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
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
  • F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
• • 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
  • F04D29/426—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for liquid pumps
  • F04D29/4293—Details of fluid inlet or outlet
• • 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
  • 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
• • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
  • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
  • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
  • Y02T10/00—Road transport of goods or passengers
  • Y02T10/10—Internal combustion engine [ICE] based vehicles
  • Y02T10/12—Improving ICE efficiencies

Definitions

• the invention relates to the field of compressors, in particular centrifugal compressors and diagonal compressors.
• the invention relates to an outflow region downstream of a compressor wheel and upstream of a diffuser region of such a compressor.
• Exhaust gas turbochargers are used as standard nowadays to increase the performance of an internal combustion engine, with a turbine in the exhaust tract of the internal combustion engine and with a compressor upstream of the internal combustion engine.
• the exhaust gases from the internal combustion engine are expanded in the turbine.
• the work gained in this way is transmitted to the compressor by means of a shaft, which compresses the air supplied to the internal combustion engine.
• Compressors especially of radial or diagonal compressors, with high swallowing compressor wheels have high ratios of the
• compressor wheel hub design should preferably be made slim in order to keep the centrifugal load below the mechanical material limits.
• a slim designed hub typically leads to a small exit angle of the compressor wheel hub contour (measured to the radial). If the meridional channel in the diffuser is conventional
• the object of the present invention is to provide an outflow region of a compressor, a compressor and a turbocharger, which is improved with regard to at least one of the disadvantages known from the prior art.
• an outflow area is used a compressor, in particular a radial compressor or diagonal compressor, according to the independent claim 1 is provided. Furthermore, a compressor with an outflow area according to the embodiments described herein and a turbocharger with such a compressor are provided.
• an outflow region of a compressor in particular a radial compressor or diagonal compressor, is provided.
• the outflow area comprises a flow channel which is delimited by a shroud-side side wall and a hub-side side wall:
• the hub-side side wall has a contour in an area of the compressor wheel outlet which is designed in such a way that the cross-sectional areas of the flow channel decrease in the flow direction, pass through a minimum and again increase.
• the flow channel has a length L which extends from a compressor wheel outlet edge to a diffuser blade inlet edge of a diffuser area.
• the diffuser area adjoins the area of the compressor wheel outlet and has a large number of diffuser blades.
• an outflow area is advantageously provided which is improved over the prior art.
• the variability of the sidewall contour on the hub side enables an advantageous cross-sectional profile (decrease - minimum - increase) of the flow channel to be implemented so that the flow upstream of a diffuser area can be more strongly decelerated without the flow on the shroud side becoming detached.
• the curvature at the shroud can first be checked and then the cross-sectional area progression via the stroke Contour (contour of the side wall on the hub side) can be set. This leads to a more compact design and higher levels of efficiency.
• the outflow area according to the invention can reduce the risk of flow separation, which has an advantageous effect on the efficiency of the compressor.
• the outflow area according to the invention can advantageously greatly delay and even out the compressor wheel outlet flow within a compact installation space without the flow tending prematurely to detachment / instability during throttling.
• a compressor in particular a radial compressor or a diagonal compressor, is provided which comprises a compressor wheel and an outflow area according to the embodiments described herein.
• a compressor with improved efficiency can advantageously be provided.
• a turbocharger with a compressor according to the embodiments described herein so that advantageously a turbocharger is provided which is improved over the prior art.
• FIG. 1 shows a schematic view of an outflow area of a compressor, in particular a diagonal compressor, according to the embodiments described herein;
• FIGS. 2 to 5 are schematic views of an outflow area of a Compressor according to further embodiments described herein, a diagonal compressor being shown in FIGS. 2 and 5 and a radial compressor being shown in FIGS. 3 and 4.
• the outflow area 10 comprises a flow channel 11 which is delimited by a shroud-side side wall 12 and a hub-side side wall 13.
• the hub-side side wall 13 has a contour in a region 14 of the compressor wheel outlet which is designed such that the cross-sectional areas, in particular the meridional cross-sectional areas, of the flow channel decrease, pass through a minimum and increase again in the flow direction 1.
• the hub-side side wall 13 is designed in such a way that the flow cross section of the flow channel 11 tapers in the flow direction 1, passes through a minimum and widens again before entering a diffuser region 16.
• the contour of the hub-side side wall 13 is designed such that the distance to the opposite shroud-side side wall 12 decreases in flow direction 1, passes through a minimum and then increases again.
• the flow channel 11 has a length L in the region 14 of the compressor wheel outlet, as is shown in FIGS. 1 to 5.
• the length L of the flow channel 11 extends from a compressor wheel outlet edge 4 to an inlet 5 into the diffuser region 16, in particular as far as a diffuser blade inlet edge of the diffuser area 16 extends.
• the diffuser area 16 adjoins the area 14 of the compressor wheel outlet and has a multiplicity of diffuser blades 17.
• the flow after the compressor wheel can initially be evened out, then delayed to a greater extent and a risk of flow separation reduced, which has an advantageous effect on the efficiency, the structural volume and the costs of the compressor.
• the contour of the hub-side side wall 13 has an S-shaped area 15.
• the contour of the side wall on the hub side has an S-shaped meridional contour course between the compressor wheel outlet and the diffuser inlet.
• the S-beat-like area 15 can be formed, for example, by at least three segments S 1 , S 2 and S 3 , as shown by way of example in FIG. FIG. 4 shows an exemplary embodiment with four segments S 1 , S 2 , S 3 and S 4 .
• the segments can be line segments and / or curve segments. It is thus to be understood that the S-beat-like region 15 can be provided by a polygon-like S-contour.
• the S-beat-like area 15 can also have a continuous contour.
• the contour course can be tangent-continuous or non-tangent-continuous.
• the S-beat-like region 15 can have a right curvature and a left curvature in the direction of flow, as is shown by way of example in FIGS. 1, 2 and 5.
• the S-beat-like region 15 can have a convex curvature pointing towards the shroud-side side wall 12 and a concave curvature.
• the S-flap-like region 15 in the flow direction after the compressor wheel outlet initially has a convex curvature pointing towards the shroud-side side wall 12 and then a concave curve pointing towards the shroud-side side wall 12 Curvature up.
• the shroud-side side wall 12 in the area of the compressor wheel outlet is exclusively convex in relation to the hub-side side wall 13.
• the shroud-side side wall 12 from the compressor wheel outlet to the entry into the diffuser area is exclusively convex compared to the hub-side
• the hub-side side wall 13 in the area 14 of the compressor wheel outlet has a continuous contour, as is shown by way of example in FIGS. 1, 2 and 5.
• the shroud-side side wall 12 in the area 14 of the compressor wheel outlet can have a continuous contour, as shown in FIGS. 1 to 5.
• the shroud-side side wall 12 is curved to the left in the direction of flow 1.
• the S-impact-like area 15 is arranged closer to the compressor wheel outlet edge 4 than at the inlet 5 of the diffuser area.
• the S-flap-like area 15 can be arranged after the compressor wheel trailing edge within 50% of the length L of the flow channel 11.
• the change in curvature of the hub-side side wall 13 provided by the S-flare is arranged closer to the compressor wheel outlet edge 4 than to the inlet 5 of the diffuser area.
• the location of the change of curvature is the turning point at which one of the convex curvature of the hub-side wall 13 pointing towards the shroud-side side wall 12 merges into a concave curvature of the hub-side side wall 13 pointing towards the shroud-side side wall 12.
• the location of the change in curvature is the place where the curvature changes its sign.
• the flow cross section which is created by the S-shaped area 15 of the flow channel 1! is formed, be arranged within 50% of the length L of the flow channel 11 after the compressor wheel outlet edge. In other words, the flow cross-section minimum is typically arranged closer to the compressor wheel outlet edge 4 than to the inlet 5 of the diffuser area.
• the flow channel 11 has a compression wheel outlet cross-sectional area A 2 and a diffuser outlet cross-sectional area A 3 , with a ratio A3 / A2 from a range of 0.80 A 3 / A 2 1.2, in particular from a range of 0.90 A 3 / A 2 1.1.
• the compressor wheel outlet cross-sectional area A2 is a cylinder surface (if the compressor wheel outlet edge runs parallel to the axis of rotation) or a conical surface (if the compressor wheel outlet edge is inclined to the axis of rotation) downstream of the twisted wheel outlet edge 4. in the case of a diffuser inlet edge inclined to the axis of rotation).
• the cross-sectional areas of the flow channel which decrease in the direction of flow, pass through a minimum and increase again, can be cylindrical surfaces and / or conical surfaces.
• a gap 3 (eg a leakage flow opening) can be formed in the hub-side wall 13, in particular at the compressor wheel outlet .
• the minimum of the cross-sectional areas of the flow channel 11 is in
• R 2 is the compressor wheel outlet radius
• Rj is the radial distance between the inlet 5 in the diffuser area and the axis of rotation 2 of the compressor wheel 21.
• a ratio VQ is the minimum of the cross-sectional areas of the
• Flow channel 11 to the compressor wheel outlet cross-sectional area Ai is selected from a range 0.8 ⁇ VQ ⁇ 1, in particular 0.9 ⁇ VQ ⁇ 1,
• the 5-stroke-like area 15 has a change of curvature from the convex curvature pointing to the shroud side wall 12 to the shroud side wall 12 showing concave curvature, which in a radial position new, which is from a range R 2 ⁇ r KW ⁇ R 2 + 0.8 ⁇ (R 3 -R 2 ), in particular R 2 ⁇ r KW ⁇ R 2 + 0.6 ⁇ (R 3 -R 2 ), is selected, R 2 is the compressor wheel outlet radius and Ra is the radial distance between the inlet 5 in the diffuser region and the axis of rotation 2 of the compressor wheel 21.
• the convex curvature has a curvature maximum at a radial position r Kmax , which is from a range R 2 ⁇ r Kmax R R 2 + 0.75 ⁇ (R 3 -R 2 ), in particular R 2 ⁇ r Kmax R 2 + 0.5 ⁇ (R 3 -R 2 ).
• the curvature maximum is to be understood as the greatest positive curvature value.
• the concave curvature has a curvature minimum at a radial position r Kmin, which can be selected from a range R 2 + 0.15 ⁇ (R 3 -R 2 ) r Kmin ⁇ R 3 , in particular R 2 + 0.25 ⁇ (R 3 -R 2 ) ⁇ r Kmin ⁇ R 3 is selected.
• the curvature minimum is to be understood as the greatest negative curvature value.
• r Kmax is selected from the range R 2 ⁇ r Kmax ⁇ R 2 + 0 75 x (R 3 -R 2 ) and r Kmin from the range R 2 + 0.15 x ( R 3 -R 2 ) r Kmin ⁇ R3, typically r Kmax and r Kmin are chosen such that r Kmax ⁇ r Kmin .
• Meridional cross-sectional areas of the flow channel are, in particular the
• the main flow direction runs along the center line between the shroud-side side wall 12 and the hub-side side wall 13.
• a compressor 20 in particular a radial compressor or a diagonal compressor, is provided which comprises a compressor wheel 21 and an outflow region 10 according to the embodiments described herein,
• the compressor wheel 21 has a compressor wheel inlet radius R 2 and a
• Compressor wheel outlet radius R 2 Compressor wheel outlet radius R 2 .
• a ratio of the compressor wheel inlet radius R 1 to the compressor wheel outlet radius R 2 is typically selected from a range of 0.65 R 1 / R 2 , in particular from a range of 0.7 ⁇ R 1 / R 2 .
• the compressor comprises a diffuser area 16 which is arranged from an axis of rotation 2 of the compressor wheel 21 at a radial distance R 3 , typically a ratio of the radial distance R 3 to the compressor wheel outlet radius Ra from a range of 1.05 ⁇ R 3 / R 2 1.30, in particular from a range of 1.10 R 3 / R 2 1.25.
• the contour of the hub-side side wall 13 comprises an S-beat-like area 15 according to one of the embodiments described herein, as is shown by way of example in Figure 5, the S-beat like area 15 have one end at a distance Rs from the axis of rotation 2 of the compressor wheel 21 in the direction of flow.
• the distance R S , the compressor wheel outlet radius R 2 and the radial distance R 3 of the diffuser region 16 from the axis of rotation 2 of the compressor wheel 21 can be selected such that the condition 0.4 (R s -R 2 ) / (R 3 - R 2 ) ⁇ 1.0 is fulfilled.
• a turbocharger can thus be provided according to a further aspect, which comprises a compressor 20, in particular a radial compressor or a diagonal compressor, according to the embodiments described herein.
• a compressor 20 in particular a radial compressor or a diagonal compressor, according to the embodiments described herein.
• the features that are described in connection with the exemplary embodiments of the radial compressor can also be transferred to the exemplary embodiments of the diagonal compressor (FIGS. 1 and 5) and vice versa.
• the embodiments described herein are in particular advantageous for high-swallowing radial or diagonal compressors.
• the discharge of the compressor wheel can advantageously be guided, evened out and delayed to a greater extent in a small installation space.
• a guide grille diifiusor vanes
• either the guide vanes can be pushed closer to the impeller or the Mach number level at the diffuser vane leading edges can be further reduced.
• the reduction in the Mach number and the equalization of the diffuser blade inflow lead to an increase in efficiency.
• the equalization of the flow and the possibility of reducing the contour curvature on the shroud side lead to improvements in stability.
• the embodiments described herein can have the following advantages. Continuous, in particular tangential continuous, as well as non-continuous, in particular non-tangential continuous, stroke-contour curves are possible, which reduce the risk of flow separation and are advantageous in terms of efficiency.
• the shroud contour curvature in the meridional view can be reduced without reducing the flow area too much. The risk of flow separation at the shroud can thus be reduced without the radial component of the flow being accelerated too much on average.
• the surface course in the diffuser (downstream of the compressor wheel) can be designed specifically so that the exchange of momentum on the Shroud side is required (by reducing the Shroud curvature and by the pinch area formed with the stroke and Shroud contour) and the Flow at the hub (e.g. upstream of the diffuser blade leading edge) is delayed to the maximum.
• the compressor wheel outlet flow can be greatly delayed and evened out within a compact installation space, without the flow prematurely tending to detach and instability during throttling.

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• Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• General Engineering & Computer Science (AREA)
• Chemical & Material Sciences (AREA)
• Combustion & Propulsion (AREA)
• Structures Of Non-Positive Displacement Pumps (AREA)
• Supercharger (AREA)

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Applications Claiming Priority (2)

Publications (1)

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Citations (4)

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• 2020
  • 2020-01-07 EP EP20150566.6A patent/EP3848590A1/de not_active Withdrawn
• 2021
  • 2021-01-07 JP JP2022541807A patent/JP7700129B2/ja active Active
  • 2021-01-07 CN CN202180008409.6A patent/CN115038878A/zh active Pending
  • 2021-01-07 EP EP21700119.7A patent/EP4088038B8/de active Active
  • 2021-01-07 WO PCT/EP2021/050171 patent/WO2021140142A1/de not_active Ceased
  • 2021-01-07 US US17/791,331 patent/US11885350B2/en active Active
  • 2021-01-07 KR KR1020227026842A patent/KR102902410B1/ko active Active

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