EP2577071B1 - Canal à surface de guidage d'écoulement - Google Patents

Canal à surface de guidage d'écoulement Download PDF

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Publication number
EP2577071B1
EP2577071B1 EP11722448.5A EP11722448A EP2577071B1 EP 2577071 B1 EP2577071 B1 EP 2577071B1 EP 11722448 A EP11722448 A EP 11722448A EP 2577071 B1 EP2577071 B1 EP 2577071B1
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EP
European Patent Office
Prior art keywords
flow
diffuser
channel
fluid
section
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Not-in-force
Application number
EP11722448.5A
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German (de)
English (en)
Other versions
EP2577071A2 (fr
Inventor
Dieter Wurz
Stefan Hartig
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ESG MBH
Original Assignee
ESG MBH
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
Priority claimed from DE102010022418A external-priority patent/DE102010022418A1/de
Priority claimed from DE102010024091A external-priority patent/DE102010024091B4/de
Priority claimed from DE201110012039 external-priority patent/DE102011012039A1/de
Application filed by ESG MBH filed Critical ESG MBH
Priority to PL11722448T priority Critical patent/PL2577071T3/pl
Publication of EP2577071A2 publication Critical patent/EP2577071A2/fr
Application granted granted Critical
Publication of EP2577071B1 publication Critical patent/EP2577071B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15D—FLUID DYNAMICS, i.e. METHODS OR MEANS FOR INFLUENCING THE FLOW OF GASES OR LIQUIDS
    • F15D1/00—Influencing flow of fluids
    • F15D1/02—Influencing flow of fluids in pipes or conduits
    • F15D1/025—Influencing flow of fluids in pipes or conduits by means of orifice or throttle elements
    • 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
    • F04D29/52—Casings; Connections of working fluid for axial pumps
    • F04D29/54—Fluid-guiding means, e.g. diffusers
    • F04D29/541—Specially adapted for elastic fluid pumps
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B01—PHYSICAL OR CHEMICAL PROCESSES OR APPARATUS IN GENERAL
    • B01F—MIXING, e.g. DISSOLVING, EMULSIFYING OR DISPERSING
    • B01F35/00—Accessories for mixers; Auxiliary operations or auxiliary devices; Parts or details of general application
    • B01F35/50—Mixing receptacles
    • B01F35/53—Mixing receptacles characterised by the configuration of the interior, e.g. baffles for facilitating the mixing of components
    • B01F35/531—Mixing receptacles characterised by the configuration of the interior, e.g. baffles for facilitating the mixing of components with baffles, plates or bars on the wall or the bottom
    • 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
    • F04D29/52—Casings; Connections of working fluid for axial pumps
    • F04D29/54—Fluid-guiding means, e.g. diffusers
    • F04D29/541—Specially adapted for elastic fluid pumps
    • F04D29/545—Ducts
    • 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
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/68—Combating cavitation, whirls, noise, vibration or the like; Balancing by influencing boundary layers
    • F04D29/681—Combating cavitation, whirls, noise, vibration or the like; Balancing by influencing boundary layers 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
    • F04D29/00—Details, component parts, or accessories
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/68—Combating cavitation, whirls, noise, vibration or the like; Balancing by influencing boundary layers
    • F04D29/681—Combating cavitation, whirls, noise, vibration or the like; Balancing by influencing boundary layers especially adapted for elastic fluid pumps
    • F04D29/684—Combating cavitation, whirls, noise, vibration or the like; Balancing by influencing boundary layers especially adapted for elastic fluid pumps by fluid injection
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15D—FLUID DYNAMICS, i.e. METHODS OR MEANS FOR INFLUENCING THE FLOW OF GASES OR LIQUIDS
    • F15D1/00—Influencing flow of fluids
    • F15D1/001—Flow of fluid from conduits such as pipes, sleeves, tubes, with equal distribution of fluid flow over the evacuation surface
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2250/00—Geometry
    • F05D2250/50—Inlet or outlet
    • F05D2250/52—Outlet

Definitions

  • the task is to homogenize flow and state fields in fluid flows.
  • One reason for this is that the inhomogeneity of the velocity distribution in a fluid behind a system component can lead to increased pressure losses or to vibration excitation in subsequent system components.
  • inhomogeneous temperature and concentration fields in fluids can cause corrosion damage. Therefore, in some cases, regardless of the task of homogenizing the velocity distribution, the goal is to homogenize the field of state variables in a flowing fluid.
  • this fluid we refer to this fluid as the primary fluid.
  • a carrier gas suspended particulate additives which we call a secondary fluid
  • a secondary fluid as homogeneously as possible in the basic flow of a primary fluid.
  • a hotter gas should be mixed as a secondary fluid in the primary fluid, for. B. to reduce a load of the primary fluid with drops by evaporation.
  • only a relatively short running distance of the flow of the primary fluid is available for coping with this mixing task. It is known that the shorter the available mixing distance, the higher the pressure loss that the primary fluid suffers in a mixer.
  • the US 5 335 501 A describes a flowed through by a fluid channel portion with cross-sectional widening in the flow direction.
  • the channel section internals are arranged, through which the channel cross-section is divided into at least 3 sub-channels.
  • the displacement thickness of at least part of the internals increases in the flow direction.
  • From the EP 0 414 021 A2 is an inductive passage with at least one slot-shaped inlet opening and at least two outlet openings, which are bounded on sides facing each other by a bluff body, which adapted in its plan the cross-section of the inlet opening and, following the flow direction, arranged at a perpendicular distance to the plane of the inlet opening is, wherein two sheet metal plates, one of which forms a frame for the inlet opening and the other each form a frame for the outlet openings, wherein for the production of the inlet opening, the one sheet metal plate is provided with a double-T-shaped slot and the two thereby resulting tongues are each bent in the direction of an outlet opening and wherein the formation of the outlet openings, the other metal plate is provided with two U-shaped slots and the two resulting tongues are angled in the direction of the inlet opening.
  • an exhaust gas outlet channel which serves for the regulation and orientation of an air flow, wherein the cross section of the exhaust gas outlet channel widens in the flow direction.
  • a handset which represents the closure, has a pyramidal shape and divides the cross section of the exhaust gas outlet channel into two sub-channels, wherein the displacement thickness of the mobile part 7 increases in the flow direction.
  • the ring diffuser 1 here consists of a slightly widening conical housing 2 and a cylindrical inner body 3, also called hub body, which has a blunt end face 4, so that here a sudden cross-sectional widening is generated, which corresponds to a Carnot shock diffuser.
  • the hub body 3 is centered over more or less star-shaped radially oriented sheets 5 and 6 in two axial positions 7 and 8.
  • the sheets 5 can be executed curved as Nachleitschaufeln the blower, with the aim to reduce the swirl in the outflow of the primary fluid from the blades and thus to achieve a largely axial flow through the following component.
  • the ring diffuser 1 is followed in this example by a short cylindrical channel section 12 and a 90 ° bend 13.
  • the manifold is equipped with a guide grille 14. Since an aerodynamically optimized Krümmerleitgitter has a relevant pressure loss, it acts in some situations as a flow field gleichmä calldes throttle grid.
  • the axial velocity distribution 15 of the primary fluid has at the entrance into the ring diffuser 1 behind the blades 11 of an axial fan, in particular at high aerodynamic load relatively high overspeed, the maximum velocity 16 is shifted to a larger radius r vmax .
  • Inner friction in the highly turbulent flow field of the primary fluid uniforms the velocity distribution in the slim-line annular diffuser 1 shown here and thus reduces the maximum velocity 16.
  • a turbulent equilibrium velocity profile would develop characterized by large velocity gradients near the wall.
  • the maximum velocity 16 of the output profile 15 is largely degraded, and the conversion of the profile 15 into the profile 18 results in an increase in the static pressure in the direction of flow of the primary fluid, commonly referred to as pressure recovery, although the process of flow delay is, of course, associated with total pressure loss.
  • Fig. 2 shows a second ring diffuser configuration 19 according to the prior art, which is characterized by a much stronger cross-sectional widening in the direction of flow of the primary fluid.
  • the outer boundary 2 as already in the configuration Fig. 1 designed as a conically weakly divergent housing.
  • the hub body 3 is designed convergent in two sections 20 and 21 in the flow direction, as can be seen from the literature.
  • the velocity distribution 15 shown here which is characterized by low flow velocities near the wall, or more precisely by low velocity gradients and thus by a low wall shear stress TW
  • the flow along the hub body does not cope with the pressure increase in the flow direction in the illustrated example, and it comes to Flow separation with scrubströmzonen 40. In this case, if necessary achieved a low pressure recovery.
  • the slimmer diffuser according to Fig. 1 can then be superior in terms of flow technology with regard to the achievable pressure recovery.
  • Fig. 3 shows another configuration, which differs from that according to Fig. 2 differs in that a throttle grid 22, which may be constructed of rods 24, is installed in the region of the rear end 23 of the hub body.
  • a throttle grid 22 which may be constructed of rods 24, is installed in the region of the rear end 23 of the hub body.
  • This throttle grid may be configured as a so-called gradient grid, whereby an adaptation to the velocity distribution of the flow of the primary fluid at the entrance to the ring diffuser is possible. If flow separation nevertheless occurs in an intermediate section despite the installation of the throttle grille, the flow to the throttle grille re-adjoins the field boundaries.
  • Such a throttle grate suffers from two negative characteristics: it generates a considerable pressure loss. It only causes a small-scale mixing, which corresponds approximately to the mesh size of the grid.
  • the main advantage is a homogenization of the velocity distribution upstream of the downstream components, so that, for example, the pressure loss in a downstream manifold or in a register silencer scenes can be significantly reduced.
  • the present invention relates to a channel section through which a primary fluid flows with a cross-sectional widening in the flow direction and with internals, by which the channel cross section is divided into at least two subchannels, the displacement thickness of at least a portion of the internals increasing in the flow direction, the channel section comprising a slender fan diffuser having an opening angle in the range of 10 ° to 20 °, on which is followed by a greatly expanded channel section with an opening angle in the range of 20 ° to 120 °, wherein the internals are designed as radially extending V-shaped gusset plates in the greatly expanded channel section.
  • essentially radially extending V - shaped gusset plates are installed in the greatly expanded passage section, as in FIG Fig. 13 and 15 the present extension is shown.
  • This embodiment according to the invention offers in particular the large blowers for power plants with a diffuser diameter of about 5 m decisive advantages in terms of manufacturing costs.
  • V-shaped radial gussets it is additionally possible to provide guide vanes which support an allocation of the flow to the following cross-section.
  • These concentric to the diffuser main axis baffles must then be performed but not necessarily thickened in the flow direction and thus to the trailing edge. Rather, they may consist of rolled and double-curved thin-walled sheet metal ring sections, which are inexpensive to produce and require only a small additional weight.
  • the concentric displacement body which are thickened towards the trailing edge and the radially extending V-shaped gusset plates. It may be sufficient and even advantageous to install the concentric displacement body 49 only in the end portions of the V - shaped gusset plates.
  • the radially extending gussets which are made hollow for weight reasons, can be used for the supply of a secondary fluid to be mixed in the primary fluid.
  • Each gusset would then be assigned an inlet nozzle, Fig. 15 , The entirety of the nozzle would be acted upon via a not shown here ring line with the secondary fluid.
  • the task is to homogenize flow and state fields in fluid flows.
  • One reason for this is that the inhomogeneity of the velocity distribution in a fluid behind a system component can lead to increased pressure losses or to vibration excitation in subsequent system components.
  • inhomogeneous temperature and concentration fields in fluids can cause corrosion damage. Therefore, in some cases, regardless of the task of homogenizing the velocity distribution, the goal is to homogenize the field of state variables in a flowing fluid, referred to herein as primary fluid 41.
  • the primary fluid may comprise a liquid or a gas or a mixture.
  • wing-like vanes are shown, which provide an improved supply of the near-field flow field with impulse from higher-velocity zones away from the wall, without the need for a strong turbulence in the flow. Rather, fluid is scavenged as smoothly as possible from a zone with high flow velocity with the aid of aerodynamically optimized guide elements and introduced as a low-turbulence overspeed jet into the impulse-weak zones.
  • this basic principle can also be used to impulse the boundary layer on the outer wall of the diffuser, if necessary. Although this is usually not necessary with regard to avoiding flow separation on the housing wall. However, if at the entrance to the channel extension, which follows on the blower diffuser, a homogeneous velocity profile as possible to be generated, it makes sense to accelerate the wall boundary layer on the housing by feeding subsets of the pulse-rich wall remote flow.
  • Axial yorksprofil is further on each of the radially extending blades of the Nachleitrades a pulse-depleted flow wake zone ("dead water”) to determine.
  • the flow also tends to increase in a slender diffuser for flow separation from the walls. If there is a strongly divergent channel extension on the slender fan diffuser, flow separation is more likely to occur without suitable remedial measures.
  • Diffusers are channel sections with a reduction in the flow velocity in Main flow direction. In subsonic flows diffusers are characterized by an extension of the flow cross-section in the flow direction. Diffusers can be designed very differently. The simplest case is a centrically symmetrical Kreis lakediffusor, which consists only of a centric symmetric and conically divergent outer housing and is therefore designed without hub body. In such circular area diffusions, the degree of slimming is described by the total opening angle 2 x ⁇ of the tapered housing.
  • the degree of slimming or the effective opening angle are determined as follows:
  • the axial profile of the free flow cross section of the annular space between hub and housing is converted into the axial profile of the cross section in the case of a circular area diffuser.
  • This circular area diffuser is referred to as a spare circular area diffuser for the ring diffuser.
  • the opening angle of the Reason Vietnamese Bengaldiffusors then serves as a measure of the slenderness.
  • a slim diffuser is used when the replacement circular diffuser has a total opening angle of 2 ⁇ ⁇ ⁇ 10 ° to 20 °.
  • the opening angle of the Reasonnikviddiffusors is also referred to as the effective opening angle of the diffuser.
  • a channel in which a fluid is conductive, wherein the channel is bounded by channel walls, wherein the channel walls an inlet opening and a Have outlet opening through which the fluid can enter the channel and can leave the channel.
  • the fluid has a flow velocity which is smaller along the channel walls than outside the immediate wall friction layer than in the middle of the channel, so that a zone of higher flow velocity and a zone of lower flow velocity can be formed in the channel, wherein in the channel a flow guide surface is arranged, by means of which Part of the fluid from the zone of higher flow velocity can be abschöpfbar and in the zone of lower flow velocity can be mixed.
  • the fluid may comprise a liquid or a gas or a mixture.
  • the channel walls span a cross-sectional area according to an embodiment, wherein the channel has a portion whose cross-sectional area increases in the flow direction.
  • the cross-sectional area may be circular or annular.
  • a plurality of flow guide surfaces are arranged in the channel.
  • the flow guide can be arranged side by side.
  • the flow guide surface can be arranged in the section whose cross-sectional area increases in the flow direction.
  • the channel is designed as a ring diffuser for an axial fan with guide vanes.
  • the flow guide surface can be designed in particular as a guide blade.
  • the vane may include an auxiliary vane that extends downstream from the trailing edge of the vane.
  • the section has a first section with an opening angle in the range of 10 ° to 20 °, to which a second section adjoins with an opening angle in the range of 20 ° to 120 °.
  • first or second sections is at least one hollow body, in particular a radially extending wedge-shaped hollow body arranged.
  • a plurality of wedge-shaped hollow bodies may be provided, in particular at least 3 wedge-shaped hollow bodies may be provided.
  • the effective opening angle in the sub-channels between the wedge-shaped hollow bodies may be of the order of 0 ° to 18 °. In rare cases, especially with a particularly unfavorable velocity distribution at the inlet to the diffuser, an acceleration of the flow in partial channels or partial sections of a diffuser with guide surfaces according to the invention may also be advantageous. Then the effective opening angle would be negative in these sections.
  • the wedge-shaped hollow bodies can end on a ring, which is arranged concentrically around its center axis in a section designed as a ring diffuser. Along the center axis, a hub may be arranged.
  • the wedge-shaped hollow body can also end on a ring which encloses the hub of the ring diffuser concentric. Between the hollow bodies concentric baffles can be drawn to the center axis of the channel.
  • a second fluid may be introduced into the channel.
  • the second fluid can be introduced into the fluid via nozzles in the vicinity of the flow guide surfaces.
  • the second fluid can be introduced into the hollow body, wherein the hollow body contain openings to inject the second fluid into the fluid.
  • inventions may refer to a slim diffuser, which is usually located immediately behind an axial fan. Subsequently, embodiments will be described, which may find application in a subsequent greatly expanded channel section.
  • Fig. 6 of the DE 10 2010 024 091 shown in the diffuser already in the region near the trailing edge of the Fan guide vanes (trailing edge)
  • Submersible vanes installed. They can be placed on the trailing edges of the existing fan guide vanes, see Fig. 13 and Fig. 16 of the present invention. In principle, however, attachment of these auxiliary guide vanes to the diffuser wall or to the diffuser hub is also possible. These weakly curved auxiliary vanes are made slightly towards the housing wall or towards the hub.
  • the pulse is fed into the flow boundary layer.
  • a velocity profile sets in at the diffuser inlet, which is characterized by high wall-near flow velocities.
  • the near-wall velocity maximum could initially be even higher than the velocity in the middle of the ring diffuser, see Fig. 14 , It is quite advantageous if the flow boundary layer has a certain momentum surplus, because it not only has to cope with the pressure increase of the diffuser, but also overcome the wall friction forces.
  • the course of the channel between the wing and the diffuser housing in the flow direction here is not divergent, but designed to be slightly convergent, because in this embodiment, the impulse is not to be fed into the near-nip area, but in the boundary layer on the housing wall.
  • a first ring of such wings is associated with the housing wall of the diffuser.
  • a second ring is assigned to the hub of the diffuser, provided it is a ring diffuser. How large the number of wings on the outer and on the inner ring should be, can not yet be reliably predicted. It could be advantageous to match the number of vanes on these rings to the number of Nachleitschaufeln the axial fan. Since there is a certain backlog and thus also deflecting flows at the leading edges of these wing-like guide elements, which are positioned in regions with high flow velocity, an overbending of the skeleton line of these wings can be advantageous in order to ensure a low-loss, shock-free flow.
  • the outer contour of an airfoil can be constructed by superimposing the radius profile of a circle of circles, whose centers lie on the skeleton line, to a skeleton line as the center line of a body. The envelope of the circle then forms the contour of the wing.
  • an airfoil or a wing-like guide element are arranged such that the tangent to the skeleton line in the region of the profile nose runs parallel to the direction of the undisturbed flow v ⁇ at a greater distance from the profile nose.
  • the effect of the guide element can be compensated for the direction of the flow by means of an overbending of the skeleton line.
  • These wings or guide elements can in turn be designed as low-turbulence mixing elements.
  • the mixed-in second fluid can be passed via an outer ring line on the housing wall side facing the wing, Fig. 14 , From here it is mixed into the deliberately low-turbulence wake flow.
  • the second fluid can also be supplied via the hollow hub to the inner ring of wings assigned to this hub.
  • the slender fan diffuser usually follows a greatly expanding channel section, which leads to a dimensioned in the usual way flue gas duct or to a housing in which, for example, silencer scenes can be installed. While the mean flow velocities at the outlet of the diffuser of a large axial blower are in a range of approximately 40-60 m / s, the mean flow velocities in flue gas ducts are only approximately 20 m / s. This speed reduction is useful to keep the flow losses in the flue gas ducts and in particular in Kanalalkrümmern within reasonable limits. If, on the other hand, a silencer directly follows an axial fan, the flow velocity in the channel extension must be reduced even further.
  • the silencer scenes cause a cross-sectional obstruction of about 50%.
  • the flow velocity in the relatively long channels between adjacent scenes is not too high, which would lead to increased pressure losses and noise generation on the silencer scenes, you reduced the void space or the Anström 1954 the scenes to about 12 m / s.
  • the aim is to realize these speed reductions with the lowest possible total pressure losses and the greatest possible static pressure gain.
  • a relevant deceleration of the high-momentum flow would cause such a strong increase in pressure that the impulse-weak zones could not flow up the pressure mountain generated in said high-pulse zones. This would result in a very disadvantageous velocity distribution in the outflow from the greatly expanded channel section and thus an unfavorable flow of a subsequent component.
  • constant pressure refers not to the pressure profile in the flow direction, but to the synchronization of the pressure increase in the adjacent sub-channels.
  • the invention relates to a channel carrying a fluid, in particular a channel carrying a primary fluid with a more or less pronounced inhomogeneous velocity distribution and / or distribution of the state variables of the primary fluid and with a subsequent flow diffuser and optionally an adjoining one highly dilating channel portion, wherein flow control surfaces are arranged in the channel, are skimmed through the subsets of the primary fluid from zones at high speed and mixed into zones at low speed.
  • the channel carrying the primary fluid has an annular cross-section and a largely centrically symmetrical velocity distribution with a more or less pronounced maximum velocity, wherein in the annulus cross-section flow control surfaces are arranged in zones with high flow velocity, skimmed by the subsets of the primary fluid and in zones with lower Speed are mixed.
  • the flow guide can be mounted on at least one ring between radially arranged swords.
  • a primary duct leading annular channel in particular a ring diffuser is provided, which is arranged behind an axial fan with Nachleitschaufeln, wherein in zones of high flow rate auxiliary vanes at the trailing edges of the Nachleitschaufeln or in the vicinity of the trailing edges of the guide vanes on the housing of the diffuser or the hub are mounted such that subsets of the primary fluid from high-speed zones are skimmed off and fed into the slower flow boundary layers on the housing and hub.
  • the channel is part of an axial fan with guide vanes, in particular, the channel is a ring diffuser behind an axial fan with guide vanes. Between the diffuser inlet and diffuser outlet guide vanes are arranged, through the subsets of the primary fluid High velocity zones are fed into slower flow boundary layers.
  • the ring diffuser behind an axial fan with guide vanes has a slightly divergent diffuser with an effective opening angle of about 10 ° - 18 °.
  • the weakly divergent diffuser can be followed by a strong channel widening with a geometric opening angle of approx. 15 ° -120 °.
  • this channel extension at least 3 relative to the main axis approximately radially aligned and wedge-shaped in the flow direction hollow body can be installed.
  • the effective opening angle in the sub-channels between the wedge-shaped hollow bodies may be on the order of about 0 ° - 18 °.
  • the wedge-shaped hollow body can end on a ring which concentrically surrounds the hub of the ring diffuser. Between the hollow bodies concentric baffles can be drawn to the diffuser axis.
  • a secondary fluid is introduced via nozzles in the vicinity of the wings in the primary fluid.
  • a secondary fluid can be introduced into the wedge-shaped hollow body and be blown from here through openings in the primary fluid.
  • a ring diffuser is provided with a concentric ring of vanes, wherein the concentric ring of vanes divides the ring diffuser into two concentric rings of approximately equal area size and the vanes alternately direct the primary fluid flow outwardly toward the housing wall and inwardly toward the housing wall Hub lead.
  • FIG. 5 show a solution.
  • Fig. 4 shows a longitudinal section through the outlet region of an axial fan 9 with a downstream ring diffuser 1
  • Fig. 5 a cross section AB through the front portion of the ring diffuser with projection in the axial direction.
  • wing-like flow guide surfaces 24 are installed in the middle section of the diffuser. However, these do not extend as ring guide surfaces over the entire circumference, but cover only shorter sections of the circumference, as from Fig. 5 can be seen.
  • the flow guide surfaces 24 are equipped with so-called tip wings 25, which dampen the formation of swirl pegs in the wake of the wing tips, as is known from the wings of large aircraft.
  • the wing sections 24 are more or less radial over the tip wings extending swords 26 so fastened that their angular position ⁇ can be adjusted at a standstill.
  • the swords 26 are attached here to the hub body. However, they could also be mounted on the outer housing 2.
  • a secondary gaseous fluid 32 which is to be mixed into the primary gaseous fluid 35, is supplied via a pipeline 31 to the interior of the hub body 20 or 21. From here, it is injected through nozzles 33 and 34 at an adapted rate into the primary fluid, so that it is optimally involved in the mixing process generated by the flow directors.
  • the hydrofoil-shaped flow guide surfaces can also be embodied as hollow profiles, which are supplied with secondary fluid via the swords 26, which is then blown or mixed into the primary fluid via bores at the trailing edge of the guide surfaces 24.
  • the outflow from the impeller of a blower or compressor still has a significant swirl component or peripheral component.
  • the flow tends increasingly to flow separation from the hub.
  • the swords 26 can serve as rectifier surfaces. With strongly twisted flows, it makes sense to curve the leading edges of the swords such that a largely shock-free and thus aerodynamically optimized flow of the primary fluid is achieved.
  • the radial supports 5 in Fig. 1 or 4 it is preferable that the radial supports 5 in Fig. 1 or 4 to perform as flow baffles.
  • blower diffuser which is basically carried out with a small opening angle, followed by a strong cross-sectional widening with a large opening angle, z.
  • blower diffuser As in front of a heat exchanger or in front of a register of silencer backdrops, it may be useful to incorporate additional wing-shaped vanes, through whose effect the flow field assumes the strong cross-sectional extension without flow separation.
  • the ring diffuser 1 here consists of a slightly widening conical housing 2 and a cylindrical inner body 3, also called hub body, which has a blunt end surface 4, so that here in the central region an abrupt cross-sectional widening is generated, which corresponds to a Carnot shock diffuser.
  • the Nabentotwasser 13 connects.
  • the hub body 3 is centered over more or less star-shaped - radially aligned sheets 5 and 6 in two axial positions 7 and 8.
  • the sheets 5 can be designed to be curved as guide vanes of the blower, with the aim of reducing the swirl in the coordination of the primary fluid 41 from the rotor blades 11 and thus to achieve a largely axial flow through the following component.
  • the radial plates 6 at the diffuser end sometimes referred to as swords, are usually designed without curvature with axial alignment.
  • the averaged over the channel cross-section flow rate of about 80 m / s as still prevails behind impeller 10 or behind the Nachleitrad 5 in section 2.1, to an average of about 45 m / s in section 2.2 reduced.
  • the velocity distribution 15 at the diffuser inlet 2.1 shows a pronounced maximum, which results in a larger radius r Vmax. 2.1 can be relocated.
  • a lightly loaded diffuser which must be designed with a small opening angle, there is a considerable static pressure recovery with only a slightly decreasing total pressure.
  • the aim of the present invention is to provide the necessary compensation operations in a greatly expanded channel section at a small distance to the subsequent component, for. B. a slotted silencer to reduce required pressure losses as much as possible.
  • the possibility should be created to interfere with a secondary fluid 42 in this area in the primary fluid 41, especially since this succeeds with little additional pressure losses.
  • a distribution grid for the secondary fluid Of course, you could also feed the secondary fluid via a downstream separate mixer in the primary fluid. But such an additional component is expensive and causes additional pressure losses.
  • Fig. 7 shows a solution. It represents a longitudinal section through the outlet region of an axial fan 9 with a downstream ring diffuser 1, a greatly expanded channel section 18 and a register of silencer gates 20 in a housing 40.
  • the ring diffuser 1 can in a classical manner or using the principles according to the German patent application DE 10 2010 022 418 be executed.
  • annular displacement bodies 21.1, 21.2 and 21.3 are installed, at least partially a slender front edge and a thick downstream end 22.1, 22.2 and 22.3.
  • the profile of the flow cross sections 23.1, 23.2 and 23.3 between adjacent rings is dimensioned such that the static pressure in the flow direction remains largely constant. Accordingly, we speak here of an approximated constant pressure deflection or of an approximately isokinetic deflection with division of the inhomogeneous flow field still remaining at the diffuser outlet 2.2 into individual flow rings.
  • a fan diffuser which is equipped with a convergent hub in addition to a flared housing, is in many cases rather disadvantageous.
  • Fig. 8 shows a corresponding embodiment. Here are mounted on the end surfaces 22.1, 22.2, 22.3 and 22.4 deflector plates 28, through which the flow at the outlet of the annular channels 24.1, 24.2 and 24.3, see.
  • Fig. 7 is alternately deflected outwards or inwards in the circumferential direction. This is drawn only in the upper half of the cross section, while in the lower half of the velocity distribution 17 and a radial sword 27 are shown.
  • Such radial blades serve to center the ring elements 21, Fig. 7 and Fig. 8 ,
  • annular internals 21.1, 21.2 and 21.3 in Fig. 7 are usually centered over radial swords 27. But by this measure alone, in some cases, no sufficient fluid dynamic decoupling of the partial streams 26.1, 26.2 and 26.3 can be achieved. These annular partial flows tend to enter into a transient interaction with each other. This can be done by the deflector according to Fig. 8 be strongly damped. Another way of damping is in Fig. 9 in section (left) and in a view from the downstream side (right). Here are between the rings 21.1. 21.2 and 21.3, Fig. 7 , and to the hub 25 toward exit-side displacement body 29.1. 29.2 and 29.3 installed, which are usefully mounted on the already mentioned radial swords 27. By this displacement body, the largely closed flow rings are divided into ring sections, which are less prone to interaction.
  • the problem of mixing a secondary fluid 42 into the primary fluid 41 is also solved.
  • the secondary fluid 42 is connected via a pipe 30 and via the hollow displacement body 29.1, 29.2 and 29.3, cf. Fig. 10 , in the hollow running ring elements 21.1, 21.2, 21.3 and in the hub body 25, Fig. 7 , which initiated equal pressure deflection.
  • the mixing process can be greatly fanned by deflector plates 28, which according to Fig.
  • a bladed manifold 32 in particular when it has a cross-sectional widening in the flow direction to equip with guide bodies 33 having a thickened downstream side 34. Due to the displacement effect associated therewith, a constant pressure deflection with subsequent Carnot impact diffusers can likewise be generated. Here it may even be advantageous to carry out the thickening somewhat stronger than would be necessary for a constant flow cross section between the guide bodies. Due to the acceleration, which is accompanied by the reduction in cross section in the flow direction in subsonic flows, a flow separation on the suction side of the turning vanes is also avoided when a strong deflection to z. B. 90 ° to be realized.
  • the angle of attack ⁇ of the deflector plates 28 can be varied from place to place. With decreasing angle ⁇ , there is a stronger local throttling of the flow of the primary fluid as well as an intensification of the interference in adjacent zones.
  • the system with the deflector plates 28 acts as a mixer and homogenizing component within the primary fluid 41.
  • Fig. 11 are also in the fan diffuser 2 baffles 36 located, as already in a previous German patent application DE 10 2010 022 418 , please refer Fig. 1 to Fig. 5 , the same inventor was proposed.
  • a homogenization of the outflow from the annular diffuser can be achieved, and this is of considerable advantage for the flow through the subsequent manifold.
  • Fig. 12 1 shows a plan view of the outflow sides 34 of the guide vanes 33.
  • the deflector plates 28, which are alternately bent to the left or to the right, can be seen, as well as the associated blow-off bores 39 for a secondary fluid 42.
  • the supply channel 44 for the secondary fluid 42 is outside the Bend arranged.
  • Fig. 13 In particular, it also shows the additional functional elements in comparison with the inventors' earlier applications.
  • a first ring 45.1 of auxiliary vanes 45 is mounted near the housing outer wall on the guide vanes 5 of the blower.
  • a second ring 45.2 of auxiliary vanes 45 is disposed near the hub 7 at the same Nachleitschaufeln.
  • the auxiliary vanes may, for. B. be mounted on the pressure side 5.1 of the vanes 5 or both on the pressure side 5.2 and on the suction side 5.1, see.
  • the detailed representation in Fig. 16 As these auxiliary vanes in Zones are arranged with high flow velocity, they would of course be designed as aerodynamically optimized wings.
  • auxiliary guide vanes The effect of these auxiliary guide vanes is shown in a speed profile according to paragraph 46 with large speed gradients 46.1 on the housing wall or on the hub 46.2. It may even be advantageous to create near the walls a zone with slightly higher flow velocities than in the middle of the channel, as for the velocity profile 46 in FIG Fig. 13 is shown.
  • a ring 47.1 is arranged on the inner wall of individual only slightly against the flow employed guide vanes.
  • a corresponding ring 47.2 of vanes is attached to the hub 3.
  • the vanes on both rings could also be designed as delta wings 48 here.
  • delta wings As a rule, however, we would not use delta wings, but wing sections with a defined leading edge, which lie on an approximately concentric to the diffuser axis ring.
  • the wing sections could advantageously be equipped with "tip wings", whereby the Randwirbel Struktur and consequently the pressure loss are reduced, as already in the application DE10 2010 022 418 was proposed. Due to the slight adjustment against the flow, each blade generates a pulse stream directed into the flow boundary layer.
  • a plurality of rings of guide vanes or guide vanes can be attached to different axial positions of the ring diffuser.
  • auxiliary baffles 45.1 and 45.2 at the trailing edges of the guide vanes 5 of the fan and the vanes 47.1 and 47.2 in the divergent section of the ring diffuser 1 a substantially homogeneous velocity profile 17 is generated in cross-section 2.2 at the diffuser end, which is characterized in particular by strong velocity gradients in the near-wall areas 17.1 and 17.2.
  • V-shaped gusset plates 52 are provided here as internals with a radially directed and rather sharply tapering inflow or front edge 52.1.
  • the V formed by the gussets does not necessarily have to be closed at the trailing edge. If a higher dust loading occurs in the fluid, however, it may be useful to avoid accumulation of dust to perform the gusset plates as a hollow body and provide a rear cover plate 52.2, see also Fig. 13 ,
  • a second fluid if such admixture z. B. of warm air is required.
  • the second fluid may be introduced via bores 52.4 into the primary fluid stream.
  • additional vanes 52.5 are attached.
  • the gusset plates 52 terminate at a concentric ring 52.7, which also represents the next nabennste Leitelement 52.5.
  • ring 52.7 is supported by radial swords 52.8.
  • the concentric baffles 52.5 between the V - shaped gusset plates are shown with a thickened trailing edge 49.
  • This solution represents a combination of the two different concepts of avoiding flow separation in a greatly expanded channel section;
  • the V-shaped radially extending gusset plates 52 are combined with displacement bodies 49 that are concentric with the main axis 30 and thickened toward the trailing edge.
  • a secondary fluid eg hot air or ammonia
  • ports 47.3 and 47.4 are mounted for introduction of the secondary fluid in close spatial proximity to the vanes 47.1 and 47.2.
  • the primary fluid is mixed into the low turbulence skimmed streams. Since the generation of a highly turbulent flow with regard to the minimization of the pressure losses was dispensed with in this invention, a longer running distance is required for the admixing of the secondary fluid.
  • FIG. 15 showing a view looking upstream to the main flow of the primary fluid 41, the principle of introducing a secondary fluid into the primary fluid via the wedge-shaped hollow bodies 52 is shown.
  • Each hollow body 52 is associated with an inlet connection 52.3.
  • the secondary fluid exit bores 52.4 are only in Fig. 13 pictorially reproduced.
  • Figure 13 also shows the end face 52.9 of the hub body 52.6 and radial web plates 52.8, over which the ring 52.7 is supported to the hub 52.6.
  • FIGS. 17 and 18 show a special case of the configuration Fig. 13 or Fig. 14 ,
  • the guide elements 47.1 and 47.2 can be made different in size.
  • the radius of the ring concentric with the main axis 16, on which the guide elements are arranged is dimensioned so that the primary fluid flow is approximately divided into two equal-volume partial streams.
  • Fig. 19 shows a variant of Fig. 7 , According to this variant, a segmentation of the annular channel and / or the channel extension may be provided in the ring diffuser 1 or in the subsequent channel extension 18.
  • the segmentation is carried out by channel segments, which are connected via radial struts 51, 61 with the inner wall of the ring diffuser 1 or the inner wall of the channel extension 18. 50, 60.
  • the channel segments 50 which may be located in the ring diffuser 1 between the inner wall and the hub 3, be designed as cylinder segments. Alternatively, they can also run parallel to the inner wall of the ring diffuser, thus be formed as segments of a cone.
  • the channel segments 60 which are located in the channel extension downstream of the annular displacement body 21.1, 21.2 and 21.3, can also as Segments of a cone to be formed.
  • the inclination of the cone may correspond to the inclination of the cone forming the channel widening, but may also be larger or smaller, depending on the desired influence on the fluid flow through the channel widening.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Chemical & Material Sciences (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Branch Pipes, Bends, And The Like (AREA)

Claims (7)

  1. Tronçon de canal traversé par un fluide primaire et présentant un élargissement de section transversale en direction d'écoulement ainsi que des dispositifs installés, par lesquels la section transversale du canal est subdivisée en au moins 2 canaux partiels, l'épaisseur de refoulement d'une partie au moins des dispositifs installés augmentant en direction d'écoulement,
    caractérisé en ce que
    le tronçon de canal comprend un diffuseur-ventilateur de forme élancée ayant un angle d'ouverture dans l'ordre de 10° à 20°, auquel se raccorde un tronçon de canal fortement élargi d'un angle d'ouverture dans l'ordre de 20° à 120°, les dispositifs installés étant réalisés sous forme de tôles en gousset (52) en forme de V s'étendant radialement par rapport à l'axe principal du diffuseur dans le tronçon de canal fortement élargi.
  2. Tronçon de canal selon la revendication 1,
    caractérisé en ce que
    une tôle de recouvrement (52.2) est prévue sur les tôles en gousset (52), de sorte que la tôle en gousset (52) est réalisée sous la forme d'un corps creux en forme de coin.
  3. Tronçon de canal selon la revendication 2,
    dans lequel
    sont agencés au moins 3 corps creux (52) en forme de coin.
  4. Tronçon de canal selon la revendication 3,
    dans lequel
    l'angle d'ouverture dans les canaux partiels entre les corps creux (52) en forme de coin est de l'ordre de 0° à 18°.
  5. Tronçon de canal selon l'une des revendications 1 à 4,
    caractérisé en ce que
    les dispositifs installés (52) sont réalisés creux et sont alimentés en un fluide secondaire depuis l'extérieur via des conduites tubulaires,
    et en ce que le fluide secondaire est soufflé dans le fluide primaire via des perçages ménagés dans la surface des dispositifs installés, à des fins de mélange.
  6. Tronçon de canal selon l'une des revendications 1 à 5,
    caractérisé en ce que
    des surfaces de déflecteur sont montées dans la zone de sortie des dispositifs installés (52), qui exercent un effet de mélange sur les fluides.
  7. Tronçon de canal selon la revendication 6,
    caractérisé en ce que
    les surfaces de déflecteur sont coudées en alternance vers l'intérieur ou vers l'extérieur.
EP11722448.5A 2010-06-01 2011-05-31 Canal à surface de guidage d'écoulement Not-in-force EP2577071B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PL11722448T PL2577071T3 (pl) 2010-06-01 2011-05-31 Kanał z powierzchnią kierującą przepływem

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE102010022418A DE102010022418A1 (de) 2010-06-01 2010-06-01 Mischer und Diffusor - Leitgitter
DE102010024091A DE102010024091B4 (de) 2010-06-17 2010-06-17 Mischer
DE201110012039 DE102011012039A1 (de) 2011-02-22 2011-02-22 Kanal mit Strömungsleitfläche
PCT/EP2011/058944 WO2011151323A2 (fr) 2010-06-01 2011-05-31 Canal à surface de guidage d'écoulement

Publications (2)

Publication Number Publication Date
EP2577071A2 EP2577071A2 (fr) 2013-04-10
EP2577071B1 true EP2577071B1 (fr) 2017-12-20

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EP11722448.5A Not-in-force EP2577071B1 (fr) 2010-06-01 2011-05-31 Canal à surface de guidage d'écoulement

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US (1) US9291177B2 (fr)
EP (1) EP2577071B1 (fr)
PL (1) PL2577071T3 (fr)
WO (1) WO2011151323A2 (fr)

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KR102343408B1 (ko) * 2017-11-17 2021-12-27 주식회사 엘지화학 열 교환기
JP7333144B2 (ja) * 2018-03-16 2023-08-24 ジョビー エアロ インク 航空機抗力低減システム及び内部冷却電気モータ・システム並びにこれらを使用する航空機
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Also Published As

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WO2011151323A3 (fr) 2012-02-16
US20130265848A1 (en) 2013-10-10
US9291177B2 (en) 2016-03-22
PL2577071T3 (pl) 2018-06-29
WO2011151323A2 (fr) 2011-12-08
EP2577071A2 (fr) 2013-04-10

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