EP2627907B1 - 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 Download PDFInfo
- Publication number
- EP2627907B1 EP2627907B1 EP11749435.1A EP11749435A EP2627907B1 EP 2627907 B1 EP2627907 B1 EP 2627907B1 EP 11749435 A EP11749435 A EP 11749435A EP 2627907 B1 EP2627907 B1 EP 2627907B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- recess
- inlet
- impeller
- side channel
- outlet
- 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
Links
- 238000002485 combustion reaction Methods 0.000 title claims description 10
- 239000012530 fluid Substances 0.000 claims description 3
- 230000003247 decreasing effect Effects 0.000 claims description 2
- 238000011144 upstream manufacturing Methods 0.000 claims 1
- 230000010349 pulsation Effects 0.000 description 3
- 238000007789 sealing Methods 0.000 description 3
- 230000015572 biosynthetic process Effects 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 239000000446 fuel Substances 0.000 description 1
- 230000001788 irregular Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
Images
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 side channel blower, in particular a secondary air blower for an internal combustion engine with a housing in which an essentially tangential outlet is formed, a housing cover in which an axial inlet is formed, two conveying channels via which the inlet is fluidically connected to the outlet, an impeller, which can be driven by a drive unit, is rotatably mounted in the housing and has conveyor blades that interact with the conveyor channels, and an interruption area between the outlet and the inlet in which the conveyor channels are interrupted in the circumferential direction, with the impeller behind in the direction of rotation the outlet on the radially delimiting wall of the interruption area, which interrupts a radially outer connection area between the two conveying channels, a first recess is formed.
- Side-channel fans are known in which only one delivery channel is formed on one axial side of the impeller in a housing part, as well as side-channel fans in which a delivery channel is formed on both axial sides of the impeller, with both delivery channels then being fluidically connected to one another.
- one of the delivery channels is formed in a housing part serving as a cover, while the other delivery channel is formed in the housing part to which the drive unit is usually attached, on whose shaft the impeller is at least non-rotatably arranged.
- the DE 100 24 741 B4 A side channel blower for secondary air supply in which a recess is formed in front of the inlet in a housing cover of the housing in the direction of rotation of the impeller, which recess grows steadily towards the inlet and has a width that essentially corresponds to the width of the conveyor channel.
- a side channel blower which also has a housing part with a conveyor channel and a housing cover with a second conveyor channel formed on the side of the first conveyor channel opposite to the impeller.
- a housing part with a conveyor channel
- a housing cover with a second conveyor channel formed on the side of the first conveyor channel opposite to the impeller.
- an additional recess is formed behind the outlet in the direction of rotation of the impeller.
- JP 52-162503 discloses a side channel pump which has small irregular recesses on the walls of the interrupter area, through which a labyrinth seal is created for the water to be pumped, whereby the gaps between the walls and the impeller can remain large.
- Such a labyrinth seal is also in the axially delimiting wall of the side channel pump according to FIG JP 02099796 designed to increase the flow resistance in the gap.
- the US 2005/0220614 A1 discloses a side channel blower which, at the outlet, has recesses on the axially delimiting wall which protrude into the interrupter area.
- a similar side channel blower is used in the JP 56165795 discloses, in which on the axially delimiting wall also juxtaposed slots projecting from the outlet in the interrupter region are formed. In addition, corresponding slots are disclosed in this axially defining wall extending from the inlet into the breaker area.
- the task is therefore to create a side channel blower with which the noises occurring can be significantly reduced even when the valve is closed.
- the first recess in the radially delimiting wall of the interruption region is followed in the direction of rotation by a second recess, the depth of which is less than that of the first recess.
- the second recess extends over the height of the conveying channel, which is partially formed in the housing cover, in the radially delimiting wall of the interruption area, the height of the second recess steadily decreasing in the direction of the inlet. In this way, 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, is fluidically connected to the inlet, the depth of the recess increasing steadily from the upper edge of the interruption area facing the impeller towards the inlet. This also results in continuous relaxation of the air.
- the width of the recess in front of the inlet corresponds essentially to the radial extension of the conveyor blades, as a result of which undesired turbulence at the inlet is avoided.
- the depth of the recess increases steadily radially outwards up to a delimiting edge of the recess, so that more expansion cross-section is available in areas of higher air speeds.
- the delimiting edge of the recess in front of the inlet has a first area in which the width of the recess essentially corresponds to the radial extension of the conveyor blades and has an adjoining second area that extends radially to the first area in the direction of rotation of the impeller is angled inside.
- a side-channel blower is thus created in which the noise emissions are particularly low compared to known side-channel blowers, especially when the control valve is closed, i.e. zero delivery of the pump against a closed valve, while at the same time the maximum possible delivery rate remains largely unchanged.
- the side channel blower shown consists of a housing 2 and an impeller 6 rotatably mounted in the housing 2 and driven by a drive unit 4, for example for conveyance of air.
- the air enters the interior of the side channel blower via an axial inlet 8 which is formed in a housing cover 10.
- the air then flows into two essentially annularly extending conveying channels 12, 14, of which the first conveying channel 12 is formed in the housing 2, in whose central opening 16 a bearing 18 of a drive shaft 20 of the drive unit 4 is also arranged, on which the impeller 6 is attached and the second delivery channel 14 is formed in the housing cover 10.
- the air is discharged via a tangential outlet 22 which is arranged in the housing 2.
- the impeller 6 is arranged between the housing cover 10 and the housing 2 and has conveyor blades 24 on its circumference, which are curved, the overall direction of extent, i.e. a connection between the foot area and the radially outer end area, running essentially radially to the center of the impeller .
- the conveyor blades 24 are divided by a radially extending circumferential ring 26 into a first row axially opposite to the first conveyor channel 12 and a second row axially 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 conveyor channels 12, 14 is slightly larger than the outer diameter of the impeller 6, so that there is a fluidic connection between the two conveyor channels 12, 14 outside the outer circumference of the impeller 6, so that an exchange of air between the two conveyor channels 12, 14 can take place.
- pockets 28 which are open radially outward are thus formed in which the air is conveyed or accelerated, so that its pressure is increased over the length of the conveyor channels 12, 14.
- 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 areas 30, 32 are arranged on the housing cover 10 and on the housing 2, which interrupt the delivery channels 12, 14 so that the smallest possible gap is present in the interruption areas 30, 32 axially opposite the delivery blades 24 of the impeller 6 is.
- an interruption area 34 acting in the radial direction is also formed on a radially delimiting wall 36 of the housing 2, which interrupts a radially outer connecting area 37 between the two conveying channels 12, 14.
- the conveying channels 12, 14 arranged in the housing 2 and in the housing cover 10 have an essentially constant width and, with the exception of the interruption areas 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 conveyor channel 12 to the end of the conveyor channel 12 or to the outlet 22 and then via the interruption area 30 back to the beginning of the conveyor channel 12, which is opposite the inlet 8, while in Figure 3 the impeller 6 is rotated clockwise, that is, 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 Figure 3 is fastened to the housing 2 by means of screws which are inserted through corresponding bores 38 which are formed on projections 40 on the housing cover 10 extending radially outward. On two of these projections 40 there are also small, axially extending bolts 42, which are used to pre-fix the housing cover 10 on the housing 2, on the corresponding bores 44 are formed, which in Figure 2 can be recognized.
- a groove 48 is formed radially behind a wall 46 of the conveying channel 14, into which a sealing ring 50 is inserted for sealing between the housing cover 10 and the housing 2 and is held in the groove 48 via lugs 52.
- An annular web 56 is formed radially in front of a wall 54 of the conveying channel 14, which, after the assembly of the fan, engages in a corresponding groove 58 of the impeller 6, thereby sealing the conveying channel 14 towards 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 conveying channels 12, 14 in the housing cover 10 and in the housing 2 are shaped in such a way that they extend in the area in front of the outlet 22 instead of in the circumferential direction in the direction of the outlet 22, ie in the tangential direction.
- the width of the conveying channels 12, 14 is smaller than the width of the outlet 22, so that the conveying channels 12, 14 initially only flow against it via its radially outer region.
- An outlet opening 62 which leads through the radially delimiting wall 36 of the housing 2 and connects the interior of the fan with the outlet 22, is shaped such that the outlet opening 62 extends into the interruption areas 30, 32 of the housing parts 2, in the direction of rotation of the impeller 6. 10 extends as in Figure 2 can be seen.
- an outlet edge 64 which delimits the outlet opening 62 in the direction of rotation of the impeller 4, extends obliquely upward from an inner edge 66 of the conveying channel 12 in the housing 2 on the wall 36, i.e. with an axial component in the direction of the Housing cover 10 and a component in the direction of rotation of the impeller 6.
- the angle of this slope should be chosen so that the component in the circumferential direction over the height of the outlet opening 62 corresponds at least to the distance between two conveyor blades 24.
- a first recess 68 is formed in the interruption region 34 of the radially delimiting wall 36 immediately behind the outlet opening 62.
- This first recess 68 is limited by an interrupter edge 70 in the direction of rotation of the impeller 6, which also runs obliquely upwards from the bottom of the housing 2, i.e. has an axial component in the direction of the housing cover 10 and a component in the direction of rotation of the impeller 6.
- the interrupter edge 70 and the outlet edge 64 do not run parallel but are arranged at an angle to one another, with the component in the direction of rotation being greater for the outlet edge 64 than for the interrupter edge 70. It should be noted that with a larger distance between the conveyor blades 24 of the Impeller 6 also the included angle between the interrupter edge 70 and the outlet edge 64 should be selected larger.
- the first recess 68 is followed by a second recess 72, which is less than about 1 mm deep than the first recess 68.
- the second recess 72 extends from the interrupter 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 level with the circumferential ring 26 of the impeller 6, so that it is formed in the area of the vortex channel to which the second conveying channel 14 in the housing cover 10 belongs.
- the recess 72 becomes steadily smaller due to the inclined design in the direction of the inlet 8 and has a circumferential length which corresponds approximately to five times the distance between two conveyor blades 24.
- the speed 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.
- the component of the air flow in the circumferential direction essentially corresponds to the speed component of the impeller 6 maximum extension of the outlet opening 62 in the direction of rotation, the air flowing out of the pocket 28 does not strike the outlet edge 64 of the outlet opening 62 in the form of a pressure surge, but rather flows into the outlet 22.
- the air flowing out behind the outlet opening 62 likewise does not strike immediately against the interruption area 34 on the radial wall 36, but rather flows into the recess 68, where at least a slight relaxation takes place due to the turbulence of the air entering the recess 68.
- the angle is chosen such that neither the air stream ejected simultaneously over the entire height of the pocket 28 reaches the interrupter edge 70 at the same time, nor does the air stream ejected simultaneously over the entire width. At the same time the Relaxation path for the remaining air is greater. In this way, pressure surges can also be reduced.
- a further recess 74 is formed in front of the inlet 8, which extends from an upper edge of the interruption region 32 in the direction of the inlet 8.
- the recess 74 is designed in such a way that its depth increases steadily in the direction of the inlet 8 and radially outwards, specifically to a depth which corresponds to the depth of the conveying channel 14.
- the width of the recess 74 in a first area corresponds approximately to the width of the conveying channel 14 or the radial extent of the conveying blades 24, with the radial boundary edge 78 of the recess 74 angled radially inward in the direction of rotation of the impeller 6 in an area shortly before the inlet 8 so that the width decreases slightly.
- the recess 74 extends over a length which corresponds approximately to 2.5 times the distance between two successive conveyor blades 24 of the impeller 6.
- the inlet 8 has a diameter which is greater than the width of the delivery channel 14, an inner edge of the inlet 8 being arranged on the same radius as an inner edge of the delivery channel 14, so that the cover part 10 is at the inlet 8 has a larger scope than in the other areas.
- a leading edge 76 which forms the line of intersection of the interruption area 32 with the recess 74, is curved so that the conveyor blades 24 of the impeller 6 sweep over the recess 74 first in the radially outer area and then in the radially inner area.
- the inlet On the side facing the recess 74, the inlet is delimited by a straight wall 80, which is arranged in relation to the conveyor blades 26 in such a way 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 conveyor blade 24 initially sweeps over the inlet 8.
- the actual interruption area i.e. the distance between the rear end of the recess 72 as seen in the direction of rotation and the front end of the front edge 76 of the recess 74 is approximately 1.5 times the distance between two conveyor blades 24 of the impeller 6.
- pressure syringes which lead to undesired noises, can be reduced by such a design, but without resulting in too high a delivery pressure loss when the valve is open. Instead, with the valve closed, very good results can be achieved both in terms of emissions and achievable pressures.
- the side channel blower described is thus distinguished by a significant reduction in noise emissions compared to known side channel blowers. At the same time, a high delivery rate is achieved.
- various modifications of the side channel blower described in the exemplary embodiment are possible without departing from the scope of protection of the main claim.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
- Exhaust Gas After Treatment (AREA)
Claims (8)
- Ventilateur à canal latéral, en particulier ventilateur d'air secondaire pour moteur à combustion interne, comprenant
un carter (2) dans lequel est formée une sortie sensiblement tangentielle (22),
un couvercle de carter (10) dans lequel est formée une entrée axiale (8),
deux canaux de refoulement (12, 14) par lesquels l'entrée (8) est reliée fluidiquement à la sortie (22),
une roue (6) pouvant être entrainée par une unité d'entrainement (4) est montée de manière rotative dans le carter (2) et présente des aubes (24) qui coopèrent avec les canaux de refoulement (12, 14),
et une zone d'interruption (30, 32, 34) entre la sortie (22) et l'entrée (8), dans laquelle zone les canaux de refoulement (12, 14) sont interrompus dans la direction circonférentielle,
dans lequel un premier évidement (68) est formé dans le sens de rotation de la roue (6) derrière la sortie (22) sur la paroi de délimitation radiale (36) de la région d'interruption (34) qui interrompe une zone de liaison (37) radialement extérieure entre les deux canaux de refoulement (12, 14),
caractérisé en ce que
devant l'entrée (8) et derrière la sortie (22), d'autres évidements (72, 74) respectifs sont formés dans la zone d'interruption (32, 34), la plus petite distance entre eux correspondant à 0,5 à 3 fois la distance entre deux aubes (24). - Ventilateur à canal latéral, en particulier ventilateur d'air secondaire pour moteur à combustion interne selon la revendication 1, caractérisé en ce que la plus petite distance entre les évidements (72, 74) devant l'entrée (8) et derrière la sortie (22) correspond à 1,5 fois la distance entre deux aubes (26).
- Ventilateur à canal latéral, en particulier ventilateur de ventilateur secondaire pour un moteur à combustion interne selon l'une des revendications 1 ou 2, caractérisé en ce qu'un deuxième évidement (72), dont la profondeur est inférieure à celle du premier évidement (68), joint le premier évidement (68) dans la paroi de délimitation radiale (36) de la zone d'interruption (34) dans le sens de rotation.
- Ventilateur à canal latéral, en particulier ventilateur d'air secondaire pour moteur à combustion interne selon l'une quelconque des revendications précédentes, caractérisé en ce que le deuxième évidement (72) s'étend sur la hauteur du canal de refoulement (14) partiellement formé dans le couvercle de carter (10) dans la paroi de délimitation radiale (36) de la zone d'interruption (34), la hauteur du deuxième évidement (72) diminuant continûment en direction de l'entrée (8).
- Ventilateur à canal latéral, en particulier ventilateur d'air secondaire pour moteur à combustion interne selon l'une quelconque des revendications précédentes, caractérisé en ce que l'évidement (74), qui est formé au niveau de la zone d'interruption (32) devant l'entrée (8), est relié fluidiquement à l'entrée (8), dans le sens de rotation de la roue (6), la profondeur de l'évidement (74) croissant continûment du bord supérieur de la zone d'interruption (32) faisant face à la roue (6) vers l'entrée (8).
- Ventilateur à canal latéral, en particulier soufflante d'air secondaire pour moteur à combustion interne selon la revendication 5, caractérisé en ce que la largeur de l'évidement (74) devant l'entrée (8) correspond essentiellement à l'étendue radiale des aubes (26).
- Ventilateur à canal latéral, en particulier ventilateur d'air secondaire pour moteur à combustion interne selon l'une des revendications 5 ou 6, caractérisée en ce que la profondeur de l'évidement (74) augmente continûment vers l'extérieur radial jusqu'à un bord de délimitation de l'évidement (74).
- Ventilateur à canal latéral, en particulier ventilateur d'air secondaire pour moteur à combustion interne selon la revendication 7, caractérisé en ce que, devant l'entrée (8), le bord de délimitation (78) de l'évidement (74) présent une première zone dans laquelle la largeur de l'évidement (74) correspond essentiellement à l'étendue radiale des aubes (26) et présent une deuxième zone adjacente inclinée radialement vers l'intérieur par rapport à la première zone dans le sens de rotation de la roue (6).
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 EP2627907A1 (fr) | 2013-08-21 |
EP2627907B1 true 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 |
NL2015220B1 (nl) * | 2015-07-24 | 2017-02-08 | Intergas Heating Assets Bv | Centrifugaalwaaier, en daarvan voorziene verwarmingsinrichting. |
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 |
EP3728860B1 (fr) * | 2017-12-21 | 2021-10-13 | 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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EP1940495B1 (fr) * | 2005-10-28 | 2015-08-26 | ResMed Motor Technologies Inc. | Moteur de ventilateur comprenant une gaine de support flexible |
NL2000657C2 (nl) | 2007-05-22 | 2008-11-25 | Voskamp Vollebregt Holding B V | Plantpot, alsmede combinatie met staander en werkwijze. |
DE102008056105B4 (de) * | 2008-11-06 | 2011-02-03 | Pierburg Gmbh | Seitenkanalgebläse, insbesondere Sekundärluftgebläse für eine Verbrennungskraftmaschine |
DE102009006652B4 (de) * | 2009-01-29 | 2014-06-18 | Pierburg Gmbh | Seitenkanalgebläse, insbesondere Sekundärluftgebläse für eine Verbrennungskraftmaschine |
-
2010
- 2010-09-29 DE DE102010046870.3A patent/DE102010046870B4/de not_active Expired - Fee Related
-
2011
- 2011-08-31 CN CN201180046740.3A patent/CN103154523B/zh active Active
- 2011-08-31 JP JP2013530658A patent/JP5602950B2/ja active Active
- 2011-08-31 EP EP11749435.1A patent/EP2627907B1/fr active Active
- 2011-08-31 US US13/825,554 patent/US9297276B2/en active Active
- 2011-08-31 WO PCT/EP2011/065053 patent/WO2012041625A1/fr active Application Filing
Non-Patent Citations (1)
Title |
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None * |
Also Published As
Publication number | Publication date |
---|---|
JP2013538977A (ja) | 2013-10-17 |
US20130209247A1 (en) | 2013-08-15 |
JP5602950B2 (ja) | 2014-10-08 |
US9297276B2 (en) | 2016-03-29 |
WO2012041625A1 (fr) | 2012-04-05 |
CN103154523A (zh) | 2013-06-12 |
DE102010046870B4 (de) | 2016-09-22 |
DE102010046870A1 (de) | 2012-03-29 |
CN103154523B (zh) | 2015-10-14 |
EP2627907A1 (fr) | 2013-08-21 |
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