EP2342464B1 - Side channel blower, in particular secondary air blower for an internal combustion engine - Google Patents

Side channel blower, in particular secondary air blower for an internal combustion engine Download PDF

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Publication number
EP2342464B1
EP2342464B1 EP09736401.2A EP09736401A EP2342464B1 EP 2342464 B1 EP2342464 B1 EP 2342464B1 EP 09736401 A EP09736401 A EP 09736401A EP 2342464 B1 EP2342464 B1 EP 2342464B1
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EP
European Patent Office
Prior art keywords
conveying
cross
outlet
blower
housing part
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EP09736401.2A
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German (de)
French (fr)
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EP2342464A1 (en
Inventor
Berthold Herrmann
Andreas Bumbel
Jakob Gehlen
Rainer Peters
Thomas Rösgen
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Pierburg GmbH
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Pierburg GmbH
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    • 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
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/403—Casings; Connections of working fluid especially adapted for elastic fluid pumps

Definitions

  • the invention relates to side channel blower, in particular secondary air blower for an internal combustion engine with a housing in which an inlet and an outlet is formed, a housing part in which a substantially annular extending delivery channel is arranged, an impeller which is rotatably mounted in the housing and conveyor blades which cooperate with the opposite conveying channel, an interrupting portion between the inlet and the outlet in which the conveying channel is interrupted in the circumferential direction and a Queritessverminderer, which reduces the conveying channel depth over a predetermined portion.
  • the object of the invention is therefore to design a side channel blower so that with the same size, an increased delivery volume can be achieved and at the same time an increased noise level can be avoided by pulsations and tearing flows.
  • the radial extent of the cross-sectional reducer increases steadily from the inlet to the outlet and the conveying channel has in cross-section two paragraphs to adjoining wall surfaces of the conveying channel. It has been found that in such a design of the cross-section reducer, the delivery volume can be increased at about the same achievable static pressure and at the same time noise emissions can be reduced by preventing turbulence when entering the air from the feed channel in the impeller.
  • the cross-sectional reducer reduces the conveying channel depth by a constant difference in the circumferential direction and in the radial direction.
  • Such an embodiment of the Queritessverminderers is relatively easy to produce in automated systems. Already with a small difference of 0.1 mm to 2 mm in the delivery channel depth a significant improvement in terms of noise emissions and achievable delivery volume is available.
  • the Querterrorismsverminderer is made in one piece with the housing part, so that additional components omitted.
  • the housing consists at least of a first housing part and a second housing part, in each of which a delivery channel is formed, wherein in both conveyor channels a Querterrorismsverminderer is arranged.
  • the radial extent of the cross-sectional reducer in the first delivery channel in the first housing part, in which the inlet is arranged grows toward the outlet from radially inward to radially outward and in the second Delivery channel in the second housing part, in which the outlet is arranged, grows toward the outlet from radially outside to radially inside, wherein the impeller blades of the impeller cooperate with two conveying channels. It has been found that this pressure fluctuations are reduced in particular in the pressure range and a better acoustics is achieved.
  • a side channel blower in which a larger volume of air can be delivered while maintaining the maximum pressure and at the same time the noise level is reduced.
  • FIG. 1 shown side channel blower 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 outlet of the air 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.
  • the axial inlet 6 is as far as possible from the tangential outlet 20 in the direction of rotation of the impeller 4.
  • interruption regions 28 on the cover part 10 and the housing part 16 are arranged, in which the delivery channels 12, 14 are interrupted, so that in the interruption region 28 axially opposite to the conveying blades 22 of Impeller 4 the smallest possible gap is available.
  • the delivery channel 12 arranged in the cover part 10 has a substantially constant width b and extends over the circumference of the cover part 10, with the exception of the interruption region 28.
  • the impeller 4 rotates clockwise from the inlet region 8 to the end of the delivery channel 12 and then over the interruption region 28, from where a single pocket 26 is again passed over the inlet region 8 and draws in air.
  • 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 web 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 toward the interior of the impeller. 4 he follows.
  • the cover part 10 has a cylindrical recess 50 into which the drive shaft 19 of the drive unit 3 projects.
  • a Querterrorismsverminderer 52 is arranged, which in the FIG. 2 hatched. This extends over the entire length of the conveying channel 12, starting shortly after the inlet region 8 and ending axially opposite to the second housing part 16 formed outlet 20.
  • the width of the Queritessverminderers 52 thereby increases from the inlet portion 8 to the outlet 20. This means that the Extending outside circumference spirally from the inlet portion 8 to the outlet 20 while the inner circumference of the Queritessverminderers 52 remains constant.
  • the cross-sectional shape of the cross-sectional reducer 52 is shown in FIGS FIG. 3 to recognize.
  • the surface area of the cross-section reducer 52 has a minimum constant height of about 0.1 mm to 2 mm.
  • the wall surface 54 of the conveying channel 12 which is usually continuous in cross-section, has two shoulders 56 each at the transition between conveying channel 12 without cross-sectional reducer 52 and conveying channel 12 with cross-sectional reducer 52.
  • the paragraphs 56 reduce the pressure pulsations occurring and thus lead to lower noise emissions.
  • FIGS. 4 and 5 is the second housing part 16 of the side channel blower according to the invention shown, wherein also a Querterrorismsverminderer 58 is formed and by hatching in figure 4 indicated.
  • This cross-sectional reducer 58 has in cross-section substantially the same shape as the Querterrorismsverminderer 52 in the cover part 10.
  • FIG. 5 clearly that the channel depth in the region of the cross-section reducer 58 is reduced by 0.1 mm to 2 mm in comparison to the other channel depth in cross section.
  • paragraphs 60 are formed in the region of the transition between a subsequent wall surface 61 of the delivery channel 14 and the surface of the cross-sectional reducer 58.
  • the Querterrorismsverminderer 58 extends over the entire length of the conveying channel 14 in the second housing part 16, starting shortly behind the opposite to the lid portion 10 formed on the inlet portion 8 and ending at the outlet 20.
  • the width of the Querterrorismsverminderers 58 grows here from the inlet portion 8 to the outlet 20th
  • the outer circumference remains constant over the run length, while the inner circumference becomes less helical toward the outlet 20.
  • the mode of operation corresponds to the mode of operation of the cross-sectional reducer 52 in the cover part 10.
  • the cross-sectional reducers 52, 58 provide for a steadily reducing from the inlet portion 8 to the outlet 20 available standing flow cross-section.
  • the maximum delivery volume is increased, while the paragraphs 56, 60 in the two delivery channels 12, 14, the speed and uniformity of the vortex flow is reduced, whereby pulsations in the transition from the delivery channels 12, 14 are avoided in the pockets 26, so that the Noise level of the side channel blower is reduced.

Description

Die Erfindung betrifft Seitenkanalgebläse, insbesondere Sekundärluftgebläse für eine Verbrennungskraftmaschine mit einem Gehäuse, in dem ein Einlass und ein Auslass ausgebildet ist, einem Gehäuseteil, in dem ein sich im Wesentlichen ringförmig erstreckender Förderkanal angeordnet ist, einem Laufrad, welches drehbar im Gehäuse gelagert ist und Förderschaufeln aufweist, die mit dem gegenüberliegenden Förderkanal zusammenwirken, einem Unterbrechungsbereich zwischen dem Einlass und dem Auslass, in dem der Förderkanal in Umfangsrichtung unterbrochen ist und einem Querschnittsverminderer, der die Förderkanaltiefe über einen vorbestimmten Abschnitt verringert.The invention relates to side channel blower, in particular secondary air blower for an internal combustion engine with a housing in which an inlet and an outlet is formed, a housing part in which a substantially annular extending delivery channel is arranged, an impeller which is rotatably mounted in the housing and conveyor blades which cooperate with the opposite conveying channel, an interrupting portion between the inlet and the outlet in which the conveying channel is interrupted in the circumferential direction and a Querschnittsverminderer, which reduces the conveying channel depth over a predetermined portion.

Seitenkanalgebläse oder -pumpen sind allgemein bekannt und werden in einer Vielzahl von Anmeldungen beschrieben. Im Kraftfahrzeug dienen sie beispielsweise zur Förderung von Kraftstoff oder zum Einblasen von Sekundärluft in das Abgassystem. Der Antrieb erfolgt üblicherweise über einen Elektromotor, der das Laufrad antreibt. Das Laufrad ist an seinem Umfang im Wesentlichen derart ausgebildet, dass es mit dem ihm axial gegenüberliegenden Förderkanal einen umlaufenden Wirbelkanal bildet. Aus dem den Wirbelkanal bildenden Teil des Laufrads ragen Förderschaufeln senkrecht in Richtung zum gegenüberliegenden, im Gehäuse ausgebildeten Teil des Förderkanals, so dass zwischen den Förderschaufeln Taschen gebildet werden. Das geförderte Fluid in den Taschen erfährt bei Drehung des Laufrades durch die Förderschaufeln eine Beschleunigung in Umfangsrichtung sowie in radialer Richtung, so dass im Förderkanal eine umlaufende Wirbelströmung entsteht.Side channel blowers or pumps are well known and described in a variety of applications. In the motor vehicle, for example, they serve to convey fuel or to inject secondary air into the exhaust system. The drive is usually via an electric motor that drives the impeller. The impeller is formed at its periphery substantially such that it forms a circumferential vortex channel with the axially opposite conveying channel. From the vortex channel forming part of the impeller projecting blades projecting vertically toward the opposite, formed in the housing part of the conveyor channel, so that pockets are formed between the conveyor blades. The pumped fluid in the pockets undergoes an acceleration in the circumferential direction and in the radial direction during rotation of the impeller by the conveyor blades, so that in the conveyor channel, a circumferential vortex flow is formed.

Es sind Seitenkanalgebläse bekannt, bei denen lediglich ein Förderkanal an einer axialen Seite des Laufrades in einem Gehäuseteil ausgebildet ist, als auch Seitenkanalgebläse bei denen an beiden axialen Seiten des Laufrades ein Förderkanal ausgebildet ist, wobei dann beide Förderkanäle fluidisch miteinander verbunden sind. Bei einem derartigen Seitenkanalgebläse ist einer der Förderkanäle in einem als Deckel dienenden Gehäuseteil ausgebildet, während der andere Förderkanal in dem Gehäuseteil ausgebildet ist, an dem die Antriebseinheit befestigt ist, auf deren Antriebswelle das Laufrad befestigt ist.Side channel blowers 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 blower in which a delivery channel is formed on both axial sides of the impeller, then both conveyor channels are fluidly connected to each other. In such a side channel blower one of the conveying channels is formed in a housing part serving as a lid, while the other conveying channel is formed in the housing part, on which the drive unit is mounted, on the drive shaft of the impeller is attached.

Nachteilhaft bei diesen bekannten Seitenkanalgebläsen sind die auftretenden Pulsationen, durch die unerwünscht hohe Körperschallemissionen auftreten.Disadvantages of these known side channel blowers are the pulsations which occur due to which undesirably high structure-borne sound emissions occur.

Um diese hohen Geräuschemissionen zu vermeiden, wird in der DE 42 20 153 A1 ein Seitenkanalgebläse vorgeschlagen, bei dem sich ein Querschnittsverminderer von der Mitte des Förderkanals zwischen Einlass und Auslass bis kurz vor die Auslassöffnung erstreckt. Durch diesen Querschnittsverminderer soll die Geschwindigkeitsdifferenz zwischen dem aus dem Förderkanal in das Laufrad einströmenden Fluid und der Förderschaufelgeschwindigkeit reduziert werden, wodurch der Geräuschpegel herabgesetzt wird. Zusätzlich soll hierdurch der erreichbare statische Druck erhöht werden. Der Querschnitt des Querschnittverminderers ist dabei im Vergleich zum Querschnitt der Nut relativ groß, wodurch der zu fördernde Volumenstrom beschränkt wird, auch wenn ein erhöhter statischer Druck erreicht wird.In order to avoid these high noise emissions, is in the DE 42 20 153 A1 a side channel blower proposed in which a Querschnittsverminderer from the center of the delivery channel between the inlet and outlet extends to just before the outlet opening. By this Querschnittsverminderer the speed difference between the inflowing from the feed channel in the impeller fluid and the speed of the conveyor blade is to be reduced, whereby the noise level is lowered. In addition, this should increase the achievable static pressure. The cross-section of the cross-section reducer is relatively large compared to the cross section of the groove, whereby the volume flow to be delivered is limited, even if an increased static pressure is reached.

Aufgabe der Erfindung ist es daher, ein Seitenkanalgebläse so zu gestalten, dass bei gleicher Baugröße ein erhöhtes Fördervolumen erreicht werden kann und gleichzeitig ein erhöhter Geräuschpegel durch Pulsationen und abreißende Strömungen vermieden werden kann.The object of the invention is therefore to design a side channel blower so that with the same size, an increased delivery volume can be achieved and at the same time an increased noise level can be avoided by pulsations and tearing flows.

Diese Aufgabe wird dadurch gelöst, dass die radiale Ausdehnung des Querschnittsverminderers vom Eintritt zum Austritt hin stetig wächst und der Förderkanal im Querschnitt zwei Absätze zu sich anschließenden Wandflächen des Förderkanals aufweist. Es hat sich gezeigt, dass bei einer derartigen Ausführung des Querschnittsverminderers das Fördervolumen bei etwa gleichem erreichbaren statischen Druck erhöht werden kann und gleichzeitig Geräuschemissionen durch die Verhinderung von Turbulenzen beim Eintritt der Luft aus dem Förderkanal in das Laufrad verringert werden können.This object is achieved in that the radial extent of the cross-sectional reducer increases steadily from the inlet to the outlet and the conveying channel has in cross-section two paragraphs to adjoining wall surfaces of the conveying channel. It has been found that in such a design of the cross-section reducer, the delivery volume can be increased at about the same achievable static pressure and at the same time noise emissions can be reduced by preventing turbulence when entering the air from the feed channel in the impeller.

Vorzugsweise verringert der Querschnittsverminderer in Umfangsrichtung und in radialer Richtung die Förderkanaltiefe um eine konstante Differenz. Eine derartige Ausführung des Querschnittsverminderers ist in automatisierten Anlagen relativ einfach herstellbar. Bereits bei einer geringen Differenz von 0,1 mm bis 2 mm in der Förderkanaltiefe ist eine deutliche Verbesserung bezüglich der Geräuschemissionen und des erreichbaren Fördervolumen vorhanden.Preferably, the cross-sectional reducer reduces the conveying channel depth by a constant difference in the circumferential direction and in the radial direction. Such an embodiment of the Querschnittsverminderers is relatively easy to produce in automated systems. Already with a small difference of 0.1 mm to 2 mm in the delivery channel depth a significant improvement in terms of noise emissions and achievable delivery volume is available.

Bevorzugt ist der Querschnittsverminderer einstückig mit dem Gehäuseteil hergestellt, so dass zusätzliche Bauteile entfallen.Preferably, the Querschnittsverminderer is made in one piece with the housing part, so that additional components omitted.

In einer besonderen Ausführungsform besteht das Gehäuse zumindest aus einem ersten Gehäuseteil und einem zweiten Gehäuseteil, in denen jeweils ein Förderkanal ausgebildet ist, wobei in beiden Förderkanälen ein Querschnittsverminderer angeordnet ist. Hierdurch können die Vorteile durch den Querschnittsverminderer auch in Seitenkanalgebläsen mit sich gegenüberliegenden Förderkanälen vollständig genutzt werden.In a particular embodiment, the housing consists at least of a first housing part and a second housing part, in each of which a delivery channel is formed, wherein in both conveyor channels a Querschnittsverminderer is arranged. As a result, the advantages can be fully utilized by the Querschnittsverminderer in side channel blowers with opposite conveyor channels.

Es hat sich als besonders vorteilhaft herausgestellt, wenn die radiale Ausdehnung des Querschnittsverminderers im ersten Förderkanal im ersten Gehäuseteil, in dem der Einlass angeordnet ist, in Richtung zum Auslass von radial innen nach radial außen wächst und im zweiten Förderkanal im zweiten Gehäuseteil, in dem der Auslass angeordnet ist, in Richtung zum Auslass von radial außen nach radial innen wächst, wobei die Förderschaufeln des Laufrades mit beiden Förderkanälen zusammenwirken. Es hat sich herausgestellt, dass hierdurch insbesondere im Druckbereich vorhandene Druckschwankungen reduziert werden und eine bessere Akustik erreicht wird.It has proven to be particularly advantageous if the radial extent of the cross-sectional reducer in the first delivery channel in the first housing part, in which the inlet is arranged, grows toward the outlet from radially inward to radially outward and in the second Delivery channel in the second housing part, in which the outlet is arranged, grows toward the outlet from radially outside to radially inside, wherein the impeller blades of the impeller cooperate with two conveying channels. It has been found that this pressure fluctuations are reduced in particular in the pressure range and a better acoustics is achieved.

Es wird somit ein Seitenkanalgebläse geschaffen, bei dem bei gleich bleibendem Maximaldruck ein größeres Luftvolumen gefördert werden kann und gleichzeitig der Geräuschpegel reduziert wird.Thus, a side channel blower is provided in which a larger volume of air can be delivered while maintaining the maximum pressure and at the same time the noise level is reduced.

Ein Ausführungsbeispiel eines erfindungsgemäßen Seitenkanalgebläses ist in den Zeichnungen dargestellt und wird nachfolgend beschrieben.

  • Figur 1 zeigt eine Seitenansicht eines Seitenkanalgebläses in geschnittener Darstellung.
  • Figur 2 zeigt eine Draufsicht auf ein Deckelteil eines erfindungsgemäßen Seitenkanalgebläses aus Richtung des Laufrades.
  • Figur 3 zeigt eine Schnittansicht entlang der Linie A-A des in der Figur 2 dargestellten Deckelteils.
  • Figur 4 zeigt eine Draufsicht ein zweites Gehäuseteil eines erfindungsgemäßen Seitenkanalgebläses aus Richtung des Laufrades.
  • Figur 5 zeigt eine Schnittansicht entlang der Linie A-A des in der Figur 4 dargestellten zweiten Gehäuseteils.
An embodiment of a side channel blower according to the invention is shown in the drawings and will be described below.
  • FIG. 1 shows a side view of a side channel blower in a sectional view.
  • FIG. 2 shows a plan view of a cover part of a side channel blower according to the invention from the direction of the impeller.
  • FIG. 3 shows a sectional view taken along the line AA of the in the FIG. 2 shown cover part.
  • FIG. 4 shows a plan view of a second housing part of a side channel blower according to the invention from the direction of the impeller.
  • FIG. 5 shows a sectional view taken along the line AA of the in the FIG. 4 shown second housing part.

Das in Figur 1 dargestellte Seitenkanalgebläse besteht aus einem zweiteiligen Gehäuse 2 sowie einem im Gehäuse 2 drehbar gelagerten und über eine Antriebseinheit 3 angetriebenen Laufrad 4, beispielsweise zur Förderung von Luft. Die Luft gelangt über einen axialen Einlass 6 in einen Einlassbereich 8 eines ersten Gehäuseteils 10, welches in vorliegender Ausführung als Deckelteil des Seitenkanalgebläses dient. Vom Einlassbereich 8 aus strömt die Luft anschließend in zwei sich im Wesentlichen ringförmig erstreckende Förderkanäle 12, 14, von denen der erste Förderkanal 12 im Deckelteil 10 ausgebildet ist und der zweite Förderkanal 14 in einem zweiten Gehäuseteil 16 ausgebildet ist, in dem auch eine Lagerung 18 einer Antriebswelle 19 der Antriebseinheit 3 angeordnet ist, auf der das Laufrad 4 befestigt ist. Der Austritt der Luft erfolgt über einen tangentialen Auslass 20, der am zweiten Gehäuseteil 16 angeordnet ist.This in FIG. 1 shown side channel blower 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 outlet of the air via a tangential outlet 20, which is arranged on the second housing part 16.

Das Laufrad 4 ist zwischen dem Deckelteil 10 und dem zweiten Gehäuseteil 16 angeordnet und weist an seinem Umfang Förderschaufeln 22 auf, die gekrümmt sind und sich radial erstrecken, wobei die Förderschaufeln 22 durch einen sich radial erstreckenden Umfangsring 24 in eine erste Reihe axial gegenüberliegend zum ersten Förderkanal 12 und eine zweite Reihe axial gegenüberliegend zum zweiten Förderkanal 14 geteilt werden, so dass zwei Wirbelkanäle ausgebildet werden, die jeweils durch einen der Förderkanäle 12, 14 mit dem zugewandten Teil des Laufrades 4 gebildet werden. Der Außendurchmesser der Förderkanäle 12, 14 ist etwas größer als der Außendurchmesser des Laufrades 4, so dass eine fluidische Verbindung zwischen den beiden Förderkanälen 12, 14 außerhalb des Außenumfangs des Laufrads 4 besteht. Zwischen den sich vom Umfangsring 24 erstreckenden Förderschaufeln 22 werden somit nach radial außen offene Taschen 26 gebildet, in denen die Luft gefördert beziehungsweise beschleunigt wird.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.

Um eine möglichst gute Förderleistung und Druckerhöhung zu erlangen, ist der axiale Einlass 6 in Drehrichtung des Laufrades 4 möglichst weit vom tangentialen Auslass 20 entfernt. Um zuverlässig eine Kurzschlussströmung entgegen der Drehrichtung des Laufrades 4 vom Einlass 6 zum Auslass 20 zu unterbinden, sind zwischen dem Einlass 6 und dem Auslass 20 Unterbrechungsbereiche 28 am Deckelteil 10 und am Gehäuseteil 16 angeordnet, in welchen die Förderkanäle 12, 14 unterbrochen sind, so dass im Unterbrechungsbereich 28 axial gegenüberliegend zu den Förderschaufeln 22 des Laufrades 4 ein möglichst geringer Spalt vorhanden ist.In order to obtain the best possible delivery rate and pressure increase, the axial inlet 6 is as far as possible from the tangential outlet 20 in the direction of rotation of the impeller 4. To reliably a short-circuit flow against the direction of rotation of the impeller 4 from Inlet 6 to prevent the outlet 20, between the inlet 6 and the outlet 20 interruption regions 28 on the cover part 10 and the housing part 16 are arranged, in which the delivery channels 12, 14 are interrupted, so that in the interruption region 28 axially opposite to the conveying blades 22 of Impeller 4 the smallest possible gap is available.

In den Figuren 2 und 3 ist zu erkennen, dass der im Deckelteil 10 angeordnete Förderkanal 12 eine im Wesentlichen konstante Breite b aufweist und sich mit Ausnahme des Unterbrechungsbereiches 28 über den Umfang des Deckelteils 10 erstreckt. Bei der hier gewählten Ansicht dreht sich somit das Laufrad 4 im Uhrzeigersinn vom Einlassbereich 8 bis zum Ende des Förderkanals 12 und anschließend über den Unterbrechungsbereich 28, von wo aus eine einzelne Tasche 26 erneut über den Einlassbereich 8 geführt wird und Luft ansaugt.In the FIGS. 2 and 3 It can be seen that the delivery channel 12 arranged in the cover part 10 has a substantially constant width b and extends over the circumference of the cover part 10, with the exception of the interruption region 28. Thus, in the view selected here, the impeller 4 rotates clockwise from the inlet region 8 to the end of the delivery channel 12 and then over the interruption region 28, from where a single pocket 26 is again passed over the inlet region 8 and draws in air.

Das Deckelteil 10 wird über Schrauben am zweiten Gehäuseteil 16 befestigt, welche durch entsprechende Bohrungen 30 gesteckt werden, die an sich nach radial außen erstreckenden Vorsprüngen 32 am Deckelteil 10 ausgebildet sind. An zweien dieser Vorsprünge 32 befinden sich zusätzlich kleine, sich axial erstreckende Bolzen 34, welche zur Vorfixierung des Deckelteils 10 auf dem zweiten Gehäuseteil 16 dienen.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.

Radial hinter einer Außenwand 36 des Förderkanals 12 ist eine Nut 38 ausgebildet, in die zur Abdichtung zwischen Deckelteil 10 und zweitem Gehäuseteil 16 ein Dichtring 40 eingelegt wird, der über Nasen 42 in der Nut 38 gehalten wird.Radially behind an outer wall 36 of the conveying channel 12, 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.

Radial vor einer Innenwand 44 des Förderkanals 12 ist ein ringförmiger Steg 46 ausgebildet, der nach dem Zusammenbau des Gebläses in eine korrespondierende Nut 48 des Laufrades 4 greift, wodurch eine Abdichtung vom Förderkanal 12 in Richtung zum Inneren des Laufrades 4 erfolgt. Zusätzlich weist das Deckelteil 10 eine zylindrische Vertiefung 50 auf, in die die Antriebswelle 19 der Antriebseinheit 3 ragt. Im Förderkanal 12 des Deckelteils 10 ist ein Querschnittsverminderer 52 angeordnet, der in der Figur 2 schraffiert dargestellt ist. Dieser erstreckt sich über die gesamte Länge des Förderkanals 12, beginnend kurz hinter dem Einlassbereich 8 und endend axial gegenüberliegend zum am zweiten Gehäuseteil 16 ausgebildeten Auslass 20. Erfindungsgemäß wächst die Breite des Querschnittsverminderers 52 dabei vom Einlassbereich 8 zum Auslass 20. Dies bedeutet, dass der Außenumfang spiralförmig vom Einlassbereich 8 zum Auslass 20 hin wächst, während der Innenumfang des Querschnittsverminderers 52 konstant bleibt.Radially in front of an inner wall 44 of the conveying channel 12, an annular web 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 toward the interior of the impeller. 4 he follows. In addition, the cover part 10 has a cylindrical recess 50 into which the drive shaft 19 of the drive unit 3 projects. In the conveying channel 12 of the cover part 10, a Querschnittsverminderer 52 is arranged, which in the FIG. 2 hatched. This extends over the entire length of the conveying channel 12, starting shortly after the inlet region 8 and ending axially opposite to the second housing part 16 formed outlet 20. According to the invention, the width of the Querschnittsverminderers 52 thereby increases from the inlet portion 8 to the outlet 20. This means that the Extending outside circumference spirally from the inlet portion 8 to the outlet 20 while the inner circumference of the Querschnittsverminderers 52 remains constant.

Die Querschnittsform des Querschnittsverminderers 52 ist in der Figur 3 zu erkennen. In Bezug auf eine sich anschließende Wandfläche 54 des Förderkanals 12 weist die Oberfläche des Querschnittsverminderers 52 eine minimale konstante Höhe von etwa 0,1 mm bis 2 mm auf. Dies bedeutet, dass die üblicherweise im Querschnitt stetig geformte Wandfläche 54 des Förderkanals 12 zwei Absätze 56 jeweils am Übergang zwischen Förderkanal 12 ohne Querschnittsverminderer 52 und Förderkanal 12 mit Querschnittsverminderer 52 aufweist. Über die gesamte Lauflänge des Förderkanals 12 betrachtet, ergibt sich somit eine stetige Verminderung des zur Verfügung stehenden Querschnitts des Förderkanals 12. Insbesondere diese Verminderung führt zu einer Erhöhung des maximalen Fördervolumens. Die Absätze 56 hingegen vermindern die auftretenden Druckpulsationen und führen somit zu geringeren Geräuschemissionen.The cross-sectional shape of the cross-sectional reducer 52 is shown in FIGS FIG. 3 to recognize. With respect to a subsequent wall surface 54 of the delivery channel 12, the surface area of the cross-section reducer 52 has a minimum constant height of about 0.1 mm to 2 mm. This means that the wall surface 54 of the conveying channel 12, which is usually continuous in cross-section, has two shoulders 56 each at the transition between conveying channel 12 without cross-sectional reducer 52 and conveying channel 12 with cross-sectional reducer 52. Considered over the entire run length of the conveyor channel 12, this results in a steady reduction of the available cross section of the conveyor channel 12. In particular, this reduction leads to an increase of the maximum delivery volume. The paragraphs 56, however, reduce the pressure pulsations occurring and thus lead to lower noise emissions.

In den Figuren 4 und 5 ist das zweite Gehäuseteil 16 des erfindungsgemäßen Seitenkanalgebläses dargestellt, wobei auch hier ein Querschnittsverminderer 58 ausgebildet und durch Schraffierung in Figur 4 kenntlich gemacht ist. Dieser Querschnittsverminderer 58 weist im Querschnitt im Wesentlichen die gleiche Form auf wie der Querschnittsverminderer 52 im Deckelteil 10. So wird insbesondere aus Figur 5 deutlich, dass die Kanaltiefe im Bereich des Querschnittsverminderers 58 um 0,1 mm bis 2 mm im Vergleich zur sonstigen Kanaltiefe im Querschnitt reduziert ist. Auch hier entstehen entsprechend Absätze 60 im Bereich des Übergangs zwischen einer sich anschließenden Wandfläche 61 des Förderkanals 14 und der Oberfläche des Querschnittsverminderers 58.In the FIGS. 4 and 5 is the second housing part 16 of the side channel blower according to the invention shown, wherein also a Querschnittsverminderer 58 is formed and by hatching in figure 4 indicated. This cross-sectional reducer 58 has in cross-section substantially the same shape as the Querschnittsverminderer 52 in the cover part 10. Thus, in particular FIG. 5 clearly that the channel depth in the region of the cross-section reducer 58 is reduced by 0.1 mm to 2 mm in comparison to the other channel depth in cross section. In this case as well, paragraphs 60 are formed in the region of the transition between a subsequent wall surface 61 of the delivery channel 14 and the surface of the cross-sectional reducer 58.

Auch der Querschnittsverminderer 58 erstreckt sich über die gesamte Länge des Förderkanals 14 im zweiten Gehäuseteil 16, beginnend kurz hinter dem gegenüberliegend zum am Deckelteil 10 ausgebildeten Einlassbereich 8 und endend am Auslass 20. Die Breite des Querschnittsverminderers 58 wächst auch hier vom Einlassbereich 8 zum Auslass 20, jedoch bleibt beim Querschnittsverminderer 58 der Außenumfang über die Lauflänge konstant, während der Innenumfang spiralförmig zum Auslass 20 geringer wird. Die Funktionsweise entspricht dabei der Funktionsweise des Querschnittsverminderers 52 im Deckelteil 10.Also, the Querschnittsverminderer 58 extends over the entire length of the conveying channel 14 in the second housing part 16, starting shortly behind the opposite to the lid portion 10 formed on the inlet portion 8 and ending at the outlet 20. The width of the Querschnittsverminderers 58 grows here from the inlet portion 8 to the outlet 20th However, in the cross-section reducer 58, the outer circumference remains constant over the run length, while the inner circumference becomes less helical toward the outlet 20. The mode of operation corresponds to the mode of operation of the cross-sectional reducer 52 in the cover part 10.

Zusätzlich weist das zweite Gehäuseteil 16 zu den Bolzen 34 und Bohrungen 30 des Deckelteils korrespondierende Bohrungen 62 mit Gewinde und Bohrungen 64 ohne Gewinde für die Bolzen 34 auf, die an sich radial erstreckenden Vorsprüngen 66 ausgebildet sind. Weitere Bohrungen 68 dienen zur Befestigung der Antriebseinheit 3 über in Figur 1 dargerstellte Schrauben 70. Zentral am Gehäuseteil 16 ist eine Durchgangsbohrung 72 zur Aufnahme der Lagerung 18 der Antriebswelle 19.In addition, the second housing part 16 to the bolts 34 and holes 30 of the cover part corresponding holes 62 threaded and non-threaded holes 64 for the bolts 34 which are formed on radially extending projections 66. Further holes 68 are used to attach the drive unit 3 via in FIG. 1 Dargelste screws 70. Central to the housing part 16 is a through hole 72 for receiving the bearing 18 of the drive shaft 19th

Gemeinsam sorgen die Querschnittsverminderer 52, 58 für einen sich vom Einlassbereich 8 zum Auslass 20 stetig reduzierenden zur Verfügung stehenden Durchströmungsquerschnitt. Hierdurch wird das maximale Fördervolumen erhöht, während durch die Absätze 56, 60 in den beiden Förderkanälen 12, 14 die Geschwindigkeit und Gleichförmigkeit der Wirbelströmung reduziert wird, wodurch Pulsationen beim Übergang von den Förderkanälen 12, 14 in die Taschen 26 vermieden werden, so dass der Geräuschpegel des Seitenkanalgebläses reduziert wird.Together, the cross-sectional reducers 52, 58 provide for a steadily reducing from the inlet portion 8 to the outlet 20 available standing flow cross-section. As a result, the maximum delivery volume is increased, while the paragraphs 56, 60 in the two delivery channels 12, 14, the speed and uniformity of the vortex flow is reduced, whereby pulsations in the transition from the delivery channels 12, 14 are avoided in the pockets 26, so that the Noise level of the side channel blower is reduced.

Es sollte deutlich sein, dass verschiedene Modifikationen des im Ausführungsbeispiel beschriebenen Seitenkanalgebläses möglich sind, ohne den Schutzbereich des Hauptanspruchs zu verlassen. So kann es sich insbesondere um eine Pumpe mit nur einem Seitenkanal handeln oder die Höhe der Querschnittsverminderer angepasst werden. Des Weiteren sind verschiedene Stellungen des Querschnittsverminderers im Förderkanal vorstellbar.It should be clear that various modifications of the side channel blower described in the embodiment are possible without departing from the scope of the main claim. This may in particular be a pump with only one side channel or the height of the cross-section reducer can be adjusted. Furthermore, different positions of the Querschnittsverminderers in the delivery channel are conceivable.

Claims (5)

  1. Side channel blower, in particular a secondary air blower for an internal combustion engine, comprising
    a housing (2) in which an inlet (6) and an outlet (20) are formed,
    a housing part (10) in which a conveying duct (12) is arranged that extends substantially in an annular shape,
    an impeller (4) rotatably supported in the housing and having conveying blades (22) cooperating with the opposite conveying duct,
    an interruption region (28) between the inlet and the outlet, in which the conveying duct is interrupted in the circumferential direction,
    and a cross-section reducer (52) reducing the depth of the conveying duct along a predetermined section,
    characterized in that
    the radial extension of the cross-section reducer (52; 58) increases constantly from the inlet (6) to the outlet (20) and, seen in cross section, the conveying duct (12; 14) has two shoulders to adjoining wall surfaces (54; 61) of the conveying duct (12; 14).
  2. Side channel blower, in particular a secondary air blower for an internal combustion engine of claim 1, characterized in that the cross-section reducer (52; 58) reduces the depth of the conveying duct (12; 14) by a constant difference in the circumferential direction and in the radial direction.
  3. Side channel blower, in particular a secondary air blower for an internal combustion engine of one of claims 1 or 2, characterized in that the cross-section reducer (52; 58) is formed integrally with the housing part (10; 16).
  4. Side channel blower, in particular a secondary air blower for an internal combustion engine of one of the preceding claims, characterized in that the housing (2) is formed at least by a first housing part (10) and a second housing part (16), in which a conveying duct (12, 14) is formed respectively, wherein a cross-section reducer (52, 58) is arranged in both conveying ducts (12, 14).
  5. Side channel blower, in particular a secondary air blower for an internal combustion engine of claim 4, characterized in that the radial extension of the cross-section reducer (52) in the first conveying duct (12) in the first housing part (10) in which the inlet (6) is provided, grows towards the outlet (20) e.g. from radially inside to radially outside, and in the second conveying duct (14) in the second housing part (16) in which the outlet (20) is provided, the radial extension grows towards the outlet (20) e.g. from radially outside to radially inside, wherein the conveying blades (22) of the impeller (4) cooperate with both conveying ducts (12, 14).
EP09736401.2A 2008-11-06 2009-10-07 Side channel blower, in particular secondary air blower for an internal combustion engine Active EP2342464B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102008056106A DE102008056106B4 (en) 2008-11-06 2008-11-06 Side channel blower, in particular secondary air blower for an internal combustion engine
PCT/EP2009/062997 WO2010052082A1 (en) 2008-11-06 2009-10-07 Side channel blower, in particular secondary air blower for an internal combustion engine

Publications (2)

Publication Number Publication Date
EP2342464A1 EP2342464A1 (en) 2011-07-13
EP2342464B1 true EP2342464B1 (en) 2018-03-28

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DE (1) DE102008056106B4 (en)
WO (1) WO2010052082A1 (en)

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Publication number Priority date Publication date Assignee Title
DE102012221916A1 (en) * 2012-11-29 2014-06-05 BSH Bosch und Siemens Hausgeräte GmbH Housing for a radial fan and radial fan
EP3728860B1 (en) * 2017-12-21 2021-10-13 Pierburg GmbH Side channel blower, in particular secondary air blower for an internal combustion engine
US11248618B1 (en) * 2019-03-13 2022-02-15 Airtech Group, Inc. O-ring for side channel blower and side channel blower including said o-ring

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Publication number Priority date Publication date Assignee Title
US2015200A (en) * 1931-01-12 1935-09-24 Spoor Willem Lodewijk Joost Rotary pump
DE876285C (en) * 1940-09-29 1953-05-11 Siemens Ag Ring compressor
IT1240003B (en) * 1990-04-24 1993-11-27 Nuovopignone-Industrie Meccaniche Efonderia IMPROVEMENTS IN A TOROIDAL CHAMBER REGENERATIVE TYPE COMPRESSOR
KR970005981B1 (en) 1991-06-18 1997-04-22 가부시기가이샤 히다찌세이사뀨쇼 Vortex flow blower

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WO2010052082A1 (en) 2010-05-14
DE102008056106B4 (en) 2011-02-17
EP2342464A1 (en) 2011-07-13
DE102008056106A1 (en) 2010-05-20

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