EP3237760B1 - Diffuseur pour un compresseur centrifuge - Google Patents

Diffuseur pour un compresseur centrifuge Download PDF

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Publication number
EP3237760B1
EP3237760B1 EP15823510.1A EP15823510A EP3237760B1 EP 3237760 B1 EP3237760 B1 EP 3237760B1 EP 15823510 A EP15823510 A EP 15823510A EP 3237760 B1 EP3237760 B1 EP 3237760B1
Authority
EP
European Patent Office
Prior art keywords
diffuser
pressure
side wall
blade
duct
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP15823510.1A
Other languages
German (de)
English (en)
Other versions
EP3237760A1 (fr
Inventor
Christian Kreienkamp
Armin Reichl
Daniel Rusch
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
ABB Schweiz AG
Original Assignee
ABB Turbo Systems AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from DE102014119562.0A external-priority patent/DE102014119562A1/de
Priority claimed from DE102014119558.2A external-priority patent/DE102014119558A1/de
Application filed by ABB Turbo Systems AG filed Critical ABB Turbo Systems AG
Publication of EP3237760A1 publication Critical patent/EP3237760A1/fr
Application granted granted Critical
Publication of EP3237760B1 publication Critical patent/EP3237760B1/fr
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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
    • F04D29/44—Fluid-guiding means, e.g. diffusers
    • F04D29/441—Fluid-guiding means, e.g. diffusers especially adapted for elastic fluid pumps
    • F04D29/444—Bladed diffusers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D27/00—Control, e.g. regulation, of pumps, pumping installations or pumping systems specially adapted for elastic fluids
    • F04D27/02—Surge control
    • F04D27/0207—Surge control by bleeding, bypassing or recycling fluids
    • 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
    • F04D29/58—Cooling; Heating; Diminishing heat transfer
    • F04D29/582—Cooling; Heating; Diminishing heat transfer specially adapted for elastic fluid pumps
    • F04D29/5846—Cooling; Heating; Diminishing heat transfer specially adapted for elastic fluid pumps cooling by injection
    • 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
    • F04D29/70—Suction grids; Strainers; Dust separation; Cleaning
    • F04D29/701—Suction grids; Strainers; Dust separation; Cleaning especially adapted for elastic fluid pumps
    • 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
    • F05D2220/00—Application
    • F05D2220/40—Application in turbochargers
    • 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
    • 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
    • F05D2260/00—Function
    • F05D2260/15—Load balancing
    • 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
    • F05D2260/00—Function
    • F05D2260/60—Fluid transfer
    • F05D2260/606—Bypassing the fluid
    • 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
    • F05D2260/00—Function
    • F05D2260/60—Fluid transfer
    • F05D2260/607—Preventing clogging or obstruction of flow paths by dirt, dust, or foreign particles

Definitions

  • the present invention relates to a diffuser for a radial compressor.
  • the term radial compressor in the following also includes so-called mixed-flow compressors with an axial inflow and a radial outflow of the compressor impeller.
  • the scope of the present invention also extends to compressors with a purely radial or diagonal inflow or outflow of the compressor impeller.
  • the present invention relates to a diffuser for a radial compressor, wherein the radial compressor can be used in a turbocharger, and wherein the turbocharger can have an axial turbine or a radial or a so-called mixed flow turbine.
  • Diffusers for use in radial compressors for turbocharger applications are known from the prior art.
  • a fluid eg air
  • a fluid eg air
  • Energy is supplied to the fluid in the form of pressure, temperature and kinetic energy.
  • High flow velocities prevail at the outlet of the compressor wheel.
  • the accelerated, compressed air leaves the compressor wheel tangentially in the direction of the diffuser.
  • the kinetic energy of the accelerated air is converted into pressure in the diffuser. This is done by delaying the flow in the diffuser.
  • the radial cross section of the diffuser is enlarged by radial expansion. This delays the fluid and builds up pressure.
  • the diffusers used therein can be equipped with blading.
  • An example of a bladed diffuser is shown in DE102008044505 .
  • the diffusers with blading known from the prior art are generally designed as radial parallel-walled diffusers with blading, as for example in FIG US4131389 shown.
  • the flow in the diffuser can be decelerated more. This reduces the flow velocities in the spiral, which reduces the wall friction losses and improves the efficiency of the compressor stage.
  • the use of diffusers with radial side wall divergence allows a greater delay with the same overall length compared to parallel-walled diffusers.
  • the delay or pressure increase that can be achieved in the diffuser by means of a geometry variation for a given operating point is limited, since the delay is too great Flow instabilities due to boundary layer detachments in the diffuser comes.
  • the limits of the stable operating range of the diffuser thus determine the position of the surge limit of the compressor in the compressor map. If a diffuser with side wall divergence is used instead of a parallel-walled diffuser - such a diffuser is for example in the WO 2012/116880 A1 and GB2041149 A described - although the efficiency increases with the same compressor pressure ratios, at the same time, however, for a given compressor pressure ratio the pump limit shifts to larger mass flows compared to the compressor with a parallel-walled diffuser. This effect is undesirable.
  • One solution is to fluidly connect a diffuser channel section of a bladed diffuser to an annular channel via pressure equalization openings in order to enable pressure equalization between individual diffuser passages of the diffuser, which are formed by adjacent diffuser blades.
  • pressure equalization openings the problem can arise that the ring channel and / or the individual pressure equalization openings become blocked, for example due to residues and deposits from a compressor cleaning or due to particles which are in oil-containing intake air. This has a negative impact on the surge limit of the compressor and, in extreme cases, can mean that a motor connected to the diffuser can no longer be operated.
  • the present invention has for its object to develop a bladed diffuser with radial side wall convergence for radial compressors in such a way that the efficiency compared to parallel-walled diffusers is improved and at the same time the flow in the diffuser is stabilized in order to improve the pumping behavior of the compressor.
  • Another object of the present invention is to avoid or reduce premature boundary layer detachments on the diffuser vanes and on the side walls of the diffuser in individual diffuser passages due to excessive delays.
  • it is a further object of the present invention to ensure that the function of the diffuser is not impaired even in the event of possible contamination due to deposits and residues from the intake air containing oil from the compressor.
  • the object is achieved by a diffuser for a radial compressor, the diffuser comprising a diffuser channel section which is formed by a first side wall and a second side wall, the first side wall and the second Sidewall are at least partially divergent from each other in the flow direction.
  • the diffuser comprises a blade ring with a number of blades, the blades being arranged at least partially in the diffuser channel section, each of the blades having a pressure side and a suction side, and wherein
  • the diffuser comprises a number of pressure compensation openings, which are incorporated in at least one of the two side walls of the diffuser channel section, each of the number of pressure compensation openings being arranged between the pressure side of a blade and the suction side of the adjacent blade of the blade ring.
  • the diffuser comprises a first ring channel, which is arranged behind the pressure compensation openings, the first ring channel being fluidically connected to the diffuser channel section via at least two of the pressure compensation openings, as a result of which a number of diffuser passages of the diffuser can be fluidly connected to one another, a region between two being used as the diffuser passage adjacent blades of the blade ring in the diffuser channel section is referred to, the number of pressure equalization openings which are incorporated in at least one of the two side walls of the diffuser channel section being arranged in a region of the respective side wall in which the first side wall and second side wall are arranged to be divergent to one another in the flow direction ,
  • the first ring channel can be connected to a pressure plenum via a connecting channel, as a result of which a fluid can flow from the pressure plenum into the first ring channel so that the first ring channel is flushed with the fluid.
  • the bladed diffuser channel section of the diffuser has pressure compensation openings which are incorporated in at least one of the two side walls of the diffuser channel section, and the diffuser channel section of the diffuser being fluidly connected to a first ring channel and wherein the first ring channel can be connected to a pressure plenum via a connecting channel, whereby a fluid can flow from the pressure plenum into the first ring channel so that the first ring channel is flushed with the fluid.
  • Another advantage of the present invention is that a pressure equalization can take place in the ring channel, which causes flow separation in the diffuser blades in the bladed diffuser channel section due to excessive flow delays counteracts and compensates for a flow separation.
  • a diffuser passage is defined as a space or a section between two adjacent diffuser blades. Uneven loads on individual diffuser passages in the diffuser channel section arise, for example, from asymmetries in the compressor housing and air intake port of the compressor and the resulting non-rotationally symmetrical pressure field in the outflow area of the diffuser, manufacturing and installation tolerances, and through transient flow effects.
  • the pressure compensation makes it possible to compensate for instabilities in individual diffuser passages, by using the stability reserves of other, still stable, diffuser passages.
  • the stable working area of the diffuser and the compressor is expanded as a whole until all diffuser passages come into the area of the unstable flow.
  • the consequence of this is that the pump limit of the compressor shifts towards lower volume flows and the usable area of the compressor map increases.
  • the pressure plenum is connected to a fluid source, the fluid source being designed to provide fluid for the pressure plenum.
  • the fluid source is designed as a charge air cooler, the charge air cooler being designed to provide fluid, and the fluid being able to be introduced from the charge air cooler into the pressure plenum.
  • the fluid from the charge air cooler which is designed, for example, as a flushing medium, can also or additionally be used for cooling a compressor wheel of the radial compressor.
  • a filter system for cleaning the fluid is installed between the pressure plenum and the fluid source.
  • a turbocharger arrangement which comprises a diffuser.
  • the first ring channel is incorporated in one of the two side walls of the diffuser channel section.
  • the pressure compensation openings are each designed as a bore and / or as a slot. Alternatively, however, a pressure compensation opening could also be formed from several individual bores or slots.
  • the orientation of each of the pressure equalization openings in the respective side wall of the diffuser channel section is determined by an angle of attack, which is defined as the angle of attack of the respective pressure equalization opening to the surface of this side wall facing the diffuser channel section.
  • the first ring channel is divided by separating means into a number of individual, sub-channel areas of the first ring channel that are separated from one another. In this way, pressure equalization between diffuser passages within a subchannel area can be limited locally.
  • each sub-channel region of the first ring channel comprises at least two pressure compensation openings.
  • the pressure compensation openings do not have to be an integral part of the ring channel.
  • At least one second ring channel is incorporated in one of the side walls with pressure compensation openings in the diffuser channel section, as a result of which the diffuser passages of two non-adjacent blades of the blade ring can be fluidly connected to one another.
  • the first or second side wall of the diffuser channel section is designed as a diffuser plate, the number of pressure compensation openings and at least one ring channel being incorporated in the diffuser plate.
  • One embodiment of the present invention includes a radial compressor with a diffuser.
  • Fig. 1 shows a diffuser 1 with blading for a radial compressor 100 according to a first embodiment of the present invention.
  • the diffuser 1 comprises a diffuser channel section 2, which is formed by a first side wall 3 and a second side wall 4.
  • the diffuser channel section 2 extends from the compressor wheel until it enters the compressor spiral (not shown).
  • the first side wall 3 and the second side wall 4 are at least partially divergent from one another in the flow direction.
  • the diffuser 1 comprises in the Figure 1 a blade ring 5 with a number of individual blades 6, 6 ', the blades 6, 6' being at least partially arranged in the diffuser channel section 2. This means that in the diffuser 1 there can be both bladed and non-bladed areas within the diffuser channel section 2.
  • a number of pressure compensation openings 7, 7 ' are incorporated in the second side wall 4, wherein in the side view of the Figure 1 only one pressure compensation opening 7, 7 'is shown.
  • the second side wall 4 of the diffuser 1 is in the embodiment of FIG Figure 1 on a side facing a turbine wheel (not shown), the turbine wheel being part of a turbocharger arrangement (not shown) which also includes the radial compressor 100.
  • the diffuser 1 comprises a first ring channel 10, which is arranged behind or after the pressure compensation openings 7, 7 '.
  • the first ring channel 10 is designed as an essentially annular continuous channel, which can also be referred to as an open channel. The pressure equalization takes place over the entire circumference of the open channel.
  • the pressure equalization ensures that the flow between the diffuser passages in the diffuser channel section 2 is stabilized by using stability reserves from adjacent or non-adjacent diffuser passages to stabilize the flow in individual diffuser passages that are already operated in the unstable area.
  • a space or an area or a section between two adjacent diffuser blades is referred to as a diffuser passage.
  • the first ring channel 10 can be integrated as a component of the side wall 3, 4 directly into one or both of the side walls 3, 4, provided that it is ensured that the ring channel 10 is always installed behind the pressure compensation openings 7, 7 '.
  • an annular channel is installed in each of the side walls 3, 4 and is fluidically connected to the diffuser channel section 2 via pressure compensation openings 7, 7 '(not shown).
  • the first ring channel 10 is incorporated in a third side wall 15, the third side wall 15 being arranged behind or after the second side wall 4 of the diffuser channel section 2 and the pressure equalization openings 7, 7 'being incorporated in the second side wall 4.
  • the third side wall 15 can also be designed as a so-called partition, which is arranged between the compressor side and the turbine side of a turbocharger arrangement.
  • the ring channel 10 and thus also the pressure compensation openings 7, 7 'could also be a component of the second side wall 4 or the first side wall 3 of the diffuser channel section 2 (not shown), so that the third side wall 15 would be omitted.
  • the pressure compensation openings 7, 7 'and the first ring channel 10 would then be incorporated in a one-piece component, one surface of this component forming the first side wall 3 or the second side wall 4.
  • the ring channel 10 would be arranged behind the pressure equalization openings 7, 7 ', so that it is ensured that the ring channel 10 is fluidly connected to the diffuser channel section 2 via the pressure equalization openings 7, and thereby at the same time it is achieved that the number the flow cross sections of the diffuser 1 are fluidly connected to one another.
  • the ring channel 10 is fluidly connected to the diffuser channel section 2 via at least two of the pressure compensation openings 7, 7 '.
  • Each of the pressure equalization openings 7, 7 ' which are incorporated in at least one of the two side walls 3, 4 of the diffuser channel section 2, are arranged in all embodiments of the invention in a region of the respective side wall 3, 4, in which the first side wall 3 and second side wall 4 are arranged divergent to each other in the flow direction.
  • the pressure compensation openings 7, 7 ' can each be designed as a bore and / or as a slot.
  • a pressure equalization opening could also be composed of a plurality of openings, that is to say for example of a plurality of individual bores or slots or a combination of both shapes.
  • another form of the pressure compensation opening in the diffuser 1 could also be realized.
  • the pressure compensation openings 7, 7 ' are also arranged in the bladed diffuser channel section 2 of the diffuser 1. This has the advantage that flow separations in this area - the bladed diffuser area - are compensated for due to excessive delays.
  • the pressure compensation openings 7, 7 'could also be arranged in a non-bladed diffuser channel section 2, which means that a number of individual pressure compensation openings 7, 7' are incorporated in at least one of the two side walls 3, 4 and in this area of the Diffuser channel section 2, which is formed by the two side walls 3, 4, no diffuser blades 6, 6 'are arranged.
  • the radial compressor 100 with the diffuser 1 according to the invention also comprises a compressor wheel 40, a compressor housing 42 and a bearing housing 44. However, additional or further components of the compressor are not shown in the figure for reasons of clarity.
  • Figure 2 shows a profile view of a partial section of a diffuser 1 with blading for a radial compressor 100 according to a second embodiment of the present invention.
  • the Figure 2 shows a diffuser 1 which in the diffuser channel section 2 has a number of diffuser blades 6, 6 'of the blade ring 5 (not completely in FIG Figure 2 shown).
  • the second side wall 4 of the diffuser 1 is shown.
  • pressure equalization openings 7, 7 ' are incorporated, in which Figure 2 only one pressure equalization opening is shown in the profile view.
  • An annular channel 10 is arranged in the side wall 4 directly behind the pressure compensation opening 7, 7 '.
  • the ring channel 10 is thus in the embodiment shown Figure 2 Part of the second side wall 4.
  • the ring channel 10 enables pressure equalization between individual diffuser blades 6, 6 ', which are at least partially arranged within the side wall divergent diffuser channel section 2. A flow separation on the individual diffuser blades 6, 6 ′ of the blade ring 5 of the diffuser 1 can thereby be compensated for. Flow separations occur when the pump limit of the diffuser 1 is approached initially in individual heavily loaded diffuser passages, that is to say in areas of two adjacent diffuser blades 6, 6 ', which are loaded unevenly due to asymmetries, such as in the compressor housing.
  • the illustrated pressure compensation opening 7, 7 'of Figure 2 connects the first ring channel 10 to the flow cross sections of the diffuser 1.
  • the second side wall 4 of the diffuser 1 is in the in Figure 2
  • the illustrated embodiment of the diffuser 1 is part of a diffuser plate 12.
  • the diffuser plate 12 comprises the individual pressure compensation openings 7, 7 'and the first ring channel 10, the first ring channel 10 being arranged behind the pressure compensation openings 7, 7'.
  • FIG 3 shows a top view of a diffuser 1.
  • the diffuser 1 comprises a diffuser plate 12.
  • the diffuser plate 12 comprises a number of pressure compensation openings 7, 7 ', each of which fluidly connects the flow cross sections of the diffuser 1 to a first ring channel 10.
  • the first ring channel 10 is arranged behind the pressure compensation openings 7, 7 '.
  • the first ring channel 10 is, as in the Figure 3 shown, designed as a so-called continuous annulus.
  • the first ring channel 10 can, as already in the Figure 1 and the Figure 2 illustrated, either be integrated directly into the diffuser plate 12, or alternatively, can be incorporated into a separate wall, the separate wall being arranged behind the diffuser plate 12.
  • Each of the pressure equalization openings 7, 7 'in Figure 3 The diffuser plate 12 shown is arranged between two adjacent blades 6, 6 '.
  • Each of the blades 6, 6 ′ comprises a pressure side 22 and a suction side 23, the pressure side 22 and the suction side 23 of each blade 6, 6 ′ from a blade leading edge 8 and from a blade leading edge 8 'of this blade 6, 6' are limited.
  • the blade 6 ′ in FIG Figure 3 a blade leading edge 8 and a blade leading edge 8 ', which respectively limit the pressure side 22 and the suction side 23 of this blade 6'.
  • Each of the number of pressure equalization openings 7, 7 ' is arranged between the pressure side 22 of one blade 6 and the suction side 23 of the adjacent blade 6' of the blade ring 5.
  • the one in the Figure 3 arranged in the diffuser passage between the blade 6 and the blade 6 'pressure equalization opening 7 such that it is arranged between the pressure side 22 of the blade 6 and the suction side 23 of the adjacent blade 6' of the blade ring 5.
  • the individual pressure equalization openings 7, 7 ' are in the Figure 3 formed as slots.
  • the individual pressure compensation openings 7, 7 ' can each be designed as a bore and / or slot.
  • the first ring channel 10 is divided by separating means 13 into a number of individual subchannel regions 11, 11 'which are separated from one another.
  • two diffuser passages are assigned to each of the sub-channel regions 11, 11 ′ of the first ring channel 10.
  • the pressure compensation openings 7, 7 ' are not an integral part of the first ring channel 10.
  • the subdivision of the first ring channel 10 into individual sub-channel areas ensures that pressure equalization takes place only between adjacent blades 6, 6 'of a sub-channel area 11, 11'. In this way, the pressure equalization between blades within a sub-channel area can be limited locally. So-called closed subchannel areas result from the individual subchannel areas.
  • a pressure equalization takes place in the Figure 3 embodiment no longer takes place over the complete first ring channel 10, as is the case in the embodiments of FIG Figure 1 and the Figure 2 is the case with a continuous ring channel.
  • the separating means 13 can be designed, for example, as partitions.
  • the individual partition walls 13 are located on the side of the diffuser 1 facing away from the flow.
  • the subdivision of the first ring channel 10 into individual subchannel regions that are independent of one another in terms of flow technology can contribute to increased stability and an improvement in the efficiency of the diffuser 1.
  • the individual subchannel areas 11, 11 'within the first ring channel 10 can be produced, for example, by so-called additive manufacturing methods. Alternatively, it would also be possible to divide the first ring channel 10 into individual sub-channel regions 11, 11 'by abutment on an adjacent component, such as a bearing housing of the radial compressor 100 (not shown).
  • Figure 4 shows a top view of a further embodiment of the diffuser 1 according to the invention.
  • Figure 4 shows the diffuser plate 12 of the diffuser 1.
  • a number of pressure compensation openings 7, 7 ', 7 " are incorporated, each of which fluidly connects the narrowest flow cross sections of the diffuser 1 with the ring channel 10, the first ring channel 10 behind the pressure compensation openings 7, 7 ', 7 "is arranged.
  • the illustrated embodiment of the diffuser 1 differs from that in FIG Figure 3 Embodiment shown in that each of the individual subchannel regions 11, 11 'comprises three pressure compensation openings 7, 7', 7 "with the three blades 6, 6 ', 6".
  • the partial channel region 11 of the first ring channel 10 is provided with corresponding reference numerals.
  • designs can also be implemented in which, by appropriate separation, more than three blades divide a partial channel area of the first ring channel 10.
  • Figure 5 shows a further embodiment of the diffuser 1 according to the invention with a diffuser plate 12 of the diffuser 1 in plan view.
  • the diffuser plate 12 shown in this embodiment Figure 5 is in principle with that in the Figure 3 illustrated embodiment of the diffuser 1 identical.
  • the embodiment of the Figure 5 differs from the embodiment of Figure 3 only in that in the diffuser plate 12 Figure 5 in addition to a first ring channel 10, a second ring channel 20 is provided.
  • the second ring channel 20 in the diffuser plate 12 has the task of fluidly connecting the diffuser passages from non-adjacent blades.
  • the ring channel 20 connects the blades of the partial channel area 11 with the blades of the partial channel area 11 ".
  • the second ring channel 20 can be in the diffuser plate 12 into which the first ring channel 10 is also worked in. Alternatively, the second ring channel 20 can be worked into a separate wall which is arranged behind the diffuser plate 12 if the diffuser plate 12 has pressure equalization openings of the side walls 3, 4 with pressure compensation openings 7, 7 'of the diffuser channel section 2 or in the third side wall 15, which is located behind one of the side walls 3, 4 with pressure compensation openings 7, 7'.
  • two diffuser passages can be fluidically mite inander connect, the two diffuser passages are not arranged directly next to each other and adjacent.
  • a diffuser passage which comprises the pressure compensation opening 7
  • a diffuser passage which comprises the pressure compensation opening 7
  • a diffuser passage which comprises the pressure compensation opening 7 ′′.
  • pressure compensation between blades or diffuser passages from non-adjacent subchannel regions can take place
  • Application can also be incorporated in the diffuser 1 more than two ring channels.
  • Fig. 6 shows a section of a diffuser plate 12 with examples of possible alignments of pressure compensation openings in a diffuser passage between two adjacent blades 6, 6 '.
  • the embodiment of the Figure 6 differs from the embodiments of FIG Figures 3 . 4 and 5 only in that the in Figure 6 pressure equalization openings 7-1 and 7-2 shown as examples within a diffuser passage of two adjacent diffuser blades 6, 6 'can each have different orientations with respect to the diffuser plate 12 or positions.
  • Each of the blades 6, 6 'of the Figure 6 each comprises a pressure side 22 and a suction side 23.
  • the pressure side 22 and the suction side 23 of each blade 6, 6 ' are delimited by a blade leading edge 8 and a blade leading edge 8' of the respective blade 6, 6 '.
  • the pressure compensation opening 7-1 located in the diffuser passage between the blade 6 and the blade 6 ' is arranged or aligned such that, for example, the pressure compensation opening 7-1 between the pressure side 22 of the blade 6 and the suction side 23 of the adjacent blade 6' of the blade ring 5 is arranged.
  • Fig. 7 shows an example of an orientation or a possible position of a pressure compensation opening 7, 7 'within a diffuser plate 12 and with respect to the main flow direction 52 of the fluid in the diffuser channel section 2.
  • the diffuser channel section is formed by the side wall 3 and the side wall 4, the side wall 4 being a component of the diffuser plate 12.
  • the pressure equalization opening 7, 7 ' is in the embodiment of the Figure 7 incorporated in the diffuser plate 12 and is connected to the first ring channel 10.
  • the Figure 7 additionally shows the direction of flow of the fluid in the diffuser channel section 2, which is represented by a vector 52.
  • the orientation of the in the Figure 7 shown pressure equalization opening 7, 7 ', which is incorporated in the side wall 4 of the diffuser channel section 2, is determined by an angle of attack 54, which is defined as the angle of attack 54 of the pressure compensation opening 7, 7' to the surface of the side wall 4 facing the diffuser channel section 2.
  • the angle of attack 54 in the embodiment of FIG Figure 7 can preferably be in a range between greater than 0 degrees and approximately less than 180 degrees in order to reduce fluid losses in the diffuser channel section 2.
  • Fig. 8 shows a schematic illustration of a turbocharger arrangement 150 with a bladed diffuser 2.
  • the turbocharger arrangement 150 comprises a diffuser 2, which is fluidly connected to a first ring channel 10 via pressure compensation openings 7, 7 '(not shown).
  • the diffuser 2 is connected to a compressor wheel 101, the compressor wheel 101 being driven by a turbine 151 via a shaft 153.
  • the diffuser 2 and the compressor wheel 101 are components of a radial compressor 100.
  • the first ring channel 10 is connected via a connecting channel 30 to a pressure plenum 31, which is also referred to as a ring channel plenum.
  • a fluid is fed into the pressure plenum 31 as a flushing agent or as a flushing medium, which fluid is preferably designed as flushing air and which, however, can also or additionally be used for cooling.
  • the fluid in the embodiment of the Figure 8 is provided by a fluid source 35.
  • This fluid source 35 which can also be referred to as a pressure source, can preferably be designed as a charge air cooler.
  • the charge air cooler is supplied with compressed air by the radial compressor 100 and cools the compressed air of the radial compressor 100 down to a certain temperature before it is supplied to an engine (not shown).
  • the fluid from the charge air cooler which is designed as a flushing agent, is then fed to the pressure plenum 31.
  • the pressure plenum 31 is in the embodiment shown Figure 8 additionally connected to the compressor wheel 101 via a channel 154, so that part of the flushing agent from the charge air cooler 35 can also be used to cool the compressor wheel 101. In this way, compressor wheel cooling can be implemented.
  • the first ring channel 10 is flushed with the flushing agent from the fluid source 35, the flushing agent being storable in the pressure plenum 31.
  • the connecting channel 30 is preferably designed as a bore with a defined diameter. However, the connecting channel 30 does not necessarily have to be designed as a bore with a specific diameter D, but can also be designed as an angular or otherwise shaped passage. Alternatively, the connection channel 30 can also be formed from a number of individual passages.
  • the geometric configuration of the connecting channel 30 is important in this respect, since it determines the pressure with which the detergent is passed through the connecting channel 30 into the first ring channel 10.
  • the amount of pressure in the first ring channel 10 should be minimally higher than a pressure which is formed in the diffuser channel section 2, so that Intended pressure equalization in the first ring channel 10 is not impaired.
  • the geometric configuration of the connecting channel 30 thus allows the pressure with which the washing-up liquid in the connecting channel 30 is transported to the first ring channel 10 to be set.
  • the flushing agent conveyed into the first ring channel 10 with a specific, set pressure ensures that the first ring channel 10 is flushed with flushing agent.
  • the flushing prevents contamination of the first ring channel 10 and clogging of the pressure equalization openings 7, 7 ', 7 ", 7"''by deposits of oil-containing particles, such as the air from the diffuser channel section 2, so that the flushing medium with a defined pressure can be introduced into the first ring channel 10, a defined pressure should be formed in the fluid source 35 and in the pressure plenum 31, which is greater in amount than a pressure in the first ring channel 10 and a pressure in the diffuser 2.
  • the pressure in the The amount of the fluid source 35 should be greater than a pressure in the pressure plenum 31 and a pressure in the ring channel 10 and a pressure in the diffuser channel section 2.
  • the fluid source 35 can also be designed as a compressed air network, in which case the fluid source 35 can also consist of a plurality of fluid sources which provide fluid for the pressure plenum 31.
  • a filter system 39 can be provided, which is installed between the pressure plenum 31 and the fluid source 35 in order to clean the detergent or fluid.
  • the fluid from the fluid source 35 can be used to rinse a second ring channel in addition to the first ring channel 10 if a corresponding connection is established between the pressure plenum 31 and the second ring channel (not shown).
  • Fig. 9 shows a diffuser 2 with blading and pressure plenum 31 for a radial compressor.
  • the embodiment of the Figure 9 differs from the embodiment of Figure 1 in that the first ring channel 10 is connected to a pressure plenum 31 via a connecting channel 30.
  • a fluid under pressure is introduced from the pressure plenum 31, which is connected to the fluid source 35, via the connecting channel 30 into the first ring channel 10.
  • This has the effect that the first ring channel 10 is flushed with the flushing agent designed as a fluid from the fluid source 35 in order to loosen or close deposits and particle residues in the ring channel 10 and in the pressure compensation openings 7, 7 ', 7 ", 7"' prevent.
  • Another difference from the embodiment of the Figure 1 consists in that a compressor wheel cooling for cooling the compressor wheel 101 is additionally realized by the fluid from the pressure plenum 31 being conducted via a connecting channel 154 to the compressor wheel 101.

Claims (14)

  1. Diffuseur pour un compresseur centrifuge (100) comprenant :
    une section de canal de diffuseur (2), laquelle est formée par une première paroi latérale (3) et une deuxième paroi latérale (4), dans lequel la première paroi latérale (3) et la deuxième paroi latérale (4) sont agencées au moins partiellement de manière divergente l'une par rapport à l'autre dans la direction du courant, une couronne d'aubes (5) dotée d'un nombre d'aubes (6, 6'), dans lequel les aubes (6, 6') sont agencées au moins partiellement dans la section de canal de diffuseur (2), dans lequel chacune des aubes (6, 6') comporte un intrados (22) et un extrados (23), et dans lequel l'intrados (22) et l'extrados (23) de chaque aube (6, 6') sont délimités par un bord d'attaque de l'aube (8) et par un bord de fuite de l'aube (8') de cette aube (6, 6'), un nombre d'ouvertures d'équilibrage de pression (7, 7'), lesquelles sont pratiquées dans au moins une des deux parois latérales (3, 4) de la section de canal de diffuseur (2), dans lequel chacune parmi le nombre d'ouvertures d'équilibrage de pression (7, 7') est agencée entre l'intrados (22) d'une aube (6) et l'extrados (23) de l'aube contiguë (6') de la couronne d'aubes (5),
    un premier canal annulaire (10), lequel est agencé derrière les ouvertures d'équilibrage de pression (7, 7'), dans lequel le premier canal annulaire (10) est relié fluidiquement à la section de canal de diffuseur (2) par le biais d'au moins deux des ouvertures d'équilibrage de pression (7, 7'), de sorte qu'un nombre de passages du diffuseur (1) peuvent être reliés fluidiquement l'un à l'autre, dans lequel une zone entre deux aubes contiguës (6, 6') de la couronne d'aubes (5) dans la section de canal de diffuseur (2) est désignée comme passage de diffuseur, et le diffuseur étant caractérisé en ce que le nombre d'ouvertures d'équilibrage de pression (7, 7'), lesquelles sont pratiquées dans au moins une des deux parois latérales (3, 4) de la section de canal de diffuseur (2), sont agencées dans une zone de la paroi latérale respective (3, 4), dans laquelle la première paroi latérale (3) et la deuxième paroi latérale (4) sont agencées de manière divergente l'une par rapport à l'autre dans la direction du courant.
  2. Diffuseur selon la revendication 1, dans lequel le premier canal annulaire (10) est pratiqué dans une des deux parois latérales (3, 4) de la section de canal de diffuseur (2).
  3. Diffuseur selon l'une des revendications précédentes, dans lequel les ouvertures d'équilibrage de pression (7, 7') sont réalisées respectivement comme perforations et/ou comme fentes.
  4. Diffuseur selon l'une des revendications précédentes, dans lequel l'orientation de chacune des ouvertures d'équilibrage de pression (7, 7') dans la paroi latérale respective (3, 4) de la section de canal de diffuseur (2) est déterminée par un angle d'inclinaison (54), lequel est défini comme l'angle d'inclinaison (54) de l'ouverture d'équilibrage de pression respective (7, 7') par rapport à la surface de cette paroi latérale (3, 4) faisant face à la section de canal de diffuseur (2).
  5. Diffuseur selon l'une des revendications précédentes, dans lequel le premier canal annulaire (10) est subdivisé par des moyens de séparation (13) en un nombre de zones de canal partielles (11, 11'), individuelles et séparées les unes des autres, du premier canal annulaire (10).
  6. Diffuseur selon la revendication 5, dans lequel chaque zone de canal partielle (11, 11') du premier canal annulaire (10) comprend au moins deux ouvertures d'équilibrage de pression (7, 7').
  7. Diffuseur selon l'une des revendications précédentes, dans lequel au moins un deuxième canal annulaire (20) est pratiqué dans une des parois latérales (3, 4) de la section de canal de diffuseur (2) dotées d'ouvertures d'équilibrage de pression (7, 7'), de sorte que les passages de diffuseur de deux aubes non contiguës (6, 6'') de la couronne d'aubes (5) peuvent être reliés fluidiquement l'un à l'autre.
  8. Diffuseur selon l'une des revendications précédentes, dans lequel la première ou la deuxième paroi latérale (3, 4) de la section de canal de diffuseur (2) est réalisée comme une plaque de diffuseur (12), dans lequel le nombre des ouvertures d'équilibrage de pression (7, 7') et au moins un canal annulaire (10, 20) sont pratiqués dans la plaque de diffuseur (12).
  9. Diffuseur selon la revendication 1, dans lequel le premier canal annulaire (10) peut être relié à un plénum de pression (31) par le biais d'un canal de raccordement (30), de sorte qu'un fluide peut s'écouler du plénum de pression (31) dans le premier canal annulaire (10), le premier canal annulaire (10) étant ainsi purgé avec le fluide.
  10. Diffuseur selon la revendication 9, dans lequel le plénum de pression (31) est relié à une source de fluide (35), dans lequel la source de fluide (35) est réalisée pour fournir du fluide pour le plénum de pression (31).
  11. Diffuseur selon la revendication 10, dans lequel la source de fluide (35) est réalisée comme un refroidisseur d'air de suralimentation, dans lequel le refroidisseur d'air de suralimentation est réalisé pour fournir du fluide, et dans lequel le fluide peut être introduit dans le plénum de pression (31) depuis le refroidisseur d'air de suralimentation.
  12. Diffuseur selon l'une des revendications 10 et 11, dans lequel un système de filtre (39) est installé entre le plénum de pression (31) et la source de fluide (35) afin de purifier le fluide.
  13. Compresseur centrifuge (100) doté d'un diffuseur (1) selon l'une des revendications 1 à 12.
  14. Système de turbocompresseur (150), comprenant un compresseur centrifuge selon la revendication 13.
EP15823510.1A 2014-12-23 2015-12-22 Diffuseur pour un compresseur centrifuge Active EP3237760B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102014119562.0A DE102014119562A1 (de) 2014-12-23 2014-12-23 Diffusor für einen Radialverdichter
DE102014119558.2A DE102014119558A1 (de) 2014-12-23 2014-12-23 Diffusor für einen Radialverdichter
PCT/EP2015/081037 WO2016102594A1 (fr) 2014-12-23 2015-12-22 Diffuseur pour compresseur radial

Publications (2)

Publication Number Publication Date
EP3237760A1 EP3237760A1 (fr) 2017-11-01
EP3237760B1 true EP3237760B1 (fr) 2020-02-05

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US (1) US10473115B2 (fr)
EP (1) EP3237760B1 (fr)
JP (1) JP7105563B2 (fr)
KR (1) KR102511426B1 (fr)
CN (1) CN107110178B (fr)
WO (1) WO2016102594A1 (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102017114007A1 (de) 2017-06-23 2018-12-27 Abb Turbo Systems Ag Diffusor für einen Radialverdichter
DE102017118950A1 (de) * 2017-08-18 2019-02-21 Abb Turbo Systems Ag Diffusor für einen Radialverdichter
US11143201B2 (en) * 2019-03-15 2021-10-12 Pratt & Whitney Canada Corp. Impeller tip cavity
US11268536B1 (en) 2020-09-08 2022-03-08 Pratt & Whitney Canada Corp. Impeller exducer cavity with flow recirculation
GB202213999D0 (en) * 2022-09-26 2022-11-09 Rolls Royce Plc Dynamic sealing assembly

Family Cites Families (24)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4164845A (en) * 1974-10-16 1979-08-21 Avco Corporation Rotary compressors
US3997281A (en) * 1975-01-22 1976-12-14 Atkinson Robert P Vaned diffuser and method
US4131389A (en) 1975-11-28 1978-12-26 The Garrett Corporation Centrifugal compressor with improved range
US4368005A (en) * 1977-05-09 1983-01-11 Avco Corporation Rotary compressors
AU533765B2 (en) * 1978-11-20 1983-12-08 Avco Corporation Surge control in gas; turbine
JPS5572698A (en) * 1978-11-29 1980-05-31 Avco Corp Rotary compressor
JPS59192899A (ja) * 1983-04-15 1984-11-01 Hitachi Ltd 遠心形タ−ボ機械の羽根付デイフユ−ザ
CA1252075A (fr) * 1983-09-22 1989-04-04 Dresser Industries, Inc. Configuration de diffuseur pour compresseur centrifuge
US4579509A (en) * 1983-09-22 1986-04-01 Dresser Industries, Inc. Diffuser construction for a centrifugal compressor
FR2698666B1 (fr) * 1992-11-30 1995-02-17 Europ Propulsion Pompe centrifuge hautement performante à rouet ouvert.
JPH06288397A (ja) * 1993-04-08 1994-10-11 Hitachi Ltd 遠心圧縮機の騒音低減装置
US6168375B1 (en) * 1998-10-01 2001-01-02 Alliedsignal Inc. Spring-loaded vaned diffuser
CN100374733C (zh) * 2004-02-23 2008-03-12 孙敏超 一种径向单列叶片扩压器
JP4146371B2 (ja) 2004-02-27 2008-09-10 三菱重工業株式会社 遠心圧縮機
US20070196206A1 (en) 2006-02-17 2007-08-23 Honeywell International, Inc. Pressure load compressor diffuser
EP2014925A1 (fr) 2007-07-12 2009-01-14 ABB Turbo Systems AG Diffuseur pour compresseur radial
CN101092976A (zh) * 2007-07-30 2007-12-26 北京航空航天大学 离心压气机扩压器叶片内引气流动控制增效装置
JP4952463B2 (ja) * 2007-09-13 2012-06-13 株式会社Ｉｈｉ 遠心圧縮機
DE102008044505B4 (de) 2008-09-08 2010-07-01 Friedrich-Alexander-Universität Erlangen-Nürnberg Radialverdichter
US8235648B2 (en) * 2008-09-26 2012-08-07 Pratt & Whitney Canada Corp. Diffuser with enhanced surge margin
EP2676814B1 (fr) 2011-02-17 2017-03-29 Bridgestone Corporation Pneu
DE102011005025A1 (de) 2011-03-03 2012-09-06 Siemens Aktiengesellschaft Resonatorschalldämpfer für eine radiale Strömungsmaschine, insbesondere für einen Radialverdichter
JP6138470B2 (ja) 2012-12-07 2017-05-31 三菱重工業株式会社 遠心圧縮機
JP5575308B2 (ja) * 2013-07-08 2014-08-20 三菱重工業株式会社 遠心圧縮機

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

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Publication number Publication date
CN107110178B (zh) 2020-03-10
KR102511426B1 (ko) 2023-03-17
EP3237760A1 (fr) 2017-11-01
KR20170096636A (ko) 2017-08-24
US20170284401A1 (en) 2017-10-05
WO2016102594A1 (fr) 2016-06-30
US10473115B2 (en) 2019-11-12
CN107110178A (zh) 2017-08-29
JP2018500502A (ja) 2018-01-11
JP7105563B2 (ja) 2022-07-25

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