EP0477650B1 - Seitenkanalgebläse - Google Patents

Seitenkanalgebläse Download PDF

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Publication number
EP0477650B1
EP0477650B1 EP91115274A EP91115274A EP0477650B1 EP 0477650 B1 EP0477650 B1 EP 0477650B1 EP 91115274 A EP91115274 A EP 91115274A EP 91115274 A EP91115274 A EP 91115274A EP 0477650 B1 EP0477650 B1 EP 0477650B1
Authority
EP
European Patent Office
Prior art keywords
blower
passageway
cooling
impeller
vortex flow
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.)
Expired - Lifetime
Application number
EP91115274A
Other languages
English (en)
French (fr)
Other versions
EP0477650A3 (en
EP0477650A2 (de
Inventor
Ito Eiichi
Susumu Yamazaki
Masayuki Fujio
Toshiharu Yoshidomi
Hiroshi Asabuki
Kazuo Kobayashi
Kengo Hasegawa
Yukio Chihara
Hajime Fujita
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.)
Hitachi Ltd
Original Assignee
Hitachi Ltd
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
Priority claimed from JP2242323A external-priority patent/JP2865835B2/ja
Priority claimed from JP27632490A external-priority patent/JPH04153597A/ja
Priority claimed from JP2279013A external-priority patent/JP2776976B2/ja
Priority claimed from JP27901590A external-priority patent/JP2714245B2/ja
Priority claimed from JP2279014A external-priority patent/JP2865849B2/ja
Application filed by Hitachi Ltd filed Critical Hitachi Ltd
Publication of EP0477650A2 publication Critical patent/EP0477650A2/de
Publication of EP0477650A3 publication Critical patent/EP0477650A3/en
Application granted granted Critical
Publication of EP0477650B1 publication Critical patent/EP0477650B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • 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
    • F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
    • F04D29/056—Bearings
    • F04D29/059—Roller bearings
    • 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
    • F04D25/00—Pumping installations or systems
    • F04D25/02—Units comprising pumps and their driving means
    • F04D25/06—Units comprising pumps and their driving means the pump being electrically driven
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D25/00—Pumping installations or systems
    • F04D25/02—Units comprising pumps and their driving means
    • F04D25/08—Units comprising pumps and their driving means the working fluid being air, e.g. for ventilation
    • F04D25/082—Units comprising pumps and their driving means the working fluid being air, e.g. for ventilation the unit having provision for cooling the motor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/44—Fluid-guiding means, e.g. diffusers
    • F04D29/441—Fluid-guiding means, e.g. diffusers especially adapted for elastic fluid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/58—Cooling; Heating; Diminishing heat transfer
    • F04D29/5806—Cooling the drive system
    • 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
    • F04D29/58—Cooling; Heating; Diminishing heat transfer
    • F04D29/582—Cooling; Heating; Diminishing heat transfer specially adapted for elastic fluid pumps
    • F04D29/5826—Cooling at least part of the working fluid in a heat exchanger
    • 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
    • F04D29/58—Cooling; Heating; Diminishing heat transfer
    • F04D29/582—Cooling; Heating; Diminishing heat transfer specially adapted for elastic fluid pumps
    • F04D29/584—Cooling; Heating; Diminishing heat transfer specially adapted for elastic fluid pumps cooling or heating the machine
    • 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

Definitions

  • the present invention relates to a vortex flow blower of the kind referred to in the preamble portion of claim 1.
  • a vortex flow blower is known from US-A-4 483 656.
  • Conventional apparatus are constituted such that, as disclosed in Japanese Utility Model Laid-Open Application No. 49-130406, an electric motor is provided in a spaced relationship from a fan casing and a location therebetween is used as a ventilating passageway for enabling windings and bearings of the electric motor to be cooled.
  • a conventional vortex pump has around an inlet port, as disclosed, for example, in Japanese Patent Publication Application No. 46-33658, a construction such that the sectional area in the neighborhood of such inlet port is made greater than the sectional area of an intermediate portion of an annular groove so as to only reduce the resistance of a flow passageway to wind or air.
  • a conventional vortex flow blower also utilizes a conventional silencer or muffler installed at each of an inlet port and an outlet port and a high pitch sound diffusing porous tube is built in the inside of each of the silencers as disclosed, for example, in the Official Gazette of Japanese Utility Model Laid-Open Application No. 56-109690. Furthermore, another structure is disclosed in the Official Gazette of Japanese Laid-Open Application No. 58-4795 wherein a silencer constituted from a tubular case is provided at an exhaust port of a blower and a tubular silencing material having a heat insulating property is provided on an inner periphery of the case. Also, is it known to frequently use an expansion type silencer and a branch type silencer as silencers for an automobile.
  • a conventional vortex blower utilized as a centrifugal pump includes a silencer or muffler casing having shape equal or similar to a rectangular parallepiped to provide a volume for deadening noise, and with sidewalls rising straight from its base, as shown in Japanese Patent Application Laid-Open No. 52600/1981.
  • the prior art described above does not pay any attention to reduction in size and mass productivity of the vortex flow blower, and since an electric motor casing and a blower casing are coupled to each other by a coupling arrangement with a spacing left therebetween and with a heat insulating wall is disposed therebetween, there are problems that the dimensions of the vortex flow blower (particularly the dimension along a direction of the shaft of the rotor of the electric motor) are increased, that the number of parts is great, and that the means productivity ability is lowered. Further, since the number of parts is great the number of operation steps in assembly is great such that the quality is not uniform and reliability is low because high accuracy in assembly is not attained.
  • Factors resulting in production of noises by a vortex flow blower include (a) collision noises at an outlet port, (b) collision noises between a whirling flow in a casing flow passageway and a front edge of a vane of the impeller, (c) expansion noises and mixing noises at an inlet port, (d) disorder noises during whirling of a whirling flow, and so forth.
  • the production amount of noise of (a) and (b) is much greater than the production amount of (c) and (d), and in order to reduce noise, it is important to reduce (a) and (b) or reduce noise by a silencer.
  • a relative flow w1 upon flowing into vanes of the impeller is experimentally determined from a flowing-in flow (absolute flow) c1 of air into the vanes and a vane circumferential speed u1
  • the relative flow w1 is about 2.5 times the vane circumferential speed u1 and is a very high flowing speed. Due to such flowing in speed w1, disorders are produced by flowing-in to front edges of the vanes, and thus lower the efficiency of the vortex flow blower and produces noises.
  • the relationship between noises of a vortex flow blower and an inlet flow rate has such a characteristic that, as the flow rate increases, noises are decreased and the noise level is highest at a point of cut-off.
  • the noise level at an operating point of the vortex flow blower is high, and, for example, where the power of the shaft of a motor is on the order of 400W, the noise level is about 85 to 95 dB (without a silencer) and is therefore high. Additionally, the noise characteristic in this instance is such that a dominant sound pressure level, like a chimney, is exhibited at a frequency (rotational noise) of [vane number x rotational speed] at which noises of a shrill tone are produced.
  • a silencer is provided at each of the inlet side and the outlet side, and the effect of the silencers is that, where the silencers for both of the inlet side and the outlet side are provided, the noise level is reduced to about 65 to 70 dB, but rotational noises of [vane number x rotational speed] still remain dominantly like a chimney and have a shrill disagreeable tone. Thus, reduction of such rotational noises is desired.
  • US-A-4 483 656 discloses a vortex flow blower including a blower casing having an annular flow passageway extending from an inlet port for receiving fluid to an outlet port for discharging the fluid, the outlet port being disposed adjacent to the inlet port, an impeller accommodated in the blower casing for producing a vortex flow of the fluid in the annular flow passageway, means for driving the impeller, and enabling means for enabling at least one of a reduction of temperature of the fluid discharged from the vortex flow blower, an increase in at least one of flow rate and pressure of the discharge fluid, a reduction in noise level of the vortex flow blower, and a compact configuration of the vortex flow blower.
  • Figs. 1 and 2 are front and rear perspective views, respectively, of a vortex flow blower in accordance with the present invention.
  • Fig. 3 is a front elevational sectional view showing construction of a vortex flow blower according to an embodiment of the present invention.
  • Fig. 4 is a sectional view taken along line A-A of Fig. 3.
  • Fig. 5 is a sectional view taken along line B-B of Fig. 3.
  • Fig. 6 is a side elevational view of the vortex flow blower of the present embodiment.
  • Fig. 7 is a diagram showing a temperature upon cut-off operation of the vortex flow blower of the present embodiment.
  • Fig. 8 is a characteristic diagram showing a shaft power and a temperature with respect to an amount of fluid of the vortex flow blower of the present embodiment.
  • Fig. 9 is a characteristic diagram showing a difference in aerodynamic characteristic depending upon presence or absence of a cooling ventilating passageway.
  • Fig. 10 is a front elevational sectional view of a modification of the present embodiment.
  • Fig. 11 is a side elevational sectional view showing a principal portion of another modification of the present embodiment.
  • Figs. 12 and 13 are a front elevational sectional view and a side elevational view, respectively, of a further modification to the present embodiment.
  • FIGs. 1 and 2 are a front and rear perspective view of a vortex flow blower in accordance with the present invention wherein casing 2 of the motor blower includes a blower or impeller casing 3, a motor casing 4, and a silencer or muffler casing 5.
  • an electric motor 30 serving as a driver has an impeller 1 of the blower connected to an end of a rotary shaft 14 thereof while a cooling impeller 18 is connected to the other end of the rotary shaft 14.
  • the electric motor 30 includes a rotor 16 fitted on the rotary shaft 14 and a stator 17 fitted in the motor casing 4.
  • the shaft 14 is supported by a radial bearing 14a provided adjacent the impeller 1 and another radial bearing 14b provided adjacent the cooling impeller 18.
  • the impeller 1 is accommodated in the blower casing 3 which is provided with a cover 15.
  • the blower casing 3 has an annular flow passageway 3a provided in an opposing relationship to vanes of the impeller 1 and extending from an inlet port 3b to an outlet port 3c.
  • the stator 17 of the electric motor 30 When the stator 17 of the electric motor 30 is energized, the rotor 16 mounted on the rotary shaft 14 is rotated, and consequently, the impeller 1 sucks air from the inlet port 3b, pressurizes the air in the annular passageway 3a and discharges the air from the outlet port 3c.
  • the silencer casing 5 for reducing noises is provided for each of the inlet port 3b and outlet port 3c.
  • the blower casing 3 is formed in an integral relationship with an electric motor casing 4 and the silencer casing 5 by aluminum diecasting.
  • an axial cooling ventilating passageway or gap 36 is formed between the electric motor casing and the silencer casing 5, and a radial cooling ventilating passageway 34 serving as a radially provided cooling passageway is formed between the inlet port 3b and the outlet port 3c of the blower casing 3 in a contiguous relationship to the cooling ventilating passageway 36 as shown in Fig. 5.
  • External air 13 is taken into the blower by the cooling impeller or fan 18 and is advanced toward the blower casing 3 through the axial cooling ventilating passageway 36 until it comes to a location in the neighborhood of the bearing 14a adjacent the annular flow passageway, and then it changes the direction and enters the radial cooling ventilating passageway 34, whereafter it passes between the inlet port 3b and the outlet port 3c and is then discharged outside.
  • Heat generation is heat the electric motor 30 generates from a portion of the blower, and discharging of heat is dominantly performed by heat transmission by ventilation wherein the cooling fan or impeller 18 and the blower impeller 1 serve as ventilation sources. Heat generation increases continuously as the blower operating condition advances from an open condition to a cut-off condition because the power of the shaft increases continuously.
  • the cooling performance while discharging of heat by the cooling impeller 18 is substantially constant, discharging of heat by air discharged from the blower decreases continuously until it becomes equal to 0 by cut-off.
  • the temperature rise of the bearing 14a presents, due to an influence of the thermal income and outgo described above, such a curve which rises toward the cut-off as shown in Fig. 8.
  • the blower exhibits an aerodynamic characteristic having a high static pressure.
  • the axial cooling ventilating passageway 36 and the radial cooling ventilating passageway 34 as a unitary form in the casing 2, which is advantageous when it is produced as a casting or a molded article (plastic, die-cast and so forth). Characteristics of the vortex flow blower of the present embodiment will be described with reference to Figs. 7 to 9.
  • a surface temperature of the cooling ventilating passageway of the vortex flow blower of the present embodiment and a temperature of air after passing the cooling ventilating passageway were measured at points C and D of Fig. 3, respectively; an outer surface temperature of the blower casing and a temperature of air after passing the outer surface of the blower casing were measured at points E and F of Fig. 6, respectively; and a temperature of the bearing 14a on the blower casing side was measured at a point G of Fig. 3 and curves showing results of such measurements are indicated in Fig. 8. Further, measurement values at the measurement points C, D, E and F upon cut-off operation are indicated in Fig. 7
  • the temperature increase value of air passing the cooling ventilating passageways 36 and 34 is 65°C, and this indicates that it is a cooling capacity about three times per the same flow rate as compared with the temperature increase value 20°C of air flowing along the outer surface of the blower casing 3.
  • the present embodiment can obtain a great cooling capacity as compared with the case wherein air is passed only along the outer surface of the blower casing. Due to such difference in cooling capacity, also air in the blower casing 3 and in the impeller 1 is lowered in temperature, and consequently, the specific weight of air is increased. As a result, the air performance can be improved as compared with an apparatus which does not have a cooling ventilating passageway as shown in the curves of Fig. 9.
  • the radial cooling venting passageway 34 passes air, which has passed through the axial cooling ventilating passageway 36, between the outlet port 3c and the inlet port 3b, and which both exhibit a substantially maximum temperature rise a superior cooling performance is obtained, and since a location between the outlet port 3a and the inlet port 3b which is a break of the annular flow passageway 3c is used effectively, the distance in the axial direction can be minimized.
  • FIG. 11 Another modification to the present embodiment will be described with reference to Fig. 11, wherein a cover portion 5h is provided for the axial ventilating passageway 36 to form an independent duct to increase an air current into the radial ventilating passageway 34 so as to improve the cooling performance.
  • FIG. 12 A further modification to the present embodiment will be described with reference to Figs. 12 and 13, wherein a guide 3d is provided below the blower casing 3 such that cooling air blown out from the radial ventilating passageway 34 is guided by the guide 3j so that it flows along an outer periphery of the blower casing 3 as indicated by a heavy arrow mark in Fig. 13.
  • a guide 3d is provided below the blower casing 3 such that cooling air blown out from the radial ventilating passageway 34 is guided by the guide 3j so that it flows along an outer periphery of the blower casing 3 as indicated by a heavy arrow mark in Fig. 13.
  • the vortex flow blower of the present modification is mounted on a mounting base shown by an alternate long and short dash line in Fig. 12, then air blown out from the radial ventilating passageway 34 collides with the mounting base and changes its direction so that it advances toward the cover 15.
  • a baffle portion 15a is formed on the cover 15 so that such air flow in
  • the present invention provides a vortex flow blower or centrifugal pump applicable not only to air type but also liquid type which is easy to transport, produces an outstandingly good result of noise deadening, and has both a small height and a small muffler casing width.

Claims (3)

  1. Wirbelströmungsgebläse, das ein Gebläsegehäuse (3) mit einem ringförmigen Strömungsdurchlaß (3a), der sich von einem Einlaßkanal (3b) für die Aufnahme von Fluid zu einem Auslaßkanal (3c) für die Ausgabe des Fluids erstreckt, wobei der Auslaßkanal (3c) in der Nähe des Einlaßkanals (3b) angeordnet ist, ein Laufrad (1), das im Gebläsegehäuse (3) untergebracht ist, um im ringförmigen Strömungsdurchlaß (3a) eine Wirbelströmung des Fluids zu erzeugen, eine Einrichtung (30) zum Antreiben des Laufrades (1), wobei die Antriebseinrichtung (30) einen Elektromotor umfaßt, wobei das Laufrad (1) mit einem Ende der Welle (14) seines Rotors (16) verbunden ist und ein Kühlgebläserad (18) mit dem anderen Ende der Welle (14) des Rotors (16) verbunden ist, sowie eine Ermöglichungseinrichtung enthält, die wenigstens entweder eine Reduzierung der Temperatur des vom Wirbelströmungsgebläse ausgegebenen Fluids oder eine Erhöhung wenigstens entweder der Strömungsrate oder des Drucks des ausgegebenen Fluids oder eine Reduzierung des Geräuschpegels des Wirbelströmungsgebläses oder eine kompakte Konfiguration des Wirbelströmungsgebläses ermöglicht,
    dadurch gekennzeichnet, daß
    die Ermöglichungseinrichtung eine Einrichtung enthält, die einen Kühlungsdurchlaß (36), der zwischen dem Einlaßkanal (3b) und dem Auslaßkanal (3c) angeordnet ist, begrenzt, um wenigstens eine Oberfläche eines Abschnitts des ringförmigen Strömungsdurchlasses (3a) zu kühlen, der sich zwischen dem Einlaßkanal (3b) und dem Auslaßkanal (3c) erstreckt,
    das Kühlgebläserad eine Kühlungsluftströmung durch den Kühlungsdurchlaß (36) erzeugt, und
    eine Einrichtung vorgesehen ist, die einen Belüftungsdurchlaß (34) begrenzt und mit dem Kühlungsdurchlaß (36) in Verbindung steht, wobei die den Belüftungsdurchlaß begrenzende Einrichtung ein Rohrleitungselement ist.
  2. Wirbelströmungsgebläse nach Anspruch 1, in dem das Gebläsegehäuse eine Führungseinrichtung enthält, um Kühlungsluft entlang einer äußeren Umfangsfläche des Gebläsegehäuses zu führen, wobei der Kühlungsdurchlaß (36) ermöglicht, daß hiervon ausgegebenes Fluid durch die Führungseinrichtung in der Weise geführt wird, daß das Fluid entlang der äußeren Umfangsfläche des Gebläsegehäuses (4) strömt.
  3. Wirbelströmungsgebläse nach Anspruch 1, in dem das Gebläsegehäuse (4) ein Paar von ringförmigen Strömungsdurchlässen (3a) enthält, die auf gegenüberliegenden Seiten des Laufrades (1) angeordnet sind, wobei das Laufrad Schaufeln aufweist, die sich gegenüber dem Paar von ringförmigen Durchlässen befinden.
EP91115274A 1990-09-14 1991-09-10 Seitenkanalgebläse Expired - Lifetime EP0477650B1 (de)

Applications Claiming Priority (10)

Application Number Priority Date Filing Date Title
JP242323/90 1990-09-14
JP2242323A JP2865835B2 (ja) 1990-09-14 1990-09-14 渦流ブロワ
JP276324/90 1990-10-17
JP27632490A JPH04153597A (ja) 1990-10-17 1990-10-17 渦流ブロワ
JP279013/90 1990-10-19
JP2279013A JP2776976B2 (ja) 1990-10-19 1990-10-19 渦流ポンプ
JP27901590A JP2714245B2 (ja) 1990-10-19 1990-10-19 渦流ポンプ
JP2279014A JP2865849B2 (ja) 1990-10-19 1990-10-19 渦流ポンプ
JP279014/90 1990-10-19
JP279015/90 1990-10-19

Publications (3)

Publication Number Publication Date
EP0477650A2 EP0477650A2 (de) 1992-04-01
EP0477650A3 EP0477650A3 (en) 1992-07-15
EP0477650B1 true EP0477650B1 (de) 1996-05-29

Family

ID=27530066

Family Applications (1)

Application Number Title Priority Date Filing Date
EP91115274A Expired - Lifetime EP0477650B1 (de) 1990-09-14 1991-09-10 Seitenkanalgebläse

Country Status (3)

Country Link
EP (1) EP0477650B1 (de)
KR (1) KR100190424B1 (de)
DE (1) DE69119854T2 (de)

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4326505C2 (de) * 1993-08-06 2002-03-14 Bosch Gmbh Robert Peripheralpumpe, insbesondere zum Fördern von Kraftstoff aus einem Vorratstank zur Brennkraftmaschine eines Kraftfahrzeugs
DE102007017915A1 (de) * 2007-04-13 2008-10-23 Gebr. Becker Gmbh Seitenkanalverdichter
KR20100097165A (ko) * 2007-12-21 2010-09-02 요네하라기켄유켄가이샤 가압 원심 펌프
KR101377057B1 (ko) 2012-08-02 2014-03-24 (주) 에이스터보 터보 블로워장치
DE102012023347B3 (de) * 2012-11-29 2014-01-30 Tni Medical Ag Kleiner, geräuscharmer Seitenkanalverdichter, insbesondere für Geräte in der Beatmungstherapie
KR101911782B1 (ko) * 2013-01-25 2018-10-26 한온시스템 주식회사 연료전지 차량용 공기 블로워
DE102016103525A1 (de) * 2016-02-29 2017-08-31 Pierburg Gmbh Gebläse für einen Verbrennungsmotor
WO2019201448A1 (de) * 2018-04-20 2019-10-24 Siemens Aktiengesellschaft Funktionseinheit eines verdichtersystems
CN114738302B (zh) * 2022-03-28 2023-05-09 浙江颐顿机电有限公司 一种可调压式漩涡风机
DE102022210555A1 (de) 2022-10-06 2024-04-11 Ziehl-Abegg Se Ventilator und Kühlstruktur für einen Ventilator

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2043926A5 (de) * 1969-05-02 1971-02-19 Manoury Leon
DE2001395B2 (de) * 1970-01-14 1978-11-09 Werner Rietschle Maschinen- Und Apparatebau Kg, 7860 Schopfheim Seitenkanalgeblaese
DE2712298C3 (de) * 1977-03-21 1980-10-09 Siemens Ag, 1000 Berlin Und 8000 Muenchen Seitenkanalverdichter
JPS58106195A (ja) * 1981-12-18 1983-06-24 Hitachi Ltd 渦流送風機
JPS6483882A (en) * 1987-09-25 1989-03-29 Fuji Electric Co Ltd Ring blower

Also Published As

Publication number Publication date
KR100190424B1 (ko) 1999-06-01
KR920006657A (ko) 1992-04-27
EP0477650A3 (en) 1992-07-15
DE69119854D1 (de) 1996-07-04
DE69119854T2 (de) 1996-10-10
EP0477650A2 (de) 1992-04-01

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