EP2342465A1 - Soufflante à canal latéral, en particulier turbine secondaire pour un moteur à combustion interne - Google Patents
Soufflante à canal latéral, en particulier turbine secondaire pour un moteur à combustion interneInfo
- Publication number
- EP2342465A1 EP2342465A1 EP09782660A EP09782660A EP2342465A1 EP 2342465 A1 EP2342465 A1 EP 2342465A1 EP 09782660 A EP09782660 A EP 09782660A EP 09782660 A EP09782660 A EP 09782660A EP 2342465 A1 EP2342465 A1 EP 2342465A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- impeller
- blower
- inlet
- channel
- region
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 238000002485 combustion reaction Methods 0.000 title claims description 10
- 230000010349 pulsation Effects 0.000 description 9
- 239000012530 fluid Substances 0.000 description 3
- 230000002093 peripheral effect Effects 0.000 description 2
- 238000010408 sweeping Methods 0.000 description 2
- 230000001133 acceleration Effects 0.000 description 1
- 230000006978 adaptation Effects 0.000 description 1
- 239000000446 fuel Substances 0.000 description 1
- 238000005457 optimization Methods 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
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
- F04D23/00—Other rotary non-positive-displacement pumps
- F04D23/008—Regenerative 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
- F04D29/08—Sealings
- F04D29/16—Sealings between pressure and suction sides
- F04D29/161—Sealings between pressure and suction sides 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
- F04D5/00—Pumps with circumferential or transverse flow
- F04D5/002—Regenerative pumps
- F04D5/007—Details of the inlet or outlet
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
- F05B2250/00—Geometry
- F05B2250/50—Inlet or outlet
- F05B2250/503—Inlet or outlet of regenerative pumps
Definitions
- the invention relates to a side channel blower, in particular secondary air blower for an internal combustion engine with a housing in which an outlet is formed, a first housing part, in which an axial inlet is formed, which opens via an inlet region in a first, substantially annularly extending conveying channel, an impeller which is drivable via a drive unit, is rotatably mounted in the housing and has conveying blades, which cooperate with the opposite conveyor channel, an interruption area between the inlet and the outlet, in which the conveyor channel is interrupted in the circumferential direction, and a recess which in Direction of rotation of the impeller is formed in front of the inlet region at the interruption region and is fluidly connected to the inlet region.
- Running direction of the impeller are as far apart as possible, with a
- Interruption area is to be prevented.
- the high noise has been found, which arises in particular by pulsations caused by sudden
- Inlet area can suddenly relax towards the inlet in the inlet area. This leads both to a poorer efficiency of the pump and to significantly increased noise emissions.
- DE 10 2004 019 868 A1 proposes a fan in which the interruption area is designed in such a way that the pockets sweeping over the interruption area are not opened at the same time over their entire cross-section, but first only in their radial outer area and only then as the movement progresses, a further opening of the pockets also follows in the radially inner region.
- the inlet itself is arranged in the radially inner region, so that the expansion of the delivered fluid does not take place directly above the inlet.
- the inlet is partially covered by the interruption area.
- noise even though reduced, is created by pressure pulsations because sudden cross-sectional changes occur downstream of the break region for partial volumes of the volume delivered in the pockets upon reaching the inlet region.
- These pressure pulsations continue from radially outward to radially inward as they reach the inlet region through the respective part of the pocket.
- This object is achieved in that the depth of the recess from the impeller facing the upper edge of the interruption area grows toward the inlet area. As a result, a sudden relaxation of a partial volume of the conveyed between the blades and air thus resulting pressure pulsations is reliably avoided.
- the air conveyed over the interruption area can relax steadily with rotation of the impeller. A restriction of the inlet cross-section of the inlet is no longer required, so that larger amounts of air can be sucked.
- the recess is in the form of a chamfer extending from the interruption region in the direction of the inlet. This form provides a steady extension of the cross-section for the air delivered over the break region for slow continuous relaxation.
- the width of the recess is equal to the width of the conveyor channel. In this way, pressure pulsations can be further reduced, since the volume is continuously increased over the entire relevant flow cross-section of the conveyor blade interspace lying opposite the recess. It when the length of the recess in the circumferential direction is greater than the distance between two successive blades of the impeller is particularly advantageous. In such an embodiment, it is ensured that first of all a relaxation of the entire volume conveyed over the interruption region takes place before the entire cross section of the inlet region is made available to a partial volume, which would again lead to a change in flow and thus to pressure pulsations.
- the length of the recess in the circumferential direction corresponds to> 1 times the distance between two successive blades of the impeller.
- the diameter of the inlet region is greater than the width of the conveying channel, wherein the shortest distance of an inner edge of the inlet region is equal to the distance of the inner edge of the conveying channel.
- the housing consists of the first housing part, which serves as a cover part, and at least a second housing part in which a second substantially annular extending delivery channel is arranged, which opens into the outlet, which is arranged tangentially to the second housing part, wherein the conveying blades of the impeller facing the delivery channels to both axial sides of the impeller.
- This version is a two-channel blower, which further improves efficiency compared to single-duct blowers. It is thus a side channel blower created in which compared to known side channel blowers the flow rate can be increased with the same size of the pump and at the same time outwardly urgent noise can be largely avoided by occurring pressure pulsations.
- Figure 1 shows a side view of a side channel blower in a sectional view.
- FIG. 2 shows a perspective view of the cover part of the side channel blower according to the invention from FIG. 1.
- Figure 3 shows a plan view of the lid part according to the figure 2 from the direction of the impeller.
- FIG. 4 shows a sectional illustration along the section line A-A of FIG. 3.
- FIG. 5 shows a sectional illustration along the section line B-B of FIG. 3.
- the side channel blower shown in Figure 1 consists of a two-part housing 2 and a rotatably mounted in the housing 2 and driven by a drive unit 3 impeller 4, for example for the promotion of air.
- the air passes via an axial inlet 6 into an inlet region 8 of a first housing part 10, which serves in the present embodiment as a cover part of the side channel blower. From the inlet region 8, the air then flows into two substantially annularly extending conveying channels 12, 14, of which the first conveying channel 12 is formed in the cover part 10 and the second conveying channel 14 is formed in a second housing part 16, in which also a bearing 18 a drive shaft 19 of the drive unit 3 is arranged, on which the impeller 4 is fixed.
- the exit of the air takes place via a tangential outlet 20, which is arranged on the second housing part 16.
- the impeller 4 is disposed between the cover member 10 and the second housing member 16 and has at its periphery conveying blades 22 which are curved and extend radially, wherein the conveying blades 22 by a radially extending peripheral ring 24 in a first row axially opposite to the first Delivery channel 12 and a second row axially opposite to the second conveying channel 14 are divided, so that two swirl ducts are formed, which are each formed by one of the conveying channels 12, 14 with the facing part of the impeller 4.
- the outer diameter of the conveying channels 12, 14 is slightly larger than the outer diameter of the impeller 4, so that a fluidic connection between the two conveying channels 12, 14 outside the outer periphery of the impeller 4 is made. Between the extending from the peripheral ring 24 conveyor blades 22 are thus formed radially outwardly open pockets 26, in which the air is promoted or accelerated.
- Cover part 10 and arranged on the housing part 16, in which the delivery channels 12, 14 are interrupted, so that in the interruption region 28 axially opposite to the conveying blades 22 of the impeller 4 as small a gap as possible.
- the delivery channel 12 arranged in the cover part 10 has a substantially constant width b and coincides with
- interruption region 28 extends over the circumference of the lid part. In the view selected here, thus, the impeller 4 rotates in
- the cover part 10 is fastened by means of screws to the second housing part 16, which are inserted through corresponding bores 30 which are formed on radially outwardly extending projections 32 on the cover part 10. At two of these projections 32 are additionally small, axially extending bolts 34, which serve for the prefixing of the cover part 10 on the second housing part 16.
- a groove 38 is formed in the seal between the cover part 10 and the second housing part 16, a sealing ring 40 is inserted, which is held by lugs 42 in the groove 38.
- an annular ridge 46 is formed, which engages after assembly of the fan in a corresponding groove 48 of the impeller 4, whereby a seal from the conveying channel 12 in the direction of the interior of the impeller 4 takes place.
- the cover part 13 has a cylindrical recess 50 into which the drive shaft 19 of the drive unit 3 protrudes.
- a recess 52 is formed in front of the inlet region 8, which extends from an upper edge 54 of the interruption region 28 in the direction of the inlet region 8.
- the recess 52 is designed so that its cross-sectional area grows steadily in the direction of the inlet region 8, wherein in the present embodiment, the width b of the recess 52 over the entire length about the width b of the conveying channel 12 corresponds, so that the growing cross-section by a change the depth is realized, which grows to the inlet portion 8 to a depth corresponding to the depth of the conveying channel 12.
- the recess 52 thus has a constant angle to the surface of the interruption region 28, so that it is formed substantially as a chamfer.
- An end region 54 of the delivery channel 12 is formed substantially corresponding to the tangential outlet 20, so that the end wall 56 delimiting the channel 12 substantially forms an extension of the outlet 12.
- the inlet 6 has to increase the delivery volume has a diameter d which is greater than the width b of the conveying channel 12, wherein an inner edge 58 of the inlet portion 8 is disposed at an equal radius as an inner edge 59 of the conveying channel 12, so that the cover part 10th in the inlet region 8 has a larger circumference than in the other areas.
- This also has the consequence that the recess 52 does not extend over the entire diameter d of the inlet region 8, but the recess 52 is bounded by a radially delimiting outer wall 60, which extends substantially axially.
- a front edge 62 which forms the line of intersection of the interruption region 28 with the recess 52, formed arcuate, so that the conveyor blades 22 of the impeller 4, the recess 52 first in the radially outer region and then in the radially inner region.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102008056105A DE102008056105B4 (de) | 2008-11-06 | 2008-11-06 | Seitenkanalgebläse, insbesondere Sekundärluftgebläse für eine Verbrennungskraftmaschine |
PCT/EP2009/061514 WO2010052044A1 (fr) | 2008-11-06 | 2009-09-07 | Soufflante à canal latéral, en particulier turbine secondaire pour un moteur à combustion interne |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2342465A1 true EP2342465A1 (fr) | 2011-07-13 |
EP2342465B1 EP2342465B1 (fr) | 2019-09-04 |
Family
ID=41571300
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP09782660.6A Active EP2342465B1 (fr) | 2008-11-06 | 2009-09-07 | Soufflante à canal latéral, en particulier turbine secondaire pour un moteur à combustion interne |
Country Status (3)
Country | Link |
---|---|
EP (1) | EP2342465B1 (fr) |
DE (1) | DE102008056105B4 (fr) |
WO (1) | WO2010052044A1 (fr) |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102010046870B4 (de) * | 2010-09-29 | 2016-09-22 | Pierburg Gmbh | Seitenkanalgebläse, insbesondere Sekundärluftgebläse für eine Verbrennungskraftmaschine |
DE102013220668A1 (de) * | 2013-10-14 | 2015-04-16 | Continental Automotive Gmbh | Laufrad für eine insbesondere als Seitenkanalgebläse ausgebildete Seitenkanal-Strömungsmaschine |
Family Cites Families (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE902074C (de) * | 1937-08-08 | 1954-01-18 | Fritz Oesterlen Dr Ing | Umlaufverdichter mit einem gleichachsig zum Laufrad gelegenen Seitenkanal |
US3252421A (en) * | 1962-10-16 | 1966-05-24 | Siemen & Hinsch Gmbh | Pumps |
US3356033A (en) * | 1965-10-22 | 1967-12-05 | Ford Motor Co | Centrifugal fluid pump |
NL7416205A (nl) | 1974-02-26 | 1975-08-28 | Siemens Ag | Ringvormige compressor. |
DE2531740C2 (de) * | 1975-07-16 | 1989-08-10 | British Gas Corp., London | Seitenkanalgebläse |
DE3822267A1 (de) * | 1988-03-06 | 1989-12-07 | Webasto Ag Fahrzeugtechnik | Ringkanalgeblaese |
DE4230014C1 (de) * | 1992-09-08 | 1994-03-24 | Eberspaecher J | Vorrichtung zur Reduzierung der Geräuschentwicklung bei Gebläsen |
DE4424629C1 (de) * | 1994-07-13 | 1995-03-09 | Becker Kg Gebr | Seitenkanalverdichter |
DE102004019868A1 (de) | 2004-04-23 | 2005-11-24 | J. Eberspächer GmbH & Co. KG | Gebläse, insbesondere Verbrennungsluftgebläse für ein Heizgerät |
-
2008
- 2008-11-06 DE DE102008056105A patent/DE102008056105B4/de active Active
-
2009
- 2009-09-07 WO PCT/EP2009/061514 patent/WO2010052044A1/fr active Application Filing
- 2009-09-07 EP EP09782660.6A patent/EP2342465B1/fr active Active
Also Published As
Publication number | Publication date |
---|---|
DE102008056105B4 (de) | 2011-02-03 |
EP2342465B1 (fr) | 2019-09-04 |
DE102008056105A1 (de) | 2010-05-20 |
WO2010052044A1 (fr) | 2010-05-14 |
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