EP2627907A1 - Soufflante à canal latéral, en particulier soufflante d'air secondaire pour un moteur à combustion interne - Google Patents

Soufflante à canal latéral, en particulier soufflante d'air secondaire pour un moteur à combustion interne

Info

Publication number
EP2627907A1
EP2627907A1 EP11749435.1A EP11749435A EP2627907A1 EP 2627907 A1 EP2627907 A1 EP 2627907A1 EP 11749435 A EP11749435 A EP 11749435A EP 2627907 A1 EP2627907 A1 EP 2627907A1
Authority
EP
European Patent Office
Prior art keywords
recess
inlet
impeller
outlet
internal combustion
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
Application number
EP11749435.1A
Other languages
German (de)
English (en)
Other versions
EP2627907B1 (fr
Inventor
Berthold Herrmann
Rainer Peters
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.)
Pierburg GmbH
Original Assignee
Pierburg GmbH
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
Application filed by Pierburg GmbH filed Critical Pierburg GmbH
Publication of EP2627907A1 publication Critical patent/EP2627907A1/fr
Application granted granted Critical
Publication of EP2627907B1 publication Critical patent/EP2627907B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
    • F01D25/24—Casings; Casing parts, e.g. diaphragms, casing fastenings
    • 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
    • F04D29/00—Details, component parts, or accessories
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
    • F04D29/667—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps by influencing the flow pattern, e.g. suppression of turbulence

Definitions

  • the invention relates to a sokanalgebiäse, in particular secondary air blower for an internal combustion engine with a housing in which a substantially tangential outlet is formed, a housing cover in which an axial inlet is formed, at least one conveying channel, via which the inlet is fluidly connected to the outlet an impeller which is drivable via a drive unit, rotatably supported in the housing and has delivery blades, which cooperate with the at least one conveyor channel, and an interruption area between the outlet and the inlet, wherein the at least one conveyor channel is interrupted in the circumferential direction, wherein In the direction of rotation of the impeller behind the outlet at the radially delimiting wall of the interruption region, a first recess is formed.
  • DE 10 2008 24 741 B4 proposes a side air duct for secondary air supply in which a recess in front of the inlet is formed in a housing cover of the housing in the direction of rotation of the impeller, which recess grows steadily toward the inlet and has a width has, which corresponds substantially to the width of the conveying channel.
  • a side channel fan is known from DE 10 2009 006 652 A1, which likewise has a housing part with a delivery channel and a housing cover with a second delivery channel formed on the side of the first delivery channel opposite the impeller.
  • a side channel fan is known from DE 10 2009 006 652 A1, which likewise has a housing part with a delivery channel and a housing cover with a second delivery channel formed on the side of the first delivery channel opposite the impeller.
  • an additional recess is formed behind the outlet in the direction of rotation of the impeller.
  • the second AusOSE extends over the height of the partially formed in the housing cover conveyor channel in the radially delimiting wall of the interruption area, wherein the height of the second recess towards the inlet decreases steadily. So a steady pressure reduction is achieved, so that pressure peaks are prevented.
  • the recess which is formed in the direction of rotation of the impeller in front of the inlet at the interruption area, fluidly connected to the inlet, wherein the depth of the recess from the impeller facing the upper edge of the interruption area to the inlet steadily grows.
  • the width of the Ausappel before the inlet substantially corresponds the radial extent of the delivery blades, thereby avoiding undesirable turbulence at the inlet.
  • the depth of the recess grows radially outward to a boundary edge of the recess steadily, so that in areas of higher velocities of the air more expansion cross-section is available.
  • the boundary edge of the recess in front of the inlet has a first region in which the width of the recess substantially corresponds to the radial extent of the conveying blades and has a second region adjoining the first region in the direction of rotation of the impeller radially angled inside.
  • FIG. 1 shows a side view of a side channel blower according to the invention in a sectional illustration.
  • FIG. 2 shows a perspective view of the housing of the side channel blower of FIG. 1.
  • FIG. 3 shows a perspective view of the housing cover of the side channel blower of FIG. 1.
  • Figure 4 shows a head view in the direction of the housing cover in a sectional view through the housing.
  • the sokanaigebiäse shown in Figure 1 consists of a housing 2 and a rotatably mounted in the housing 2 and driven by a drive unit 4 impeller 6, for example for the promotion of air.
  • the air passes through an axial Einiass 8, which is formed in a housing cover 10, in the interior of the side channel blower.
  • the impeller 6 is arranged between the housing cover 10 and the housing 2 and has on its circumference beneficiaschaufein 24, which are curved, wherein the total extension direction, ie a compound of the foot region with the radially outer end region extends substantially radially to the center of the impeller ,
  • the conveyor blades 24 are divided by a radially extending peripheral ring 26 in a first row axially opposite to the first conveyor channel 12 and a second row axiai opposite to the second conveyor channel 14, so that two vortex channels are formed, each through one of the conveyor channels 12, 14 with the facing part of the impeller 6 are formed.
  • the outer diameter of the delivery channels 12, 14 is slightly larger than the outer diameter of the impeller 6, so that a fluidic connection between the two delivery channels 12, 14th outside the outer periphery of the impeller 6, so that an exchange of air between the two delivery channels 12, 14 can take place.
  • the axial inlet 8 is arranged as far as possible from the tangential outlet 22 in the direction of rotation of the impeller 6.
  • interruption regions 30, 32 are arranged between the inlet 8 and the outlet 22 on the housing cover 10 and on the housing 2, which interrupt the conveying channels 12, 14 that in the interruption areas 30, 32 axially opposite to the conveying blades 24 of the impeller 6 as small as possible gap is present.
  • a working in the radial direction Ünterbrechungs Society 34 is formed on a radially limiting wall 36 of the housing 2, which interrupts a radially outer connection region 37 between the two conveying channels 12, 14.
  • the delivery channels 12, 14 arranged in the housing 2 and in the housing cover 10 have a substantially constant width and, with the exception of the interruption regions 30, 32, extend over the circumference of the housing cover 10 and the housing 2 ,
  • the impeller 6 rotates counterclockwise from the beginning of the delivery channel 12 to the end of the delivery channel 12 or to the outlet 22 and then via the interruption region 30 back to the beginning of the delivery channel 12, which is opposite to the inlet 8
  • the impeller 6 in a clockwise direction is rotated, ie from the inlet 8 via the delivery channel 14 and the interruption area 32 back to the inlet. 8
  • the housing cover 10 according to FIG. 3 is fastened by screws to the housing 2, which are inserted through corresponding bores 38, which are formed on the housing cover 10 on radially outwardly extending projections 40.
  • On two of these projections 40 are additionally small, axially extending bolts 42, which serve for the prefixing of the housing cover 10 on the housing 2, on which corresponding holes 44 are formed, which can be seen in Figure 2.
  • a groove 48 is formed, in which a sealing ring 50 is inserted for sealing between the housing cover 10 and the housing 2, which is held in the groove 48 via lugs 52.
  • the housing cover 10 Radially in front of a wall 54 of the conveying channel 14, an annular web 56 is formed, which engages after assembly of the fan in a corresponding groove 58 of the impeller 6, whereby a seal from the conveying channel 14 in the direction of the interior of the impeller 6.
  • the housing cover 10 has a cylindrical recess 60 into which the drive shaft 20 of the drive unit 4 protrudes.
  • the delivery channels 12, 14 are formed in the housing cover 10 and in the housing 2 in such a way that they extend in the area in front of the outlet 22 in the tangential direction instead of the outlet 22 in the circumferential direction.
  • the width of the conveying channels 12, 14 is less than the width of the outlet 22, so that it is initially flown by the conveying channels 12, 14 only over its radially outer region.
  • An outlet opening 62 which leads through the radially delimiting wall 36 of the housing 2 and the interior of the fan with the outlet 22nd is formed such that in the direction of rotation of the impeller 6, the outlet opening 62 extends into the interruption regions 30, 32 of the Gezzausetefle 2, 10, as can be seen in Figure 2.
  • an outlet edge 64 which extends the outlet opening 62 limited in the direction of rotation of the impeller 4, from an inner edge 66 of the conveyor channel 12 in the housing 2 on the wall 36 obliquely upward, so with an axial component in the direction of the Gescousedeckeis 10 and a component in the direction of rotation of the impeller 6.
  • a first recess 68 is formed immediately behind the outlet opening 62 at the interruption region 34 of the radially delimiting wall 36.
  • This first recess 68 is bounded by a breaker edge 70 in the direction of rotation of the impeller 6, which also extends from the bottom of the housing 2 obliquely upwards, so having an axial component in the direction of the housing cover 10 and a component in the direction of rotation of the impeller 6.
  • the interrupt edge 70 and Ausiasskante 64 are not parallel but are arranged at an angle to each other, for the Austasskante 64, the component in the direction of rotation is greater than for the breaker edge 70. It should be noted that with a larger distance between the blades 24 of the Impeller 6 and the included angle between the interrupt edge 70 and the outlet edge 64 should be selected larger.
  • a second recess 72 connects, which has a smaller Depth of about 1 mm than the first recess 68.
  • the second recess 72 extends from the breaker edge 70 approximately halfway up the wall 36 obliquely upward in the direction of the housing cover 10. The starting point of this recess 72 is thus approximately equal to the peripheral ring 26 of the impeller 6, so that it is formed in the region of the swirl duct to which the second delivery channel 14 in the housing cover 10 belongs.
  • the recess 72 is steadily smaller by the oblique formation in the direction of the inlet 8 and has a circumferential length which corresponds approximately to 5 times the distance between two conveying blades 24.
  • the velocity vector of this residual air has a component radially outward, a component in the direction of rotation of the impeller 6 and a component in the direction of the housing cover 10, while the component of the air flow in the circumferential direction substantially corresponds to the speed component of the impeller 6. It follows that due to the selected maximum extent of the outlet opening 62 in the direction of rotation of the bag 28th outflowing air does not abut against the outlet edge 64 of the Ausiassö réelle 62 in the form of a pressure surge, but flows into the outlet 22.
  • the air flowing out behind the outlet opening 62 also does not strike immediately against the interruption region 34 on the radial wall 36 but flows into the recess 68, where at least a slight relaxation takes place by turbulence of the air entering the recess 68.
  • the Winkei is chosen so that neither the simultaneously over the entire height of the bag 28 ejected air flow reaches the breaker edge 70 at the same time still reached over the entire width simultaneously ejected air flow.
  • the expansion path for the existing residual air increases. So pressure surges can be additionally reduced.
  • the outlet valve is closed, however, pressure pulsations continue to develop in the region of the outlet 22, leading to unwanted noise in the inlet 8, unless the second recess 72 is additionally formed.
  • this second recess 72 By means of this second recess 72, the pulsations amplified by the closure of the outlet 22 are reduced by additional vortex formation in the region of the recess 72.
  • the radially outward flowing air receives additional Ausströmqueritese that ensure a reduction of pressure peaks, without a pressure loss by overflows to the inlet 8 would result when the valve is open.
  • a further recess 74 is formed in front of the inlet 8, which extends from an upper edge of the interruption area 32 in the direction of the inlet 8.
  • the recess 74 is designed so that its depth in the direction of the inlet 8 and radially outwardly grows steadily and approximately to a depth corresponding to the depth of the conveying channel 14.
  • the width of the Ausappel 74 corresponds initially in a first region about the width of the delivery channel 14 and the radial extent of the Conveyor blades 24, wherein in a region shortly before the inlet 8, the radial boundary edge 78 of the recess 74 is angled radially inwardly in the direction of rotation of the impeller 6, so that the width is slightly reduced.
  • the recess 74 extends over a length which corresponds approximately to 2.5 times the distance between two successive conveying blades 24 of the impeller 6.
  • the inlet 8 has to increase the delivery volume to a diameter which is greater than the width of the conveying channel 14, wherein an inner edge of the inlet 8 is arranged at an equal radius as an inner edge of the conveying channel 14, so that the cover part 10 at the inlet 8 a larger scale than in the other areas.
  • a front edge 76 which forms the line of intersection of the interruption region 32 with the recess 74, formed arcuate, so that the conveying blades 24 of the impeller 6, the recess 74 initially in the radially outer region and then in the radially inner region.
  • the inlet is bounded by a straight wall 80 which is disposed to the conveyor blades 26 such that an angle of 10-20 ° is formed between the wall 80 and the outwardly facing end of the conveyor blades 24.
  • the radially outer part of each delivery blade 24 passes over the inlet 8.
  • the additionally available space is extended from outside to inside, starting from the highest air speed and compression area.
  • the actual interruption range ie the distance between the rear end of the recess 72 seen in Drehrlchtuhg and the front end of the front edge 76 of the recess 74 is approximately 1.5 times the distance between two impeller blades 24 of the impeller 6 to each other.
  • the described side channel blower is thus characterized by a significant reduction in noise emissions compared to known side channel blowers. At the same time, a high delivery rate is achieved.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Exhaust Gas After Treatment (AREA)

Abstract

On connaît des soufflantes à canal latéral pourvues de dispositifs destinés à réduire à un minimum les émissions sonores, qui ne réduisent cependant pas suffisamment les bruits en cas de fermeture de la vanne de réglage. La présente invention concerne donc une soufflante à canal latéral dans laquelle des évidements (72, 74) supplémentaires sont ménagés dans la zone d'interruption (32, 34) avant l'orifice d'entrée (8) et après l'orifice de sortie (22), dont le plus petit écart entre eux correspond à 0,5 à 3 fois l'écart de deux aubes de refoulement entre elles. Une telle configuration permet d'obtenir une réduction supplémentaire du bruit, même lorsque la vanne de réglage est fermée, sans réduction du flux de refoulement maximal.
EP11749435.1A 2010-09-29 2011-08-31 Soufflante à canal latéral, en particulier soufflante d'air secondaire pour un moteur à combustion interne Active EP2627907B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102010046870.3A DE102010046870B4 (de) 2010-09-29 2010-09-29 Seitenkanalgebläse, insbesondere Sekundärluftgebläse für eine Verbrennungskraftmaschine
PCT/EP2011/065053 WO2012041625A1 (fr) 2010-09-29 2011-08-31 Soufflante à canal latéral, en particulier soufflante d'air secondaire pour un moteur à combustion interne

Publications (2)

Publication Number Publication Date
EP2627907A1 true EP2627907A1 (fr) 2013-08-21
EP2627907B1 EP2627907B1 (fr) 2021-01-20

Family

ID=44532873

Family Applications (1)

Application Number Title Priority Date Filing Date
EP11749435.1A Active EP2627907B1 (fr) 2010-09-29 2011-08-31 Soufflante à canal latéral, en particulier soufflante d'air secondaire pour un moteur à combustion interne

Country Status (6)

Country Link
US (1) US9297276B2 (fr)
EP (1) EP2627907B1 (fr)
JP (1) JP5602950B2 (fr)
CN (1) CN103154523B (fr)
DE (1) DE102010046870B4 (fr)
WO (1) WO2012041625A1 (fr)

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DE102013226563B4 (de) * 2013-12-19 2017-03-09 Eberspächer Climate Control Systems GmbH & Co. KG Gebläsegehäuse, insbesondere für ein Seitenkanalgebläse
DE102014106440A1 (de) * 2014-05-08 2015-11-12 Gebr. Becker Gmbh Laufrad, insbesondere für eine Seitenkanalmaschine
USD785677S1 (en) * 2014-11-11 2017-05-02 Busch Dienste Gmbh Housing element for a regenerative blower
CN104389819B (zh) * 2014-12-01 2017-01-04 重庆德固科技有限公司 一种风机上盖
DE102015100214B4 (de) 2015-01-09 2021-01-14 Pierburg Gmbh Seitenkanalgebläse für eine Verbrennungskraftmaschine
DE102015100215B4 (de) 2015-01-09 2021-01-14 Pierburg Gmbh Seitenkanalgebläse für eine Verbrennungskraftmaschine
DE102015213549A1 (de) 2015-07-17 2017-01-19 Gardner Denver Deutschland Gmbh Seitenkanal-Maschine
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DE102016103525A1 (de) 2016-02-29 2017-08-31 Pierburg Gmbh Gebläse für einen Verbrennungsmotor
CN106286393A (zh) * 2016-09-01 2017-01-04 温州市彼得汽车部件有限公司 一种通过排气驱动的汽车二次空气泵
US11371515B2 (en) 2017-11-03 2022-06-28 Fisher & Paykel Healthcare Limited Regenerative blower
EP3720528B1 (fr) 2017-12-08 2022-05-11 Koninklijke Philips N.V. Système de génération de pression
WO2019120633A1 (fr) * 2017-12-21 2019-06-27 Pierburg Gmbh Compresseurs à canal latéral, en particulier compresseurs d'air secondaires pour un moteur à combustion interne
CN110195633A (zh) * 2019-05-24 2019-09-03 江苏超力电器有限公司 基于无刷电机驱动的二次空气泵
CN112392766B (zh) * 2019-08-15 2023-08-18 广东德昌电机有限公司 侧流道泵
DE102020205531A1 (de) 2020-04-30 2021-11-04 Mahle International Gmbh Seitenkanalverdichter zum Verdichten von Gas
WO2023236011A1 (fr) * 2022-06-06 2023-12-14 广东德昌电机有限公司 Pompe à canal latéral

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Also Published As

Publication number Publication date
EP2627907B1 (fr) 2021-01-20
JP5602950B2 (ja) 2014-10-08
CN103154523B (zh) 2015-10-14
WO2012041625A1 (fr) 2012-04-05
JP2013538977A (ja) 2013-10-17
CN103154523A (zh) 2013-06-12
US20130209247A1 (en) 2013-08-15
US9297276B2 (en) 2016-03-29
DE102010046870B4 (de) 2016-09-22
DE102010046870A1 (de) 2012-03-29

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