auf, die zur Führung des Fluids im Gehäuse über den Umfang des Laufrades eine Spiralform ausbilden. Hierauf beruht die geläufige Bezeichnung "Spiralgebläse" bzw. Gebläsespirale. Der Abgriff der Strömung erfolgt dabei über eine so genannte Spirallippe oder Spiralzunge, die zur Trennung des Ausströmraums vom Einströmraum vorgesehen ist. Bei den meisten Gebläseanordnungen strömt das Fluid, insbesondere die Luft senkrecht zur Drehachse des Laufrades radial oder tangential nach außen ab. Unterschiedlich hierzu offenbart die Druckschrift
Bei den beschriebenen Ausführungsformen findet also an derselben Umfangsposition ϕ des Laufrades sowohl ein Beginn der Förderung des Fluids in das Gehäuse als auch ein Abströmen des durch das Gehäuse geführten Fluids über die Abgriffslippe statt, d.h. Ausströmraum und Einströmraum weisen dieselbe Umfangsposition ϕ auf.Thus, in the described embodiments, at the same circumferential position φ of the impeller, both the beginning of the delivery of the fluid into the housing and the outflow of the fluid passing through the housing, via the tapping lip, take place. Outflow space and inflow space have the same circumferential position φ.
Ferner ist aus der Druckschrift
Ferner beschreibt die Druckschrift
Häufig ist die Ausgestaltung des Gehäuses vom Laufradaustritt abhängig. Für Anwendungen mit Platzproblemen beschreibt beispielsweise die Druckschrift
Die Druckschriften
Bei den meisten Spiralgehäusen tritt jedoch die Luft mit einer Komponente senkrecht zur Drehachse des Laufrades aus. Ist der Einsatz der Gebläseanordnung in einem Radialgebläse unter engen Platzverhältnissen als Schubgebläse oder in einer Dunstabzugshaube vorgesehen, so ergeben sich folgende Probleme:
- Das Fluid wir durch die Gebläseanordnung axial angesaugt, aber in einer Ebene senkrecht zur Drehachse des Laufrades ausgeblasen, d.h. es ist eine Umlenkung des Fluids in axialer Richtung erforderlich.
- Die Gebläsespirale erfordert speziell bei hohen Volumenströmen eine hohe radiale Weite.
- Der Abgriff erfolgt abrupt in einem engen Umfangsbereich, wodurch ein hoher Geräuschpegel entstehen kann.
- The fluid is sucked axially through the blower arrangement, but blown out in a plane perpendicular to the axis of rotation of the impeller, ie a deflection of the fluid in the axial direction is required.
- The fan coil requires a high radial width especially at high flow rates.
- The tap is abruptly in a narrow peripheral area, whereby a high noise level can occur.
Ausgehend hiervon liegt der Erfindung die Aufgabe zugrunde, eine Gebläseanordnung zu schaffen, die die zuvor genannten Nachteile beseitigt und insbesondere die Einleitung der Strömung vom Laufrad in das Sammelgehäuse verbessert. Die Aufgabe wird ausgehend von den Merkmalen des Oberbegriffes des Patentanspruches 1 durch dessen kennzeichnende Merkmale gelöst.Proceeding from this, the present invention seeks to provide a blower arrangement which eliminates the aforementioned disadvantages and in particular improves the introduction of the flow from the impeller into the collecting housing. The object is achieved on the basis of the features of the preamble of
Der wesentliche Aspekt der Erfindung ist darin zu sehen, dass der erste Einströmraum und der zweite Einströmraum über zumindest einen Gehäusewandabschnitt voneinander getrennt sind, dass die zum Laufrad weisende Außenkante des zumindest einen Gehäusewandabschnittes eine Abgriffslippe bildet und dass der Gehäusewandabschnitt sich in Richtung der Einströmräume erstreckt und zumindest eine radiale Komponente aufweist. Der Spiralabgriff verläuft somit schräg zur Drehachse des Laufrades, wobei der die Abgriffslippe bildende Wandabschnitt des Spiralabgriffes radial oder mit stark radialer Komponente nach außen, d.h. in Richtung der Einströmräume verläuft bevor diese in das Sammelgehäuse bzw. in den Ausströmbereich übergehen.The essential aspect of the invention is to be seen in that the first inflow space and the second inflow space are separated from one another via at least one housing wall section, that the outer edge of the at least one housing wall section facing the impeller forms a tapping lip and that the housing wall section extends in the direction of the inflow chambers and has at least one radial component. The spiral tap thus runs obliquely to the axis of rotation of the impeller, wherein the tap portion forming the wall portion of the spiral tap radially or radially Component to the outside, ie in the direction of the inflow space before they pass into the collection housing or in the outflow.
Zusätzlich sind erfindungsgemäß der erste Einströmraum und der zweite Ausströmraum zumindest abschnittsweise in Bezug auf die Drehachse axial zueinander versetzt und überlappen sich zumindest teilweise im Bereich des Laufrades. Bei der erfindungsgemäßen Gebläseanordnung gibt es somit einen Umfangsbereich Δϕ, indem ein beginnender erster Einströmbereich und ein ggf. endender zweiter Einströmbereich sich zumindest teilweise überlappen und die über den Gehäusewandabschnitt voneinander getrennt sind. Im Übergangsbereich wird der erste Einströmraum auf Kosten des zweiten Einströmraumes allmählich verbreitert, wobei der zweite Einströmraum bereits den Ausströmraum des Spiralgebläses bilden kann. Am Ende des Übergangsbereiches fördert somit das Laufrad auf voller Breite in den ersten Einströmraum, während die Förderung in den zweiten Einströmraum bzw. Ausströmraum abgeschlossen ist. Der zweite Einströmraum bzw. Ausströmraum wird an dieser Stelle bzw. Umfangsposition zum Austrittskanal und befindet sich dann axial versetzt neben oder auch radial versetzt zum ersten Einströmraum. Die erfindungsgemäße Ausbildung des Spiralabgriffes zur Trennung der beiden Einströmräume bzw. des Ein- und Ausströmraumes soll im Folgenden als Schräglippenabgriff bezeichnet werden.In addition, according to the invention, the first inflow space and the second outflow space are at least partially offset axially relative to one another with respect to the axis of rotation and overlap at least partially in the area of the impeller. In the case of the blower arrangement according to the invention, there is thus a peripheral region Δφ in that an incipient first inflow region and an optionally terminating second inflow region at least partially overlap and which are separated from one another via the housing wall section. In the transition region, the first inflow space is gradually widened at the expense of the second inflow space, wherein the second inflow space can already form the outflow space of the spiral blower. At the end of the transition region, the impeller thus promotes full width into the first inflow space, while the delivery into the second inflow space or outflow space is completed. The second inflow space or outflow space is at this point or circumferential position to the outlet channel and is then axially offset next to or radially offset from the first inflow space. The inventive design of the spiral tap for the separation of the two inflow spaces or of the inflow and outflow space will be referred to below as Schräglippenabgriff.
Der beschriebene Übergangsbereich kann ebenfalls zur Ausbildung eines Umlenkungsbereiches für eine Strömung in axialer Richtung vorgesehen werden. Erfindungsgemäß bildet der zweite Einströmraum zumindest abschnittsweise den Ausströmraum zum Ausbringen des vom ersten Einströmraum durch das Spiralgehäuse geförderten Volumenstromes.The transition region described can also be provided to form a deflection region for a flow in the axial direction. According to the invention, the second inflow space forms, at least in sections, the outflow space for discharging the volumetric flow conveyed from the first inflow space through the volute casing.
Obwohl sie nicht Teil der Erfindung ist, ist eine Verwendung in einer Zweifachspirale ("Mehrfachspirale") realisierbar. Der beginnende erste Einströmraum des einen Spiralgehäuses liegt dabei neben dem zweiten Einströmraum bzw. dem Ausströmbereich des zweiten Spiralgehäuses. Dabei können die Übergangsbereiche für Ein- und Austritt bei beiden Spiralhälften nahezu identisch ausgelegt sein, d.h. Δϕ1 = Δϕ2. Alternativ können die Übergangsbereiche unterschiedlich schräg zueinander verlaufen, d.h. Δϕ1 ≠ Δϕ2. Möglich ist auch die Verbindung des Schräglippenabgriffes mit einem normalen Spiralabgriff. Der Wechsel vom ersten Einströmraum zum zweiten Einströmraum bzw. Ausströmraum erfolgt dann abrupt.Although not part of the invention, use in a double spiral ("multiple spiral") is feasible. The incipient first inflow space of the one volute casing lies next to the second inflow space or the outflow region of the second volute casing. In this case, the transition regions for inlet and outlet can be designed almost identically for both spiral halves, ie Δφ1 = Δφ2. Alternatively, the transition regions may be different obliquely to each other, ie Δφ1 ≠ Δφ2. It is also possible to connect the bevel lip tap with a normal spiral tap. The change from the first inflow space to the second inflow space or outflow space then takes place abruptly.
Die Entwicklung des Verlaufs des Spiralquerschnittes entlang der Umfangskoordinate ϕ wird nachfolgend beispielhaft beschrieben.The development of the course of the spiral cross section along the circumferential coordinate φ will be described below by way of example.
Der Volumenstrom bei einer Spirale mit schrägem Abgriff nimmt im Übergangsbereich Δϕ nicht linear zu, sondern je nach Verlauf der Übergangskurve zwischen Ein- und Ausströmraum, die im einfachsten Fall eine Gerade auf einer Zylinderoberfläche ("Hüllzylinder um das Laufrad") ist. Statt des winkelspezifischen Volumenstromes QSPEZ-W wird bei Schräglippenspiralen das Verhältnis Volumenstrom und der Fläche des Hüllzylinders QSPEZ-A = Q / ALR verwendet. Aus der Fläche des Spiralkanals ALR(ϕ) auf dem Hüllzylinder bis zur Position ϕ lässt sich der Volumenstrom aus dem Laufrad Q(ϕ) = QSPEZ-A * ALR(ϕ) bestimmen. Diesem Fördervolumenstrom Q(ϕ) entspricht eine bestimmte Durchtrittsfläche des Spiralgehäuses AS(ϕ) je nach Entwicklungsregel für die Geschwindigkeit. Aus der notwendigen Fläche lassen sich dann die geometrischen Abmessungen des Querschnittes bestimmen.The volumetric flow in a spiral with an oblique tap does not increase linearly in the transitional range Δφ, but depending on the course of the transition curve between inflow and outflow space, which in the simplest case is a straight line on a cylinder surface ("enveloping cylinder around the impeller"). Instead of the angle-specific volume flow Q SPEZ-W , the ratio volumetric flow and the area of the enveloping cylinder Q SPEZ-A = Q / A LR are used for oblique spiral spirals . From the surface of the spiral channel A LR (φ) on the enveloping cylinder to the position φ, the volume flow from the impeller Q (φ) = Q SPEZ-A * A LR (φ) can be determined. This delivery volume flow Q (φ) corresponds to a specific passage area of the volute casing A S (φ) depending on the development rule for the speed. From the necessary surface then the geometric dimensions of the cross section can be determined.
Umgekehrt kann zu einer vorgegeben Durchtrittsfläche AS(ϕ) auch ein Fördervolumenstrom Q(ϕ) angeben werden und damit die Umfangsposition ϕ bestimmt werden. Ferner kann es sich als zweckmäßig erweisen, die Kontur des Spiralquerschnittes längs der Umfangskoordinate ϕ zu verändern.Conversely, for a given passage area A S (φ), a delivery volume flow Q (φ) can also be specified, and thus the circumferential position φ can be determined. Furthermore, it may prove expedient to change the contour of the spiral cross-section along the circumferential coordinate φ.
Für die analytische Zuordnung des Volumenstromes Q(ϕ) und damit auch der Umfangsposition ϕ zu einem Querschnitt AS(ϕ) wird des Querschnitt des Strömungskanals innerhalb der Gebläseanordnung aus analytisch beherrschbaren Teilelementen aufgebaut, beispielsweise Rechtecke, Dreiecke, Trapeze, Halbkreise und Viertelkreise. Diese Teilelemente verändern sich derart entlang des Umfanges des Spiralgehäuses, dass das Spiralgehäuse möglichst stetig verläuft. Dies gilt insbesondere für den Fall, dass das Spiralgehäuse in Bereiche unterteilt wird, in denen sich die Teilelemente des Querschnittes nach unterschiedlichen Regeln verändern. Dazu kann es zweckmäßig sein einen Entwicklungsbereich in eine endliche Anzahl von Entwicklungsschritten i = 1, 2 ... n zu unterteilen. Innerhalb dieses Bereiches kann eine Größe als Funktion a) des Entwicklungsschrittes i, b) einer Referenzgröße rK ("Referenz") und c) eines Exponenten exp_verändert werden. Der Exponent kann dabei eine beliebige reelle Zahl > 0 sein. Für die Größe rK(ϕ(i)) ist die exponentiell gewichtete Funktion Wrk beispielhaft wie folgt dargestellt.
Alternativ kann als Wichtungsfunktion auch die Tangenshyperbolicus Funktion verwendet werden.Alternatively, the tangency hyperbolic function can be used as the weighting function.
Übergänge zwischen den Bereichen, insbesondere im Abgriffsbereich können aber auch wie bei dem Strakplan für die Spanten eines Bootsrumpfes erfolgen, wobei die jeweiligen Querschnitte den jeweiligen Entwicklungsregeln für die Kontur unterworfen werden und die Übergangsbereiche einfach eingestrakt werden. Sehr lokal entstehen damit leicht von den Entwicklungsregeln abweichen Querschnitte, vergl. auch
Allgemein ist bei allen Querschnittsformen, also z.B. frei gezeichneten, der zugehörige Volumenstrom der jeweilige Querschnitte auch numerisch berechenbar und die Winkelposition dem entsprechenden Volumenstrom aus dem Laufrad zuordenbar.Generally, in all cross-sectional shapes, e.g. freely drawn, the corresponding volume flow of the respective cross-sections also numerically calculable and assign the angular position of the corresponding volume flow from the impeller.
Die Erfindung ist natürlich auch auf Laufräder übertragbar, deren Form von der Zylinderform abweicht, und zwar beispielsweise kegelstumpfförmige Laufräder oder Laufräder mit nahezu beliebiger Rotationskörperform. Von besonderer Bedeutung ist hierbei die räumliche Fläche der jeweiligen Hüllform an der Austrittsposition, die zur Festlegung des zugehörigen Spiralquerschnittes erforderlich ist.The invention is of course also applicable to wheels whose shape deviates from the cylindrical shape, for example, frustoconical wheels or Impellers with almost any rotational body shape. Of particular importance in this case is the spatial surface of the respective envelope shape at the exit position, which is required for fixing the associated spiral cross-section.
Die Erfindung wird im Folgenden anhand von Figuren mittels mehrerer Ausführungsbeispiele beschrieben.The invention will be described below with reference to figures by means of several embodiments.
Die Kontur des spiralförmigen Gehäuses 20 wird beispielsweise speziell bei Rechteckspiralen durch das Verhältnis der Absolutgeschwindigkeiten CM/CU festgelegt.
In
Hier entsprechen nur die zwei einströmigen Schräglippenabgriffe 150a und 150b der Erfindung.Here, only the two single-slip bevel taps 150a and 150b of the invention correspond.
Die beiden Bereiche 15a, b finden ihre Fortsetzung in der Abwicklung des Hüllzylinders 161. Der Übergangsbereich 45a der Schräglippen 40a, b erstreckt sich über 180° und ist in der
Die Beispiele der
Zur Verdeutlichung des Querschnittsaufbaus des spiralenförmigen Gehäuses wird dieses beispielsweise in einen ersten bis vierten Bereich unterteilt, die aneinander anschließen. Das spiralenförmige Gehäuse ist hierbei beispielsweise zweiströmig ausgebildet und besteht beispielsweise aus zwei Halbspiralen. Der erste und zweite Bereich 1, 2 der Ausströmung haben dieselbe Erstreckung und Übergangsfunktion über den Umfang Δϕ1 = Δϕ2 = 40°. Die beiden Spiralhälften sind somit identisch.To illustrate the cross-sectional structure of the spiral-shaped housing, this is divided, for example, into a first to fourth area, which adjoin one another. The spiral-shaped housing is in this case, for example, zweiströmig and consists for example of two half-spirals. The first and
In den
In den
Der dritte Bereich 3 ist in
Die
In
Eine perspektivische Schnittdarstellung durch die Gebläseanordnung mit einer Doppelspirale zeigt beispielsweise
Alternativ kann jedoch auch den Hauptvolumenstrom an der Stelle 470 mit einem normalen Spiralabgriff abgezweigt werden, und zwar bildet sich beispielsweise der Querschnitt 510 an der Position 490 aus. Der Einströmquerschnitt 520 erstreckt sich in diesem Fall mit Ausnahme des beginnenden Einströmquerschnittes 525 nahezu über die gesamte Breite des Hüllzylinders bLR. Die Trennung von Einströmquerschnitt 520 und Ausströmquerschnitt 530 erstreckt sich somit in axialer und radialer Richtung. Um im Bereich 540 keine Förderung durch das Laufrad 10 entsteht zu lassen, ist der an der Position 490 der Querschnitt 550 erforderlich.Alternatively, however, it is also possible to branch off the main volume flow at the
Die Abwicklung eines Hüllzylinders 440b, der in einen Förderbereich 580 für den Hauptstrom und in einen weiteren Förderbereich 590 für zwei Nebenströme 560a, b unterteilt ist beispielsweise der
In
In den
Ein axialer Querschnitt durch eine in den
Mittel des erfindungsgemäßen Schräglippenabgriff wird eine Führung des Fluid in einem engen Umfangsbereich vermieden, wodurch der Geräuschpegel der Absaugvorrichtung, insbesondere einer Dunstabzugshaube deutlich reduziert werden kann.Means of the invention Schräglippenabgriff a guidance of the fluid is avoided in a narrow peripheral area, whereby the noise level of the suction device, in particular a cooker hood can be significantly reduced.
Die Erfindung wurde voranstehend an einem Ausführungsbeispiel beschrieben, es versteht sich, dass zahlreiche Variationen und Änderungen des Anmeldungsgegenstandes möglich sind, ohne hierdurch den in den anschließenden Ansprüchen definierten Erfindungsgegenstand zu verlassen.The invention has been described above with reference to an exemplary embodiment, it being understood that numerous variations and changes of the subject of the application are possible without thereby departing from the subject matter of the invention defined in the subsequent claims.
- 1010
- LaufradWheel
- 1212
- Laufradschaufelimpeller blade
- 1313
- Motorengine
- 15a,b15a, b
- Laufradbereichimpeller area
- 1717
- radiale Richtungradial direction
- 2020
- Spiralgehäusevolute
- 3030
- normale Abgriffslippenormal tap lip
- 4040
- SchräglippeBevel lip
- 40 a,b40 a, b
- SchräglippeBevel lip
- 45 a,b,c45 a, b, c
- ÜbergangsbereichTransition area
- 47 a,b47 a, b
- einseitige Einströmungone-sided inflow
- 49 a-e49 ae
- Abströmungoutflow
- 5050
- AustrittsquerschnittOutlet cross section
- 6060
- erster Einströmraumfirst inflow space
- 7070
- Spaltgap
- 8080
- zweiter Einströmraum bzw. Ausströmraumsecond inflow space or outflow space
- 9090
- Achseaxis
- 100100
- Hüllzylinderenvelope cylinder
- 103103
- Kurve ALR(ϕ)Curve ALR (φ)
- 105105
- Abwicklung HüllzylinderSettlement envelope cylinder
- 107107
- Fläche LippenkanalArea lip channel
- 110110
- normaler Abgriffnormal tap
- 120120
- schräger Abgriffoblique tap
- 130130
- gebogener Abgriffcurved tap
- 140140
- AusströmraumtrennungAusströmraumtrennung
- 150a,b,150a, b,
- einströmige Schräglippenabgriffesingle-flow bevel lip taps
- 151, 152151, 152
- einströmige Schräglippenabgriffe über 720°, 1080°single-flow bevel taps over 720 °, 1080 °
- 160160
- zweiströmiger Schräglippenabgrifftwo-legged oblique lip tap
- 161, 162161, 162
- zweiströmiger Schräglippenabgriff - Trommelläufertwo-row bevel lip pick - drum runner
- 170170
- dreiströmiger Schräglippenabgriffthree-legged oblique lip tap
- 171-173171-173
-
Abwicklung 4 Lippenkanäle - (d.h. vierströmig)
Processing 4 lip channels - (i.e., four-flow) - 177a-c177a-c
- Lippenkanallip channel
- 180180
- Rechteckrectangle
- 185185
- Querschnitt Position fCross-section position f
- 188188
- Volumenstrom aus Fläche HüllzylinderVolumetric flow of area enveloping cylinder
- 189189
- Volumenstrom aus Integration DrallsatzVolume flow from integration swirl set
- 190190
- Viertelkreisquadrant
- 195195
- Dreiecktriangle
- 200200
- Halbkreissemicircle
- 210210
- Halbellipsehemiellipse
- 220220
- Einströmrauminflow
- 230a,b230a, b
- Kanalraumchannel space
- 240240
- frei gezeichnete Formfree drawn form
- 250250
- Führungsdornguide pin
- 260260
-
Querschnitt Ende Bereich 3Cross
section end area 3 - 270270
- Abwicklung HüllzylinderSettlement envelope cylinder
- 280280
-
Bereich 4
Area 4 - 290290
-
Bereich 1
Area 1 - 300a, b300a, b
- Austrittskanaloutlet channel
- 305305
- Halbschale Austrittskanal axiale RichtungHalf shell outlet channel axial direction
- 310310
- axiale Richtungaxial direction
- 320a-e320a-e
-
Querschnitte Bereich 4
Cross sections area 4 - 330330
- EntdrallerEntdraller
- 340340
- Doppelspiraledouble helix
- 350350
- Ansaugkanal (Halbschale)Intake channel (half shell)
- 355355
- Ansaugkanal Halbschale von obenIntake channel half shell from above
- 360360
- Lagerungstorage
- 370370
- SchräglippeBevel lip
- 380380
- Bereich 1 - BauausführungArea 1 - Construction
- 390390
- Bereich 4 - BauausführungArea 4 - Construction
- 400400
- NebenstrombereichIn addition to the electricity sector
- 410410
- HauptstrombereichMain power region
- 420420
- Verlauf SchräglippeGradient lip
- 430430
- Verlauf SchräglippeGradient lip
- 440a,b440a, b
- Abwicklung HüllzylinderSettlement envelope cylinder
- 450450
- Blasströmungblast flow
- 460460
- Erfassungsschirmcapture screen
- 470470
- Position Anfang SchräglippenabgriffPosition beginning bevel pick
- 480480
- Position Ende SchräglippenabgriffPosition end bevel pick-off
- 490490
-
Position innerhalb Übergangsbereich 540Position within
transition area 540 - 500500
- Querschnitt bei SchräglippenabgriffCross section at oblique lip tap
- 510510
- Querschnitt bei normalem SpiralabgriffCross section with normal spiral tapping
- 520520
- Einströmquerschnittinflow
- 525525
- Einströmquerschnittinflow
- 530530
- Ausströmquerschnittoutflow
- 540540
- Übergangsbereich Ausströmung HauptvolumenstromTransition area outflow Main volume flow
- 550550
-
Querschnitt ohne Einströmung in Bereich 540Cross section without inflow in
area 540 - 560 a,b560 a, b
- Nebenströmesecondary streams
- 570570
- normaler Spiralabgriffnormal spiral tap
- 580580
- Förderbereich HauptstromDelivery area main stream
- 590590
- Förderbereich NebenströmeDelivery area secondary streams
- 600 a,b600 a, b
- keilförmig angeordnete Schräglippenwedge-shaped oblique lips
- 610a,b610a, b
- NebenstromkanäleIn addition to current channels
- 620620
- HauptstromkanalMain stream channel
- 630630
- Gebläsefan
- 640640
- Dunstabzugshaube oder sonstige AbsaugeinrichtungExtractor hood or other suction device
- 641641
- Filterfilter
- 642642
- Saugraumsuction
- 643643
- Kaminfireplace
- 644644
- Abluftleitungexhaust duct
- 650650
- AusblasungBlow out
- 660 a-q660 a-q
- Kanalquerschnitt-BugspiraleChannel cross-sectional Bugspirale
- 661661
- knochenartiger Querschnittbone-like cross-section
- 662 a,b662 a, b
- schräge Schräglippeoblique oblique lip
- 665665
- bugartige Aussparungbow-shaped recess
- 666,667666.667
- Übergangsbereiche Df' und Df"Transition regions Df 'and Df "
- 668668
- Breite HüllzylinderWide envelope cylinder
- 670670
- LaufradWheel
- 680 a-f680 a-f
- Kanalquerschnitt-WendelspiraleChannel cross-section helical spiral
- 690690
- Lippenkanallip channel
- 700700
- Einströmunginflow
- 710710
- Abströmungoutflow
- 720720
- Motorengine
- 730730
- AbströmkonusAbströmkonus
- 740740
- Ringdiffusorring diffuser
- 750750
- AusgangsquerschnittOutput section
- 760 a-c760 a-c
- GehäusewandabschnittHousing wall section
Claims (11)
- A blower arrangement for turbo machines, consisting of at least one spiral-shaped housing (20) and at least one impeller (10) having blade face sides, the impeller being accommodated in the spiral-shaped housing (20) and being mounted to be rotatable about a rotational axis (90), wherein the spiral-shaped housing (20) has at least one first inflow chamber (60, 280) and at least one second inflow chamber (50, 290), in which the first inflow chamber (60, 280) and the at least second inflow chamber (50, 290) are separated from one another via at least one housing wall section (760a - 760c), in which the outer edge of the at least one housing wall section (760a - 760c) facing the impeller (10) forms a grip lip (40), in which the housing wall section (760a - 760c) extends in the direction of the inflow chambers (50, 290) and in which the first inflow chamber (60, 280) and the second inflow chamber (50, 290) are axially offset to one another, at least in sections, in relation to the rotational axis (90), wherein the beginning first inflow chamber (60, 280) and the ending second inflow chamber (50, 290) at least partially overlap one another in the region of the housing wall section (760a - 760c), and the housing wall section (760a - 760c) comprises at least one radial component (17, 310), wherein the first inflow chamber (60, 280) and the second inflow chamber (50, 290) are radially offset to one another in relation to the rotational axis (90), characterized in that the second inflow chamber (50, 290) forms at least in sections the outflow chamber for delivering the volume flow fed from the first inflow chamber (60, 280) through the spiral-shaped housing (20), wherein the first inflow chamber (60) and the outflow chamber (80) directly connect to the free blade face sides of the impeller (10) in the region of the grip lip (40), namely in the radial direction in relation to the rotational axis (90).
- The blower arrangement according to claim 1, characterized in that the housing wall section and the rotational axis (90) enclose an angle (γ) less than 90°.
- The blower arrangement according to claim 2, characterized in that the angle (γ) varies along the grip lip (40), in particular forms a bow-like housing wall section (760a - 760c).
- The blower arrangement according to any one of claims 1 to 3, characterized in that in addition to the grip lip (420, 430, 600a, b) which is running slopedly to the rotational axis (90), another grip lip (550, 570) is provided, which preferably runs parallel to the rotational axis (90).
- The blower arrangement according to any one of the claims 1 to 4, characterized in that the turbo machine is designed in a single-flow or multi-flow manner and/or in a single-entry or multi-entry manner.
- The blower arrangement according to any one of claims 1 to 5, characterized in that outflowing (49a - e, 710) is carried out in the axial, radial and/or tangential direction (49a, b, e).
- The blower arrangement according to any one of claims 1 to 6, characterized in that depending on the circumferential position (ϕ), the first inflow chamber (60, 280) and the second inflow chamber (50, 290) have a different cross-sectional shape and/or that the impeller used is a drum impeller (11) and/or that the spiral-shaped housing (20) has at least one device for swirl reduction (330, 740).
- A thrust blower for a vehicle, in particular a jet glider, comprising a blower arrangement according to any one of the preceding claims.
- The thrust blower according to claim 8, characterized in that the volume flow generated by the blower arrangement is at least partially provided for boundary layer suction and/or that the blower arrangement has a feed line (350, 355) including a device for generating a pre-swirl.
- A suction unit, in particular an extractor hood (640) comprising a blower arrangement according to any one of claims 1 to 7.
- The suction unit according to claim 10, characterized in that the blower arrangement (630) comprises a bow spiral or a helical spiral and/or that the volume flow generated by the blower arrangement (630) is at least partially provided for boundary layer suction.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102007055507A DE102007055507A1 (en) | 2007-11-21 | 2007-11-21 | Bevel lip spiral |
PCT/DE2008/001925 WO2009065394A1 (en) | 2007-11-21 | 2008-11-21 | Blower arrangement for turbo machines |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2222960A1 EP2222960A1 (en) | 2010-09-01 |
EP2222960B1 true EP2222960B1 (en) | 2015-03-18 |
Family
ID=40473470
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP08852563.9A Not-in-force EP2222960B1 (en) | 2007-11-21 | 2008-11-21 | Blower spiral volute with a discharge tongue that separates two axially offset discharge areas |
Country Status (3)
Country | Link |
---|---|
EP (1) | EP2222960B1 (en) |
DE (1) | DE102007055507A1 (en) |
WO (1) | WO2009065394A1 (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102016010216A1 (en) | 2016-08-22 | 2018-03-22 | Georg Emanuel Koppenwallner | Thrust flap for a glider, aircraft or ground effect vehicle |
Families Citing this family (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102010023017A1 (en) | 2010-06-08 | 2011-12-08 | Georg Emanuel Koppenwallner | Humpback whale blower, method for locally improving the flow in turbomachinery and vehicles |
JP5433560B2 (en) * | 2010-12-27 | 2014-03-05 | 三菱重工業株式会社 | Turbine scroll part structure |
WO2016147032A1 (en) * | 2015-03-13 | 2016-09-22 | Vata Korkut | An ultra-high rpm rotatory system for propulsion in the vacuum of space |
CN109642585A (en) * | 2016-09-02 | 2019-04-16 | 惠普发展公司, 有限责任合伙企业 | Blower-casting for noise reduction |
DE102017217759B3 (en) | 2017-10-06 | 2019-03-28 | Ford Global Technologies, Llc | Supercharged internal combustion engine with turbocharger and electrically driven compressor |
Family Cites Families (18)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE310721C (en) | ||||
DE319721C (en) * | 1920-03-15 | Ludwig Hartwagner | Centrifugal fan with worm housing | |
DE469827C (en) | 1924-03-05 | 1928-12-27 | Wilhelm Beck Dipl Ing | Centrifugal pump or blower |
US2405048A (en) * | 1944-11-18 | 1946-07-30 | Gen Electric | Centrifugal compressor |
US3243102A (en) * | 1963-12-20 | 1966-03-29 | Kenton D Mcmahan | Centrifugal fluid pump |
DK118475B (en) * | 1965-08-02 | 1970-08-24 | Nordisk Ventilator | Radial fan with axial outflow. |
DE3028606A1 (en) * | 1980-07-28 | 1982-03-04 | Wilhelm Gebhardt Gmbh, 7112 Waldenburg | FOR INSTALLATION IN PIPELINES, CHANNELS OR CHANNEL-LIKE HOUSINGS OR. FAN UNIT DETERMINED IN VENTILATION AND AIR CONDITIONING |
JPS57181999A (en) * | 1981-05-01 | 1982-11-09 | Mitsubishi Heavy Ind Ltd | Turbo machine |
JPS58117393A (en) * | 1981-12-31 | 1983-07-12 | Matsushita Electric Ind Co Ltd | Fan |
DE3706772A1 (en) * | 1987-03-03 | 1988-09-15 | Gebhardt Gmbh Wilhelm | FAN UNIT AND METHOD FOR PRODUCING THE GUIDING BLADES OF SUCH A FAN UNIT |
US5156524A (en) | 1990-10-26 | 1992-10-20 | Airflow Research And Manufacturing Corporation | Centrifugal fan with accumulating volute |
DE4313617C2 (en) | 1993-04-26 | 1996-04-25 | Kreis Truma Geraetebau | Radial fan |
DE4331606C1 (en) | 1993-09-17 | 1994-10-06 | Gutehoffnungshuette Man | Spiral housing for turbo-engines (rotary engines, turbomachines) |
DE19811877C2 (en) | 1998-03-18 | 2001-09-13 | Motoren Ventilatoren Gmbh | Radial fan |
DE19957962B4 (en) | 1999-05-19 | 2009-01-29 | Röhl-Hager, Hannelore | Method and apparatus for confining, capturing and exhausting fluid media |
FR2825142B1 (en) * | 2001-05-22 | 2003-08-29 | Conseils Etudes Et Recherches En Gestion De Lair Cerga | FAN INTENDED TO BE ASSOCIATED WITH AN AIR EXHAUST DUCT OUTSIDE AT LEAST ONE PREMISES |
DE10300621B4 (en) | 2003-01-10 | 2008-08-21 | Georg Emanuel Koppenwallner | Jet propulsion method e.g. for a glider |
DE102004024392A1 (en) | 2004-05-17 | 2005-12-08 | Institut für Leistungselektronik und Regelungstechnik Universität Stuttgart | Winding and groove configuration for electrical machine, has superconductor combining with groove winding and shield that shields teeth against magnetic leakage flux, where different superconducting materials are used for winding and shield |
-
2007
- 2007-11-21 DE DE102007055507A patent/DE102007055507A1/en not_active Ceased
-
2008
- 2008-11-21 EP EP08852563.9A patent/EP2222960B1/en not_active Not-in-force
- 2008-11-21 WO PCT/DE2008/001925 patent/WO2009065394A1/en active Application Filing
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102016010216A1 (en) | 2016-08-22 | 2018-03-22 | Georg Emanuel Koppenwallner | Thrust flap for a glider, aircraft or ground effect vehicle |
Also Published As
Publication number | Publication date |
---|---|
EP2222960A1 (en) | 2010-09-01 |
WO2009065394A1 (en) | 2009-05-28 |
DE102007055507A1 (en) | 2009-06-04 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
DE69114647T2 (en) | Axial flow blower. | |
EP2222960B1 (en) | Blower spiral volute with a discharge tongue that separates two axially offset discharge areas | |
EP1508669B1 (en) | Stator vanes ring for a compressor and a turbine | |
DE102008011645A1 (en) | Turbomachine with rotors with low rotor outlet angles | |
DE2632155C3 (en) | Gas turbine jet engine | |
DE102007056953B4 (en) | Turbomachine with Ringkanalwandausnehmung | |
DE102011017419A1 (en) | Deflection unit for a gas flow in a compressor and compressor containing them | |
EP2024606A1 (en) | Annular flow duct for a turbomachine through which a main flow can flow in the axial direction | |
WO2019063384A1 (en) | Diffuser for a compressor | |
CH710476A2 (en) | Compressor with a Axialverdichterendwandeinrichtung to control the leakage flow in this. | |
EP2881548B1 (en) | Gas turbine compressor | |
DE102015111746A1 (en) | Cooled turbine wheel, in particular for an aircraft engine | |
DE102014212910A1 (en) | Flow deflection in a turbomachine | |
EP1865148B1 (en) | Flow machine with rotors with a high specific energy transfer | |
EP3568597B1 (en) | Return stage and radial turbo fluid energy machine | |
EP3682119A1 (en) | Diffuser for a radial compressor | |
EP3390832B1 (en) | Backfeed stage of a radial turbo fluid energy machine | |
DE102014212909A1 (en) | Flow deflection in a turbomachine | |
DE102015014900A1 (en) | Radial turbine housing | |
DE102017114007A1 (en) | Diffuser for a centrifugal compressor | |
DE102009012132A1 (en) | Exhaust gas turbine for internal combustion engine of e.g. passenger car, has adjustable guide vane arranged in upstream of rotor blade in flow passage and rotated at point of variable cross section along longitudinal axis | |
DE202018101699U1 (en) | Turbine with adjusting ring | |
DE102019213932B4 (en) | Airend with variable stator blade inclination | |
WO2019034313A1 (en) | Mixed-flow turbine for a turbocharger | |
DE102008039285A1 (en) | Compressor for an internal combustion engine |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
PUAI | Public reference made under article 153(3) epc to a published international application that has entered the european phase |
Free format text: ORIGINAL CODE: 0009012 |
|
17P | Request for examination filed |
Effective date: 20100322 |
|
AK | Designated contracting states |
Kind code of ref document: A1 Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MT NL NO PL PT RO SE SI SK TR |
|
AX | Request for extension of the european patent |
Extension state: AL BA MK RS |
|
DAX | Request for extension of the european patent (deleted) | ||
17Q | First examination report despatched |
Effective date: 20111003 |
|
GRAP | Despatch of communication of intention to grant a patent |
Free format text: ORIGINAL CODE: EPIDOSNIGR1 |
|
INTG | Intention to grant announced |
Effective date: 20141017 |
|
GRAS | Grant fee paid |
Free format text: ORIGINAL CODE: EPIDOSNIGR3 |
|
GRAA | (expected) grant |
Free format text: ORIGINAL CODE: 0009210 |
|
AK | Designated contracting states |
Kind code of ref document: B1 Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MT NL NO PL PT RO SE SI SK TR |
|
REG | Reference to a national code |
Ref country code: GB Ref legal event code: FG4D Free format text: NOT ENGLISH |
|
REG | Reference to a national code |
Ref country code: CH Ref legal event code: EP |
|
REG | Reference to a national code |
Ref country code: IE Ref legal event code: FG4D Free format text: LANGUAGE OF EP DOCUMENT: GERMAN |
|
REG | Reference to a national code |
Ref country code: AT Ref legal event code: REF Ref document number: 716771 Country of ref document: AT Kind code of ref document: T Effective date: 20150415 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R096 Ref document number: 502008012789 Country of ref document: DE Effective date: 20150430 |
|
REG | Reference to a national code |
Ref country code: NL Ref legal event code: VDEP Effective date: 20150318 |
|
REG | Reference to a national code |
Ref country code: NL Ref legal event code: VDEP Effective date: 20150318 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: HR Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150318 Ref country code: NO Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150618 Ref country code: FI Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150318 Ref country code: LT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150318 Ref country code: SE Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150318 |
|
REG | Reference to a national code |
Ref country code: LT Ref legal event code: MG4D |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: LV Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150318 Ref country code: GR Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150619 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R084 Ref document number: 502008012789 Country of ref document: DE |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: NL Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150318 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: SK Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150318 Ref country code: EE Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150318 Ref country code: PT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150720 Ref country code: RO Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150318 Ref country code: ES Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150318 Ref country code: CZ Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150318 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: PL Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150318 Ref country code: IS Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150718 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R097 Ref document number: 502008012789 Country of ref document: DE |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: IT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150318 |
|
PLBE | No opposition filed within time limit |
Free format text: ORIGINAL CODE: 0009261 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: DK Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150318 |
|
26N | No opposition filed |
Effective date: 20151221 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: SI Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150318 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: LU Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20151121 Ref country code: MC Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150318 |
|
REG | Reference to a national code |
Ref country code: CH Ref legal event code: PL |
|
GBPC | Gb: european patent ceased through non-payment of renewal fee |
Effective date: 20151121 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: CH Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20151130 Ref country code: LI Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20151130 |
|
REG | Reference to a national code |
Ref country code: IE Ref legal event code: MM4A |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: ST Effective date: 20160729 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: IE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20151121 Ref country code: GB Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20151121 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: FR Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20151130 |
|
REG | Reference to a national code |
Ref country code: AT Ref legal event code: MM01 Ref document number: 716771 Country of ref document: AT Kind code of ref document: T Effective date: 20151121 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: AT Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20151121 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: BG Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150318 Ref country code: HU Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO Effective date: 20081121 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: CY Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150318 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: BE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20151130 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: TR Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150318 Ref country code: MT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150318 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: DE Payment date: 20171130 Year of fee payment: 10 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R119 Ref document number: 502008012789 Country of ref document: DE |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: DE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20190601 |