EP1013938B1 - Low specific speed blower rotor - Google Patents
Low specific speed blower rotor Download PDFInfo
- Publication number
- EP1013938B1 EP1013938B1 EP98124090A EP98124090A EP1013938B1 EP 1013938 B1 EP1013938 B1 EP 1013938B1 EP 98124090 A EP98124090 A EP 98124090A EP 98124090 A EP98124090 A EP 98124090A EP 1013938 B1 EP1013938 B1 EP 1013938B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- impeller
- blade
- air
- blower
- efficiency
- 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
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- 230000000241 respiratory effect Effects 0.000 claims description 3
- 230000007423 decrease Effects 0.000 claims description 2
- 239000000428 dust Substances 0.000 claims description 2
- 238000001914 filtration Methods 0.000 claims description 2
- 230000001681 protective effect Effects 0.000 claims description 2
- 238000005259 measurement Methods 0.000 description 10
- 238000010586 diagram Methods 0.000 description 5
- 238000002474 experimental method Methods 0.000 description 3
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 3
- 244000052616 bacterial pathogen Species 0.000 description 2
- 230000001419 dependent effect Effects 0.000 description 2
- 238000013461 design Methods 0.000 description 2
- 239000007789 gas Substances 0.000 description 2
- 230000029058 respiratory gaseous exchange Effects 0.000 description 2
- WHXSMMKQMYFTQS-UHFFFAOYSA-N Lithium Chemical compound [Li] WHXSMMKQMYFTQS-UHFFFAOYSA-N 0.000 description 1
- 239000003795 chemical substances by application Substances 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 230000006866 deterioration Effects 0.000 description 1
- 239000003814 drug Substances 0.000 description 1
- 230000002538 fungal effect Effects 0.000 description 1
- 238000002347 injection Methods 0.000 description 1
- 239000007924 injection Substances 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 229910052744 lithium Inorganic materials 0.000 description 1
- 230000007774 longterm Effects 0.000 description 1
- 229910052751 metal Inorganic materials 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 239000002245 particle Substances 0.000 description 1
- 230000002093 peripheral effect Effects 0.000 description 1
- 238000011160 research Methods 0.000 description 1
- 230000002441 reversible effect Effects 0.000 description 1
- 230000003068 static effect Effects 0.000 description 1
- 238000001356 surgical procedure Methods 0.000 description 1
- 238000012360 testing method Methods 0.000 description 1
- 238000009423 ventilation Methods 0.000 description 1
- 239000013585 weight reducing agent Substances 0.000 description 1
Images
Classifications
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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
- F04D29/00—Details, component parts, or accessories
- F04D29/26—Rotors specially for elastic fluids
- F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
- F04D29/30—Vanes
-
- 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
- F04D29/26—Rotors specially for elastic fluids
- F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
- F04D29/284—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for compressors
Definitions
- the invention relates to an impeller, in particular a high-pressure impeller, for radial fans according to the preamble of the claim 1.
- measuring devices are used for determination of the germ content in the air.
- the air is in a slit-like cross-section Speeds of 10 m / sec. up to 70 m / sec. accelerates.
- the Volume flows are 28 l / m. up to 100 l / min.
- the one there necessary pressure differences are 200 to 5000 Pa.
- the required fan power is 1 to 9 watts.
- the filtration method is also used to determine the Germ content of the air applied.
- the air is sucked through filters and the germs are picked up deposited on the filter.
- the volume flows here are 3.5 l / min. up to 150 l / min., the necessary pressure differences at 300 to 8000 Pas.
- the required blower output is 1 up to 20 watts.
- Ventilated respiratory protection hoods are used in surgery used, with fan lines as mentioned above.
- a well-known radial blower that delivers the required performance at least comes close is mentioned below.
- the at DC motor used in this blower has the same Data such as the motor related to the invention. Only one The difference is that he is not so heavily loaded can. Power output is up to a voltage of 13.2 V. and the speed of both motors is the same.
- the invention has for its object the above Improve the impeller in such a way that it is a significant one Has increased performance, and especially as High-pressure impeller for small volume flows with a clear one Award for increased efficiency.
- Another object of the invention is to increase this performance miniaturization and related To achieve weight reduction in radial compressors, so that this opens up new areas of application.
- the blade entry angle ⁇ 1 should be at least 55 ° and at most 80 °.
- the fan efficiency is in all five measured working areas between 50.5% -55.7%.
- n q values were between 9.1 and 9.9 min ⁇ 1 , which means that they did not even reach the lower limit.
- the invention on the other hand, presented in the published patent application on average requires 0.17 watts per mm of water, which is a Performance increase of almost 40% compared to normal house vacuum cleaners means.
- the invention mentioned is a three-stage one Blower (3 paddle wheels and 2 guide wheels). Also vacuum cleaners usually have a multi-stage blower.
- the significantly higher efficiency of the new miniature blower (approx. 40%) compared to vacuum cleaners (according to the manufacturer's information 12 to 22%) is an indication that with the impeller (larger diameter) according to claim 1 and / or 2 also blowers this size can be improved.
- multi-stage blowers can also be used with the new impeller develop.
- Impeller drive motor DC motor 0.25 watts, nominal voltage 3.5 V, weight 3.5 g. Total weight: impeller, volute casing, Motor: 9.5 g.
- the blower which was once again greatly reduced in size, was integrated into a cylindrical housing with a diameter of 40 mm and a length of 100 mm, and air was drawn through a filter with a diameter of 37 mm. Particles, germs and fungal spores with a diameter of up to 0.3 ⁇ m are deposited on the filter.
- the small functional model of a miniature air sampler was operated by a lithium battery with a nominal voltage of 3.6 volts. The power consumed by the motor was 0.054 watts. The operating time with one battery was 150 hours. The volume flow through the filter was 60 liters per hour. The total weight of the functional model is 90 grams.
- the cover plate of the impeller is shown, the consists of a flat circular disc (1) which in Center also has a circular opening (2).
- the Disc has on one or more bolt circles (depending of the impeller diameter) holes (3) that the Correspond to the number of blades.
- the impeller (4) shown in Figure 2 is in one piece milled (or designed as a plastic injection molded part) the bucket height (5) (see cross-sectional view) constant is.
- the blades (6) are curved backwards.
- the knobs (7) are with the cover plate (1) ultrasonically welded (for plastic) or riveted (for metal).
- the central bore (8) is used for attachment on the drive shaft.
- FIG. 2a (section from FIG. 2) shows the blade channel, formed by two profiled impeller blades, and the blade entry and exit angles ⁇ 1 and ⁇ 2 according to the present invention.
- Figure 9 shows the impeller according to claims 1 and 2 of the present Invention, which has a diameter of 26 mm.
- FIG. 10 shows the blade channel cross section A k as a function of the channel length 1 according to the present invention.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Description
Die Erfindung betrifft ein Laufrad, insbesondere Hochdrucklaufrad,
für Radialgebläse nach dem Oberbegriff des Anspruches
1.The invention relates to an impeller, in particular a high-pressure impeller,
for radial fans according to the preamble of the
Aus der US-A-2 767 906 ist ein Radialventilatorlaufrad bekannt, bei dem der Schaufelkanalquerschnitt Ak in Abhängigkeit von der Kanallänge von innen nach außen abnimmt. Auch haben die Schaufeln eine konstante Dicke. Nachteilig macht sich bei dieser vorbekannten Lehre bemerkbar, daß die Schaufeldicke und somit die Schaufelversperrung gering ist, so daß die Fördermenge des Gases kaum eingeschränkt wird. Zwar hat letzteres den Vorteil der Laufruhe, jedoch wird der Wirkungsgrad erheblich eingeschränkt.From US-A-2 767 906 a radial fan impeller is known in which the blade duct cross section A k decreases from the inside to the outside depending on the duct length. The blades also have a constant thickness. A disadvantage of this previously known teaching is that the blade thickness and thus the blade blockage are small, so that the flow rate of the gas is hardly restricted. The latter has the advantage of running smoothly, but the efficiency is considerably restricted.
Im Bereich der Lufthygiene werden Messgeräte zur Bestimmung des Keimgehaltes der Luft eingesetzt. Bei der Impaktionsmethode wird die Luft in einem schlitzartigen Querschnitt auf Geschwindigkeiten vom 10 m/sec. bis 70 m/sec. beschleunigt.In the field of air hygiene, measuring devices are used for determination of the germ content in the air. With the impaction method the air is in a slit-like cross-section Speeds of 10 m / sec. up to 70 m / sec. accelerates.
Die Volumenströme liegen bei 28 l/m. bis 100 l/min. Die dabei nötigen Druckdifferenzen liegen bei 200 bis 5000 Pa. Die erforderlichen Gebläseleistungen betragen 1 bis 9 Watt.The Volume flows are 28 l / m. up to 100 l / min. The one there necessary pressure differences are 200 to 5000 Pa. The required fan power is 1 to 9 watts.
Ebenso wird die Filtrationsmethode bei der Bestimmung des Keimgehaltes der Luft angewandt.The filtration method is also used to determine the Germ content of the air applied.
Hierbei wird die Luft durch Filter gesaugt und die Keime auf dem Filter abgeschieden.The air is sucked through filters and the germs are picked up deposited on the filter.
Die Volumenströme liegen hier bei 3.5 l/min. bis 150 l/min., die nötigen Druckdifferenzen bei 300 bis 8000 Pas. Die erforderlichen Gebläseleistungen betragen 1 bis 20 Watt.The volume flows here are 3.5 l / min. up to 150 l / min., the necessary pressure differences at 300 to 8000 Pas. The required blower output is 1 up to 20 watts.
Im Bereich des Arbeitsschutzes werden Staubmessgeräte, Schutzkleidungen mit gefilterter Atemluft eingesetzt. Gebläseleistungen in diesem Anwendengsbereich liegen ebenfalls in dem oben angeführtem Bereich.In the area of occupational safety, dust measuring devices, Protective clothing with filtered breathing air is used. Blower performance in this area of application are also in the area listed above.
In der Chirurgie werden ventilierte Atemluftschutzhauben eingesetzt, mit Gebläseleitungen wie oben angeführt.Ventilated respiratory protection hoods are used in surgery used, with fan lines as mentioned above.
In der Medizin werden zur Behandlung von schlafbezogenen Atmungsstörungen, und bei lebenserhaltenden Maßnamen (künstliche Beatmung) Geräte benötigt, die ebenfalls die oben genannten Gebläseleistungen erfordern.In medicine, for the treatment of sleep-related breathing disorders, and in life-supporting measures (artificial Ventilation) devices required, which also include the above Require blower performance.
Nach umfangreichen Marktrecherchen wurde festgestellt ,daß Kleingebläse mit den zuvor beschriebenen Leistungsanforderungen nicht angeboten werden. In der Praxis wird daher mit stark überdimensionierten Radialgebläsen (Leistungsaufnahme bis 350 Watt) oder auch Vakuumpumpen (Leistungsaufnahme bis 500 Watt ) gearbeitet. Ein wünschenswerter netzunabhägiger Betrieb (Akku oder Batterie) ist unter diesen Bedingungen nicht möglich.After extensive market research it was found that Small blowers with the performance requirements described above not be offered. In practice, therefore oversized radial blowers (power consumption up to 350 watts) or vacuum pumps (power consumption up to 500 watts) worked. A desirable off-grid Operation (battery or battery) is under these conditions not possible.
Ein bekanntes Radialgebläse, das der geforderten Leistung zumindest nahe kommt, wird weiter unten erwähnt. Der bei diesem Gebläse eingesetzte Gleichstrommotor hat die gleichen Daten wie der in der Erfindung verwandte Motor. Einziger Unterschied ist ,daß er nicht so hoch belastet werden kann. Bis zu einer Spannung von 13.2 V sind abgegebene Leistung und die Drehzahl beider Motoren gleich.A well-known radial blower that delivers the required performance at least comes close is mentioned below. The at DC motor used in this blower has the same Data such as the motor related to the invention. Only one The difference is that he is not so heavily loaded can. Power output is up to a voltage of 13.2 V. and the speed of both motors is the same.
Der Erfindung liegt die Aufgabe zugrunde, das eingangs genannte Laufrad derart zu verbessern, daß es eine erhebliche Leistungssteigerung aufweist, und sich insbesondere als Hochdrucklaufrad für kleine Volumenströme bei einer deutlichen Steigerung des Wirkungsgrades auszeichnet.The invention has for its object the above Improve the impeller in such a way that it is a significant one Has increased performance, and especially as High-pressure impeller for small volume flows with a clear one Award for increased efficiency.
Ein weiteres Ziel der Erfindung ist es, durch diese Leistungsteigerung eine Miniaturisierung und damit verbundene Gewichtsreduzierung bei Radialverdichtern zu erreichen, so daß sich mit diesem neue Anwendungsbereiche erschließen lassen.Another object of the invention is to increase this performance miniaturization and related To achieve weight reduction in radial compressors, so that this opens up new areas of application.
Diese Aufgabe wird erfindungsgemäß durch das im Anspruch 1
gekennzeichnete Laufrad gelöst.This object is achieved according to the invention in
Versuche haben überraschenderweise ergeben, daß der Schaufeleintrittswinkel β1 mind. 55° und maximal 80° aufweisen sollte.Surprisingly, tests have shown that the blade entry angle β 1 should be at least 55 ° and at most 80 °.
Messungen mit Laufrad (Fig.lund Fig.2) nach Anspruch 1 und 2
im Gehäuse mit Leitspirale.Measurements with impeller (Fig.lund Fig.2) according to
Antriebsmotor: Nennspannug 9 V, Leerlaufdrehzahl 10000 UPM,
Typenleistung 20 Watt Drehmomentkonstante 7,97 mNm/Amp.,
Max. Wirkungsgrad 77,1% .Drive motor: nominal voltage 9 V, idle speed 10000 rpm,
Im Diagramm (Fig.4) sind die Druckdifferenz in Abhängigkeit vom Volumenstrom (Drosselkurve), die Leistungsaufnahme des Motors und der Wirkungsgrad des Gesamtsystems Gebläseleistung/Motor-Input) angegeben.In the diagram (Fig.4) the pressure difference is dependent of the volume flow (throttle curve), the power consumption of the Motor and the efficiency of the overall system fan power / motor input) specified.
Aus den errechneten Werten der Motorabgabeleistung (mit den Parametern des Arbeitspunktes des maximalen Wirkungsgrades des Gesamtsystems) wurde der Wirkungsgrad des Radialverdichters ermittelt. (Gebläseleistung/Motorabgabeleistung.)From the calculated values of the engine output (with the Parameters of the operating point of the maximum efficiency of the overall system) was the efficiency of the radial compressor determined. (Blower output / engine output.)
Erste Messung bei einer konstanten Spannung von 9 V.First measurement at a constant voltage of 9 V.
Maximaler Wirkungsgrad des Gesamtsystems 38% bei 1100 Pa und
118 l/min. Gebläsewirkunsgrad 54% bei 1100 Pa und 118 l/min.Maximum efficiency of the
Zweite Messung bei einer konstanten Spannung von 12 V (Radialgebläse wie oben) Diagramm (Fig.5).Second measurement at a constant voltage of 12 V (radial fan as above) diagram (Fig. 5).
Maximaler Wirkungsgrad des Gesamtsystems 38% bei 2150 Pa und
128 l/min. Gebläsewirkungsgrad 53% bei 2150 Pa und
128 l/min.Maximum efficiency of the
Dritte Messung bei einer konstanten Spannung von 13.2 V (Radialgebläse wie oben) Diagramm (Fig.6). Third measurement at a constant voltage of 13.2 V (radial fan as above) diagram (Fig. 6).
Maximaler Wirkungsgrad des Gesamtsystems 38% bei 2800 Pa und
125 l/min. Gebläsewirkungsgrad 52% bei 2800 Pa und
125 l/min.Maximum efficiency of the
Vierte Messung bei einer konstanten Spannung von 15 V (Radialgebläse wie oben) Diagramm (Fig.7).Fourth measurement at a constant voltage of 15 V (radial fan as above) diagram (Fig. 7).
Maximaler Wirkungsgrad des Gesamtsystems 41% bei 3650 Pa und
141 l/min. Gebläsewirkungsgrad 55.7% bei 3650 Pa und
141 l/min.Maximum efficiency of the
Fünfte Messung bei einer konstanten Spannung von 18 V (Radialgebläse wie oben) Diagramm (Fig.8).Fifth measurement at a constant voltage of 18 V (radial fan as above) diagram (Fig. 8).
Maximaler Wirkungsgrad des Gesamtsystems 40% bei 5460 Pa und
150 l/min. Gebläsewirkungsgrad 50.5% bei 5460 Pa und
150 1/min.Maximum efficiency of the
Insbesondere durch die spezielle Laufradausbildung nach Anspruch
1 und 2 der Erfindung, mit einem Schaufeleintrittswinkel
β1 = 70.7 Grad (so daß die Eintrittsöffnung des
Schaufelkanales auf das Laufradzentrum gerichtet ist) und
einem Schaufelkanal wie er in Fig.3 dargestellt ist, wurde
in überraschender und nicht vorhersehbarer Weise ein sehr
hoher Wirkungsgrad erzielt.In particular by the special impeller design according to
In allen fünf gemessenen Arbeitsbereichen liegt der Gebläsewirkungsgrad zwischen 50.5%-55.7%.The fan efficiency is in all five measured working areas between 50.5% -55.7%.
Ein Vergleich mit dem Radialgebläse U97EM-12KK-3 12VDC des
Standes der Technik (Micronel AG) mit den Messungen der
Erfindung bei 12V und 13.2V zeigt im Bereich 50 bis
100 l/min. eine dreifach höhere Gebläseleistung der Erfindung
bei gleicher Motorspannung.A comparison with the radial blower U97EM-12KK-3 12VDC of the
State of the art (Micronel AG) with the measurements of the
Invention at 12V and 13.2V shows in the
Versuche mit Schaufeleintrittswinkeln β1 <40 Grad (die nach "Pfleiderer, C.: Die Kreiselpumpen für Flüssigkeiten und Gase, Springer-Verlag, Berlin, Göttingen, Heidelberg (1961) 1-23, 91-248, 352-393" errechneten Werte für die gemessenen fünf Arbeitsbereiche des Schaufeleintrittswinkels lagen zwischen 36-37 Grad) ergaben eine Reduzierung der Pumpenleistung um die Hälfte. Dabei wurden die Laufräder mit Winkeln kleiner 40 Grad im gleichem Gehäuse betrieben.Experiments with blade entry angles β 1 <40 degrees (the values calculated according to "Pfleiderer, C .: The centrifugal pumps for liquids and gases, Springer-Verlag, Berlin, Goettingen, Heidelberg (1961) 1-23, 91-248, 352-393" For the five working ranges of the blade entry angle measured between 36-37 degrees), the pump output was reduced by half. The impellers were operated with angles less than 40 degrees in the same housing.
Versuche mit einem Schaufelkanalquerschnitt, der sich bis zum Ende der Umfangskante stetig vergrößert (wie in Bohl, Willi: Strömungsmaschinen, Vogel, (Vogel-Fachbuch) (Kamprath-Reihe) 2. Berechnung und Konstruktion - 5. Aufl.-1995, vorgegeben), brachten ebenfalls eine Verschlechterung der Gebläseleistung.Try a blade channel cross section that extends up to steadily enlarged at the end of the peripheral edge (as in Bohl, Willi: Turbomachinery, Vogel, (Vogel specialist book) (Kamprath series) 2. Calculation and construction - 5th edition-1995, given), also brought about a deterioration the blower output.
Die Versuche zeigen, daß das nach Anspruch 1 und/oder 2 gestaltete Laufrad die Hauptursache für die große Leistungssteigerung bei gleichzeitiger Steigerung des Wirkungsgrades ist.The experiments show that the designed according to claim 1 and / or 2 Impeller the main cause of the big increase in performance while increasing efficiency is.
Der hohe Wirkungsgrad ist um so erstaunlicher, da in der genannten Literatur genau das Gegenteil angegeben wird. Als wichtigste Größen werden die spezifische Drehzahl nq und die Gebläsegröße, ausgedrückt im Volumenstrom, genannt. Für Radiallaufräder soll die spezifische Drehzahl nq zwischen 10 und 80 min-1 liegen.The high level of efficiency is all the more astonishing since the opposite is stated in the literature mentioned. The most important variables are the specific speed n q and the fan size, expressed in volume flow. For radial impellers, the specific speed n q should be between 10 and 80 min -1 .
Bei den fünf angeführten Versuchen mit dem erfindungsgemäß gestalteten Laufrad lagen die nq-Werte bei 9.1 bis 9.9 min-1, erreichen also nicht einmal den unteren Grenzwert.In the five experiments with the impeller designed according to the invention, the n q values were between 9.1 and 9.9 min −1 , which means that they did not even reach the lower limit.
Der Volumenstrom bei dem Gebläse ist so klein, daß er in der letztgenannten Literatur ( Bild 1.31 Seite 35 ) nicht mehr dargestellt wird. Es wird angenommen, daß ein Gebläse dieser geringen Größe einen so schlechten Wirkungsgrad hat, daß es nicht mehr relevant ist.The volume flow in the blower is so small that it is in the the latter literature (Figure 1.31 page 35) no longer is pictured. It is believed that a blower of this type small size has such a poor efficiency that it is no longer relevant.
Das ist jedoch nach den Erkenntnissen des Erfinders nicht der Fall.However, according to the inventor's knowledge, this is not the case.
Da hier eine kleine Gebläsegröße mit gutem Wirkunggrad gewollt ist, wäre also nur die spezifische Drehzahl zu erhöhen. Eine Verdopplung der Motordrehzahl würde den nq - Wert auf knapp 20 min-1 erhöhen, was den Umkehrschluß zuläßt, daß die patentgemäße Gestaltung des Gebläselaufrades zur Folge hat, daß schon bei relativ kleinen Drehzahlen, im Verhältnis zum Laufraddurchmesser, gute Ergebnisse erreicht werden.Since a small fan size with a good degree of efficiency is desired, only the specific speed would have to be increased. A doubling of the engine speed would increase the n q value to just under 20 min -1 , which allows the reverse conclusion that the patented design of the fan impeller means that good results are achieved even at relatively low speeds in relation to the impeller diameter.
Betrachtung des statischen Druckes (Volumenstrom = 0) bzw. an der Saugseite gemessen auch als Saugkraft bezeichnet.Consideration of the static pressure (volume flow = 0) or measured on the suction side also referred to as suction power.
In der Offenlegungsschrift DE 3204113 A1 wird für normale Hausstaubsauger pro mm Wassersäule Saugkraft 0,26 bis 0,29 Watt Leistungsaufnahme angegeben, im Mittel also 0,275 Watt.In the published patent application DE 3204113 A1 for normal House vacuum cleaner per mm water column suction power 0.26 to 0.29 watts of power consumption indicated, on average 0.275 watts.
Die dagegen in der Offenlegungschrift vorgestellte Erfindung benötigt im Mittel pro mm Wassersäule 0,17 Watt, was eine Leistungssteigerung von fast 40% gegenüber normalen Hausstaubsaugern bedeutet.The invention, on the other hand, presented in the published patent application on average requires 0.17 watts per mm of water, which is a Performance increase of almost 40% compared to normal house vacuum cleaners means.
Bei der genannten Erfindung handelt es sich um ein dreistufiges Gebläse (3 Schaufelräder und 2 Leiträder). Auch Hausstaubsauger haben in der Regel ein mehrstufiges Gebläse.The invention mentioned is a three-stage one Blower (3 paddle wheels and 2 guide wheels). Also vacuum cleaners usually have a multi-stage blower.
Bei den durchgeführten fünf Messungen mit dem erfindungsgemäßem Laufrad wurden pro Millimeter Wassersäule Saugkraft 0.0225 bis 0.034 Watt benötigt, im Mittel wurden 0,0287 Watt benötigt.In the five measurements carried out with the inventive Impeller were suction power per millimeter of water 0.0225 to 0.034 watts were required, an average of 0.0287 watts needed.
Daraus ergibt sich eine Leistungssteigerung, gegenüber den Hausstaubsaugern, von 89% und gegenüber der in der Offenlegungsschrift zitierten Erfindung von 83%.This results in an increase in performance compared to Vacuum cleaners, of 89% and compared to that in the published patent application cited invention of 83%.
Der deutlich höhere Wirkungsgrad des neuen Miniaturgebläses
(ca.40%) gegenüber Hausstaubsaugern (nach Herstellerangaben
12 bis 22% ) ist ein Hinweis darauf, daß mit dem Laufrad
(größeren Durchmessers) nach Anspruch 1 und/oder 2 auch Gebläse
dieser Größe verbessert werden können. Selbstverständlich
lassen sich mit dem neuen Laufrad auch mehrstufige Gebläse
entwickeln.The significantly higher efficiency of the new miniature blower
(approx. 40%) compared to vacuum cleaners (according to the manufacturer's
Versuche mit einem nochmals stark verkleinertem Laufrad
(Fig.10) nach Anspruch 1 und/oder 2 Laufraddurchmesser
26 mm, Schaufelhöhe 2,5 mm, geschlossenes Laufrad. Try with a much smaller impeller
(Fig.10) according to
Antriebsmotor des Laufrades: DC Motor 0.25 Watt, Nennspannung 3.5 V, Gewicht 3,5 g. Gesamtgewicht: Laufrad, Spiralgehäuse, Motor: 9.5 g.Impeller drive motor: DC motor 0.25 watts, nominal voltage 3.5 V, weight 3.5 g. Total weight: impeller, volute casing, Motor: 9.5 g.
Das nochmals stark verkleinerte Gebläse wurde in ein zylindrisches Gehäuse mit einem Durchmesser von 40 mm und einer Länge von 100 mm Länge integriert und Luft durch einen Filter von 37 mm Durchmesser gesaugt. Auf dem Filter werden Partikel, Keime, und Pilzsporen bis zu einem Durchmesser von 0.3 µm abgeschieden. Das kleine Funktionsmodell eines Miniatur-Luftkeimsammlers wurde von einer Lithiumbatterie mit einer Nennspannung von 3,6 Volt betrieben. Die vom Motor aufgenommene Leistung betrug 0.054 Watt. Die Betriebszeit mit einer Batterie betrug 150 Stunden. Der Volumenstrom durch den Filter lag bei 60 Liter pro Stunde. Das Gesamtgewicht des Funktionmodells beträgt 90 Gramm.The blower, which was once again greatly reduced in size, was integrated into a cylindrical housing with a diameter of 40 mm and a length of 100 mm, and air was drawn through a filter with a diameter of 37 mm. Particles, germs and fungal spores with a diameter of up to 0.3 µm are deposited on the filter. The small functional model of a miniature air sampler was operated by a lithium battery with a nominal voltage of 3.6 volts. The power consumed by the motor was 0.054 watts. The operating time with one battery was 150 hours. The volume flow through the filter was 60 liters per hour. The total weight of the functional model is 90 grams.
Mit diesem batteriebetriebenen Miniatur-Luftkeimsammler können erstmals Langzeitmessungen durchgeführt werden. Sein geringes Gewicht (90g) läßt auch personenbezogene Messungen zu, da er problemlos am Körper getragen werden kann.With this battery operated miniature air sampler you can long-term measurements are carried out for the first time. Its minor Weight (90g) also leaves personal measurements because it can be worn easily on the body.
Die vorliegende Erfindung wird beispielsweise mittels der beiliegenden Figuren 1 bis 11 näher erläutert.The present invention is, for example, by means of enclosed Figures 1 to 11 explained in more detail.
In Figur 1 und 2 ist das Radiallaufrad gemäß der vorliegenden Erfindung in der Draufsicht dargestellt.In Figures 1 and 2, the radial impeller according to the present Invention shown in plan view.
In Figur 1 wird die Deckscheibe des Laufrades gezeigt, die aus einer flachen kreisrunden Scheibe (1) besteht, die im Zentrum eine ebenfalls kreisrunde Öffnung (2) hat. Die Scheibe hat auf einem oder mehreren Lochkreisen ( in Abhängigkeit vom Laufraddurchmesser) Bohrungen (3), die der Schaufelanzahl entsprechen.In Figure 1, the cover plate of the impeller is shown, the consists of a flat circular disc (1) which in Center also has a circular opening (2). The Disc has on one or more bolt circles (depending of the impeller diameter) holes (3) that the Correspond to the number of blades.
Das in Figur 2 dargestellte Laufrad (4) ist aus einem Stück gefräst (oder als Kunststoffspritzgussteil ausgebildet ) wobei die Schaufelhöhe (5) (siehe Querschnittdarstellung) konstant ist. Die Schaufeln (6)sind rückwärts gekrümmt. Auf den Schaufeln (6), auf einem oder mehreren Lochkreisen angeordnet, befinden sich zylindrische Noppen (7) zur Aufname der Deckscheibe (1). Die Noppen (7) werden mit der Deckscheibe (1) ultraschallverschweißt (bei Kunststoff) oder vernietet (bei Metall). Die zentrische Bohrung (8) dient zur Befestigung an der Antriebswelle.The impeller (4) shown in Figure 2 is in one piece milled (or designed as a plastic injection molded part) the bucket height (5) (see cross-sectional view) constant is. The blades (6) are curved backwards. On the Blades (6), arranged on one or more circles of holes, there are cylindrical knobs (7) for picking up the Cover plate (1). The knobs (7) are with the cover plate (1) ultrasonically welded (for plastic) or riveted (for metal). The central bore (8) is used for attachment on the drive shaft.
In Figur 2a (Ausschnitt aus Figur 2) ist der Schaufelkanal, gebildet von zwei profilierten Laufradschaufeln, sowie der Schaufeleintritts- bzw. Austrittswinkel β1 und β2 gemäß der vorliegenden Erfindung dargestellt.FIG. 2a (section from FIG. 2) shows the blade channel, formed by two profiled impeller blades, and the blade entry and exit angles β 1 and β 2 according to the present invention.
In Figur 3 ist das kommplette Radialgebläse dargestellt.In Figure 3 the complete radial fan is shown.
In Figur 4, 5, 6, 7, und 8 ist die Druckdifferenz in Abhängigkeit vom Volumenstrom, die Leistungaufnahme des Motors und der Wirkungsgrad des Gesamtsystems des Radialverdichters gemäß der vorliegenden Erfindung dargestellt.In Figure 4, 5, 6, 7, and 8, the pressure difference is dependent from the volume flow, the power consumption of the motor and the efficiency of the overall system of the radial compressor according to the present invention.
In Figur 9 zeigt das Laufrad nach Anspruch 1 und 2 der vorliegenden
Erfindung, das einen Durchmesser von 26 mm aufweist.In Figure 9 shows the impeller according to
In Figur 10 ist der Schaufelkanalquerschnitt Ak in Abhängigkeit
von der Kanallänge 1 gemäß der vorliegenden Erfindung
dargestellt.FIG. 10 shows the blade channel cross section A k as a function of the
Claims (3)
- Impeller for a radial blower, comprising a cover, a central bore for fixing to a driving shaft, a plurality of impeller blades passing in part spiral manner from the outside to the bore, characterized in that the cross-section AK of the impeller blade channel from its start to two third of its length increases and in its last third towards the circumferential edge becomes smaller or remains constant, in that the thickness of the impeller blade is given a corresponding profile-like configuration which comprises a certain thickness at the entry of air which increases up to a multiple and decreases to the exit of air onto the starting value, whereby the blade entry angle β1 having a value of 55-80°.
- Impeller according to claim 1, characterized by a total weight, including the motor of <10 g for a power consumption of 0.054 Watt.
- Use of a radial blower with an impeller according to claims 1 and 2,a) in the work protection field for collecting and measuring dust and filtering respiratory air, orb) in the medical sector in respirators and/or ventilated respiratory air protective hoods.
Priority Applications (5)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE59801139T DE59801139D1 (en) | 1998-12-18 | 1998-12-18 | Fan wheel with low specific speed |
| EP98124090A EP1013938B1 (en) | 1998-12-18 | 1998-12-18 | Low specific speed blower rotor |
| ES98124090T ES2160389T3 (en) | 1998-12-18 | 1998-12-18 | RODETE FOR RADIAL BLOWERS. |
| CA002289785A CA2289785C (en) | 1998-12-18 | 1999-11-16 | High pressure impeller with high efficiency for small volume flows for radial blowers of different size |
| US09/458,314 US6340291B1 (en) | 1998-12-18 | 1999-12-10 | High pressure impeller with high efficiency for small volume flows for radial blowers of different size |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| EP98124090A EP1013938B1 (en) | 1998-12-18 | 1998-12-18 | Low specific speed blower rotor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| EP1013938A1 EP1013938A1 (en) | 2000-06-28 |
| EP1013938B1 true EP1013938B1 (en) | 2001-08-01 |
Family
ID=8233175
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| EP98124090A Expired - Lifetime EP1013938B1 (en) | 1998-12-18 | 1998-12-18 | Low specific speed blower rotor |
Country Status (5)
| Country | Link |
|---|---|
| US (1) | US6340291B1 (en) |
| EP (1) | EP1013938B1 (en) |
| CA (1) | CA2289785C (en) |
| DE (1) | DE59801139D1 (en) |
| ES (1) | ES2160389T3 (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP2677175A1 (en) | 2012-06-19 | 2013-12-25 | Lothar Reckert | Multi-stage radial fan |
| CN104912846A (en) * | 2015-07-10 | 2015-09-16 | 珠海格力电器股份有限公司 | Draught fan impeller and blade skeleton line fitting method thereof as well as draught fan |
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| US6666660B2 (en) * | 2001-04-27 | 2003-12-23 | The Hoover Company | Motor-fan assembly for a floor cleaning machine |
| ITMI20012413A1 (en) * | 2001-11-15 | 2003-05-15 | Nuovo Pignone Spa | CENTRIFYGO COMPRESSOR IMPELLER WITH MEDIUM FLOW COEFFICIENT |
| ITMI20012414A1 (en) * | 2001-11-15 | 2003-05-15 | Nuovo Pignone Spa | BLADE FOR CENTRIFUGAL COMPRESSOR IMPELLER WITH MEDIUM-HIGH FLOW COEFFICIENT |
| JP2005042709A (en) * | 2003-07-10 | 2005-02-17 | Ebara Corp | Vacuum pump |
| US7481616B2 (en) * | 2003-08-21 | 2009-01-27 | Nidec Corporation | Centrifugal fan, cooling mechanism, and apparatus furnished with the cooling mechanism |
| US20050047943A1 (en) * | 2003-08-29 | 2005-03-03 | Jarrah Yousef M. | Compressor surge prevention via distinct blade shapes |
| CN2784587Y (en) * | 2005-04-20 | 2006-05-31 | 张兴林 | Impeller of centrifugal, mixed-flow type pump and compressor |
| US7597541B2 (en) * | 2005-07-12 | 2009-10-06 | Robert Bosch Llc | Centrifugal fan assembly |
| US7563074B2 (en) * | 2005-09-13 | 2009-07-21 | Ingersoll-Rand Company | Impeller for a centrifugal compressor |
| TWI314033B (en) * | 2007-01-23 | 2009-08-21 | Sunonwealth Electr Mach Ind Co | Mini heat dissipating module |
| FI122540B (en) * | 2007-04-20 | 2012-03-15 | Flaekt Woods Ab | Radiaalisiipipyörä |
| US8313300B2 (en) * | 2007-06-14 | 2012-11-20 | Christianson Systems, Inc. | Rotor for centrifugal compressor |
| FR2927670B1 (en) * | 2008-02-15 | 2010-03-19 | Alstom Hydro France | WHEEL FOR HYDRAULIC MACHINE, HYDRAULIC MACHINE COMPRISING SUCH A WHEEL AND ENERGY CONVERSION INSTALLATION EQUIPPED WITH SUCH A HYDRAULIC MACHINE. |
| CA2703855C (en) * | 2009-07-31 | 2018-12-11 | Rem Enterprises Inc. | Improved air vacuum pump for a particulate loader and transfer apparatus |
| US8528166B2 (en) | 2010-04-30 | 2013-09-10 | Techtronic Floor Care Technology Limited | Upright vacuum with floating head |
| US20110265285A1 (en) * | 2010-04-30 | 2011-11-03 | Morgan Charles J | Upright vacuum with reduced noise |
| WO2012094287A2 (en) * | 2011-01-05 | 2012-07-12 | Borgwarner Inc. | Impeller design for fluid pump assembly and method of making |
| US9192795B2 (en) | 2011-10-07 | 2015-11-24 | Honeywell International Inc. | System and method of calibration in a powered air purifying respirator |
| US9808656B2 (en) | 2012-01-09 | 2017-11-07 | Honeywell International Inc. | System and method of oxygen deficiency warning in a powered air purifying respirator |
| US9777743B2 (en) * | 2012-11-06 | 2017-10-03 | Asia Vital Components Co., Ltd. | Centrifugal fan impeller structure |
| US9777742B2 (en) * | 2012-11-06 | 2017-10-03 | Asia Vital Components Co., Ltd. | Centrifugal fan impeller structure |
| CN104074797B (en) * | 2013-03-25 | 2017-05-24 | 华硕电脑股份有限公司 | Impeller and fan using the same |
| KR20140125287A (en) * | 2013-04-18 | 2014-10-28 | 한라비스테온공조 주식회사 | Air blower for fuel cell vehicle |
| JP6627175B2 (en) * | 2015-03-30 | 2020-01-08 | 三菱重工コンプレッサ株式会社 | Impeller and centrifugal compressor |
| US11143195B2 (en) * | 2017-11-06 | 2021-10-12 | Isaacs Hydropermutation Technologies, Inc. | Machine and process for filterless wet removal of particles from and humidification of air |
| CN111699323B (en) * | 2018-06-11 | 2021-12-21 | 三菱重工发动机和增压器株式会社 | Rotating blade and centrifugal compressor provided with same |
| US11519421B2 (en) * | 2018-07-06 | 2022-12-06 | Zhongshan Broad-Ocean Motor Co., Ltd. | Wind wheel and blower comprising the same |
| USD907067S1 (en) * | 2018-09-12 | 2021-01-05 | Micronel Ag | Centrifugal pumps |
| USD975751S1 (en) * | 2019-10-25 | 2023-01-17 | Watson-Marlow GmbH—qonqave | Pump for liquids |
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| DE927821C (en) * | 1948-10-02 | 1955-05-16 | Demag Ag | Turbo compressor impeller |
| US2767906A (en) * | 1952-11-07 | 1956-10-23 | Doyle Vacuum Cleaner Co | Centrifugal fan wheel |
| US3788765A (en) * | 1971-11-18 | 1974-01-29 | Laval Turbine | Low specific speed compressor |
| DE3329298A1 (en) * | 1983-08-12 | 1985-02-28 | Bosch-Siemens Hausgeräte GmbH, 7000 Stuttgart | Blower for a forced-air oven |
| US4666373A (en) * | 1986-03-20 | 1987-05-19 | Eiichi Sugiura | Impeller for rotary fluid machine |
| US4944654A (en) * | 1989-05-15 | 1990-07-31 | Carrier Corporation | Split scroll for centrifugal blower |
| FR2713720B1 (en) * | 1993-12-14 | 1996-03-01 | Unir | Rotor, centrifugal air pump and air control device so equipped. |
| IL110951A0 (en) * | 1994-09-13 | 1994-11-28 | Adler Dan | Turbo machines for high pressure and low discharge |
| US5741123A (en) * | 1996-01-18 | 1998-04-21 | Pauly; Lou Allen | Turbocharger compressor fan and housing |
| US5964576A (en) * | 1996-07-26 | 1999-10-12 | Japan Servo Co., Ltd. | Impeller of centrifugal fan |
| DE19647612A1 (en) * | 1996-11-18 | 1998-05-20 | Bosch Gmbh Robert | Fan wheel |
-
1998
- 1998-12-18 DE DE59801139T patent/DE59801139D1/en not_active Expired - Lifetime
- 1998-12-18 ES ES98124090T patent/ES2160389T3/en not_active Expired - Lifetime
- 1998-12-18 EP EP98124090A patent/EP1013938B1/en not_active Expired - Lifetime
-
1999
- 1999-11-16 CA CA002289785A patent/CA2289785C/en not_active Expired - Fee Related
- 1999-12-10 US US09/458,314 patent/US6340291B1/en not_active Expired - Lifetime
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP2677175A1 (en) | 2012-06-19 | 2013-12-25 | Lothar Reckert | Multi-stage radial fan |
| CN104912846A (en) * | 2015-07-10 | 2015-09-16 | 珠海格力电器股份有限公司 | Draught fan impeller and blade skeleton line fitting method thereof as well as draught fan |
| CN104912846B (en) * | 2015-07-10 | 2017-11-17 | 珠海格力电器股份有限公司 | Draught fan impeller and its center line of blade profile approximating method, blower fan |
Also Published As
| Publication number | Publication date |
|---|---|
| CA2289785C (en) | 2008-01-22 |
| ES2160389T3 (en) | 2001-11-01 |
| CA2289785A1 (en) | 2000-06-18 |
| EP1013938A1 (en) | 2000-06-28 |
| DE59801139D1 (en) | 2001-09-06 |
| US6340291B1 (en) | 2002-01-22 |
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