EP3486494B1 - Boîtier de ventilateur radial et ventilateur radial - Google Patents

Boîtier de ventilateur radial et ventilateur radial Download PDF

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Publication number
EP3486494B1
EP3486494B1 EP18190075.4A EP18190075A EP3486494B1 EP 3486494 B1 EP3486494 B1 EP 3486494B1 EP 18190075 A EP18190075 A EP 18190075A EP 3486494 B1 EP3486494 B1 EP 3486494B1
Authority
EP
European Patent Office
Prior art keywords
centrifugal fan
fan housing
pressure compensation
section
spiral section
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP18190075.4A
Other languages
German (de)
English (en)
Other versions
EP3486494A1 (fr
Inventor
Daniel Gebert
Jens Müller
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.)
Ebm Papst Mulfingen GmbH and Co KG
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Ebm Papst Mulfingen GmbH and Co KG
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Publication of EP3486494A1 publication Critical patent/EP3486494A1/fr
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Publication of EP3486494B1 publication Critical patent/EP3486494B1/fr
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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
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/4206—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
    • F04D29/4226—Fan casings
    • F04D29/424—Double entry casings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/08—Centrifugal pumps
    • F04D17/16—Centrifugal pumps for displacing without appreciable compression
    • F04D17/162—Double suction 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
    • F04D25/16—Combinations of two or more pumps ; Producing two or more separate gas flows
    • F04D25/166—Combinations of two or more pumps ; Producing two or more separate gas flows using fans

Definitions

  • the invention relates to a radial fan housing and a radial fan with such a radial fan housing, in particular for use in extractor hoods.
  • Radial fans are known in various designs from the prior art.
  • double-flow radial fans with suction openings on two axially opposite sides their radial fan housings, are often used due to the limited space available have two housing parts for receiving a fan wheel.
  • the two fan wheels generate two air currents in the housing parts.
  • the two housing parts are brought together in the blow-out section of the radial blower, so that the two air streams are blown out together into the exhaust pipe via a single blow-out opening.
  • the inner diameter of the exhaust pipe is standardized in many countries and is usually 150mm.
  • the blow-out opening of the radial fan is designed to be correspondingly large.
  • the parallel operation of the two fan wheels with a single drive motor is realized in the prior art, for example, by an engine lock.
  • the air characteristics generated (efficiency, maximum pressure) of the individual impellers differ only slightly.
  • Another possibility for realizing the parallel operation of the fan wheels can be done, for example, by a drive motor which is arranged between the fan wheels.
  • the two individual impellers In parallel, i.e. when the wheels are connected, the situation changes significantly.
  • the two individual impellers must each reach the same pressure in parallel operation. This is also possible up to a certain pressure and volume flow, but subsequently both the efficiency and the pressure drop significantly.
  • the invention is therefore based on the object of providing a solution for radial fans with a plurality of impellers operated in parallel, in which the efficiency achieved is improved over the course of the volume flow conveyed, in particular with volume flows below the maximum efficiency of the radial fan.
  • a radial fan housing of a radial fan with a first housing part for receiving a first radial impeller and an axially directly adjacent second housing part for receiving a second radial impeller is proposed.
  • the first and the second housing part have flow spaces which run separately in a spiral spiral section of the radial fan housing and which open into one another in a blow-out section of the radial fan housing which directly adjoins the spiral section in the circumferential direction.
  • the first housing part and the second housing part are flow-connected in the spiral section via at least one pressure equalization opening to ensure pressure equalization between the housing parts.
  • the flow spaces in the spiral spiral section of the radial fan housing each form the pressure space of the individual impellers, the respective flow spaces increasing in the circumferential direction due to the spiral shape in the direction of the blow-out opening.
  • the spiral shape can extend over the entire spiral section.
  • the pressure chambers run in sections in the circumferential direction, in part with a constant, in part with a spirally increasing flow cross-sectional area.
  • the at least one pressure equalization opening in the spiral section of the radial fan housing enables pressure equalization between the Housing parts even before the individual flows of the respective impellers are brought together in the blow-out section. This results in the possibility, for example, of an impact on the ratio of the pressure difference to the volume difference (dp / dV) of one impeller that occurs due to the fluidic connection with the flow space of the other impeller, and to prevent a pressure drop and drop in efficiency at a certain volume flow .
  • a plurality of pressure equalization openings spaced apart from one another, are provided in the spiral section thereof, viewed in the circumferential direction.
  • the pressure equalization is distributed over several places, so that fluctuations occurring in the circumferential direction in the individual housing parts can be compensated for repeatedly.
  • the flow cross-sectional area of each individual pressure equalization opening can be reduced and the risk of noise formation can thus be reduced.
  • An embodiment is particularly favorable in which a plurality of pressure equalization openings are provided in the spiral section which are uniform in the circumferential direction, i.e. are arranged in the circumferential direction at an identical distance from each other.
  • the radial blower housing is characterized in that the pressure compensation openings each have an identical, in particular round, opening cross-sectional area.
  • the pressure compensation openings can be designed as bores or channels. This favors an inexpensive introduction into or attachment to the housing parts. With an identical opening cross-sectional area of the pressure compensation openings, for example in a solution with bores, the same tool can always be used economically advantageously.
  • the blow-out section is also designed in a spiral shape and forms a single blow-out opening of the radial fan housing.
  • the spiral section of the radial fan housing viewed in the circumferential direction, has an angular range of up to 280 ° and the blow-off section has an angular range of at least 80 °.
  • the blow-out section is designed to be as large as possible in order to ensure the longest possible flow path in the blow-out section of the individual flows generated by the two radial impellers.
  • the size of the pressure equalization openings also has a significant impact on the efficiency of the radial fan.
  • the one or the plurality of pressure equalization openings have a total opening cross-sectional area that determines at least 2.7% of the cross-sectional area of the blow-out opening.
  • the total opening cross-sectional area is defined as the sum of the opening cross-sectional area of all pressure equalization openings.
  • each subsection comprises at least one pressure compensation opening which forms at least 10% of the total opening cross-sectional area.
  • each subsection comprises at least one pressure compensation opening, each of which has identical opening cross-sectional areas.
  • an embodiment variant which is advantageous in terms of efficiency provides that the two subsections adjoining the blow-out section in the circumferential direction each comprise at least one pressure compensation opening, which together form at least 30% of the total opening cross-sectional area.
  • the invention also comprises a radial fan with a radial fan housing as described above in any of the variants described.
  • a radial impeller is arranged in each of the first and second housing parts, which can be driven together and are designed to generate separate air volume flows in the spiral section in the first and second housing parts in the spiral section. The separated air flows are brought together in the blow-out section and blown out of the blow-out opening. In the spiral section, the air volume flows between the first and the second housing part are flow-connected via the at least one pressure compensation opening for pressure compensation.
  • the fluidic effect is advantageous in the case of a radial fan in which the radial impellers have impeller blades which are curved forwards.
  • the radial impellers are arranged in parallel and can each be driven by the motor at an identical speed.
  • FIG 1 a double-flow radial blower 50 with a radial blower housing 1 is shown in perspective view.
  • Figure 2 shows the same radial fan 50 in a sectional view.
  • the radial fan housing 1 comprises a first housing part 2 and an axially separated second housing part 4, in each of which a radial impeller 3, 5 is accommodated with forward-curved impeller blades.
  • the radial impellers 3, 5 are simultaneously driven in parallel by the motor 12.
  • Both housing parts 2, 4 each have an axial suction opening 22, 23, through which the radial fan 50 sucks air axially.
  • the first and second housing parts 2, 4 of the radial fan housing 1 form a spiral-shaped spiral section 6, within which the separate flow spaces 8, 9 inside the housing parts 2, 4 expand radially in the circumferential direction.
  • the radial fan housing 1 comprises the blow-out section 7, in which the flow spaces 8, 9 open into one another into a single enlarged blow-out space which extends as far as the blow-out opening 11.
  • the blow-out section 7 of the radial fan housing 1 is also spiral-shaped and increases the pressure space in the blow-out section 7 in the circumferential direction even more than in the spiral section 6.
  • the sectional view according to Figure 2 runs through the spiral section 6 and shows, by way of example, two pressure compensation openings 10 in the spiral section 6, which connect the first housing part 2 and the second housing part 4 in terms of flow technology for pressure compensation and are designed as channels. After the two housing parts 2, 4 are at least locally axially spaced from one another, the channels bridge the axial distance and ensure pressure equalization between the separate housing parts 2, 4 in the spiral section 6.
  • Fig. 3 is the double-flow radial fan 50 from Figure 1 shown as a schematic side view, in which the circumferential course of the spiral section 6 and the adjoining blow-out section 7 with the blow-out opening 11 with diameter D can be seen.
  • the spiral section 6 is divided in the circumferential direction into four sub-sections 41, 42, 43, 44 of equal size, which together take up an angular range ⁇ of 280 °, the blow-out section 7 accordingly determines an angular range ⁇ of 80 °.
  • Fig. 4 shows a schematic side view of a double-flow radial fan in an embodiment according to Figure 1 , however, the two housing parts 2, 4 axially abut one another and six pressure equalization openings 10 in the form of round bores are evenly distributed in the circumferential direction over the spiral section 6.
  • each subsection 41, 42, 43, 44 comprises at least one pressure equalization opening 10. After all pressure equalization openings 10 in Figure 4 are of identical size, each of the pressure equalization openings 10 forms approximately 16.7% of the total opening cross-sectional area.
  • Figure 5 is a variant according to execution Figure 4 , in which the six pressure equalization openings 10 are provided only in the three sub-sections 41, 42, 43 which are closer to the blow-out section 7 when viewed in the direction of flow.
  • the spiral section 6 is circumferential, as in FIG Figure 3 shown, divided into four sub-sections 41, 42, 43, 44 of equal size, however, the pressure equalization openings 10 are then provided in particular in the two sub-sections 41, 42 adjoining the blow-out section 7 in the circumferential direction and are designed such that they together form at least 30% of the total opening cross-sectional area form.
  • FIG 6 is a diagram with characteristic curves for the pressure curve psf [Pa] and the efficiency nse [%] at different volume flows qv [m 3 / h] of the radial fan 50 measured in accordance with an identical test setup Fig. 1 and the same radial blower without a pressure compensation opening in the spiral section, the solid characteristics in each case according to the radial blower 50 Fig. 1 and the dashed curves each characterize the radial fan without a pressure compensation opening in the spiral section.
  • the advantageous effect of the pressure equalization between the housing parts in the spiral section on the efficiency can be clearly seen especially in the particularly important area with a volume flow of up to approx. 500 m 3 / h.

Landscapes

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

Claims (14)

  1. Boîtier de ventilateur radial (1) d'un ventilateur radial (50) ayant une première partie de boîtier (2) pour recevoir une première roue radiale (3) et une seconde partie de boîtier (4) immédiatement adjacente à celle-ci de manière axiale pour recevoir une seconde roue radiale (5), dans lequel les première et seconde parties de boîtier (2, 4) présentent des espaces d'écoulement (8, 9) s'étendant séparément dans une section en spirale (6) du boîtier de ventilateur radial (1), lesquels espaces d'écoulement, débouchent l'un dans l'autre dans une section de soufflage (7) du boîtier de ventilateur radial (1) se raccordant immédiatement à la section en spirale (6) vu dans la direction circonférentielle, dans lequel la première partie de boîtier (2) et la seconde partie de boîtier (4) sont reliées en écoulement dans la section en spirale (6) par au moins une ouverture de compensation de pression (10), dans lequel la section de soufflage (7) est conçue en forme de spirale et forme une seule ouverture de soufflage (11) du boîtier de ventilateur radial (1).
  2. Boîtier de ventilateur radial selon la revendication 1, caractérisé en ce que plusieurs ouvertures de compensation de pression (10) disposées à distance les unes des autres sont prévues dans la section en spirale (6) du boîtier de ventilateur radial (1), vu dans la direction circonférentielle.
  3. Boîtier de ventilateur radial selon l'une des revendications précédentes, caractérisé en ce que la section en spirale (6) du boîtier de ventilateur radial (1), vue dans la direction circonférentielle, a une plage angulaire jusqu'à 280 ° et la section de soufflage (7) a une plage angulaire d'au moins 80 °.
  4. Boîtier de ventilateur radial selon l'une des revendications précédentes, caractérisé en ce que plusieurs ouvertures de compensation de pression (10) sont prévues dans la section en spirale (6) et sont disposées par répartition uniforme dans la direction circonférentielle.
  5. Boîtier de ventilateur radial selon l'une des revendications précédentes 2 à 4, caractérisé en ce que les ouvertures de compensation de pression (10) présentent chacune une section transversale d'ouverture identique.
  6. Boîtier de ventilateur radial selon l'une des revendications précédentes, caractérisé en ce que la ou les ouvertures de compensation de pression (10) sont conçues comme un ou plusieurs alésages ou canaux.
  7. Boîtier de ventilateur radial selon la revendication précédente, caractérisé en ce que la ou les ouvertures de compensation de pression (10) présentent chacune une surface de section transversale ronde.
  8. Boîtier de ventilateur radial selon l'une des revendications précédentes, caractérisé en ce que la ou les ouvertures de compensation de pression (10) présentent une surface totale de section transversale d'ouverture qui détermine au moins 2,7 % d'une surface de section transversale de l'ouverture de soufflage (11).
  9. Boîtier de ventilateur radial selon la revendication précédente, caractérisé en ce que la section en spirale (6) peut être divisée dans la direction circonférentielle en quatre sous-sections de même taille (41, 42, 43, 44), dans lequel chaque sous-section (41, 42, 43, 44) comprend au moins une ouverture de compensation de pression (10), laquelle forme au moins 10 % de la surface totale de section transversale d'ouverture.
  10. Boîtier de ventilateur radial selon la revendication 8 ou 9, caractérisé en ce que la section en spirale (6) peut être divisée dans la direction circonférentielle en quatre sous-sections de même taille (41, 42, 43, 44), dans lequel chaque sous-section (41, 42, 43, 44) comprend au moins une ouverture de compensation de pression (10), chacune présentant des surfaces de section transversale d'ouverture identiques,
  11. Boîtier de ventilateur radial selon la revendication précédente, caractérisé en ce que la section en spirale (6) peut être divisée en quatre sous-sections de même taille (41, 42, 43, 44) dans la direction circonférentielle, dans lequel les deux sous-sections adjacentes (41, 42) à la section de soufflage (7) dans la direction circonférentielle comprennent chacune au moins une ouverture de compensation de pression (10), lesquelles forment ensemble au moins 30 % de la surface totale de section transversale d'ouverture.
  12. Ventilateur radial (50) doté d'un boîtier de ventilateur radial (1) selon l'une des revendications précédentes, dans lequel une roue radiale (3, 5) est disposée dans chacune de la première et la seconde partie de boîtier (2, 4), lesquelles, ensemble, peuvent être entraînées par l'intermédiaire d'un moteur (12) unique disposé de manière axialement adjacente aux roues radiales (3, 5) et sont conçues pour générer des flux de volume d'air séparés dans les première et seconde parties de boîtier (2, 4) dans la section en spirale (6), lesquels flux sont regroupés dans la section de soufflage (7) et sont soufflés hors de l'ouverture de soufflage (11), dans lequel les flux de volume d'air dans la section en spirale (6) entre la première et la seconde partie de boîtier (2, 4) sont reliées en écoulement par l'intermédiaire de l'au moins une ouverture de compensation de pression (10) pour la compensation de pression.
  13. Ventilateur radial selon la revendication précédente, caractérisé en ce que les roues radiales (3, 5) présentent des pales de roue courbées vers l'avant.
  14. Ventilateur radial selon la revendication 12 ou 13, caractérisé en ce que les roues radiales (3, 5) sont disposées en parallèle et peuvent chacune être entraînées par le moteur (12) à une vitesse identique.
EP18190075.4A 2017-11-15 2018-08-21 Boîtier de ventilateur radial et ventilateur radial Active EP3486494B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102017126912.6A DE102017126912A1 (de) 2017-11-15 2017-11-15 Radialgebläsegehäuse und Radialgebläse

Publications (2)

Publication Number Publication Date
EP3486494A1 EP3486494A1 (fr) 2019-05-22
EP3486494B1 true EP3486494B1 (fr) 2020-06-17

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ID=63350468

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Application Number Title Priority Date Filing Date
EP18190075.4A Active EP3486494B1 (fr) 2017-11-15 2018-08-21 Boîtier de ventilateur radial et ventilateur radial

Country Status (3)

Country Link
EP (1) EP3486494B1 (fr)
CN (1) CN207999390U (fr)
DE (1) DE102017126912A1 (fr)

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2710573A (en) * 1951-04-30 1955-06-14 Trade Wind Motorfans Inc Air handling apparatus
US3469772A (en) * 1967-07-19 1969-09-30 Donald A Mcdonald Air moving apparatus
US3874191A (en) * 1974-06-12 1975-04-01 Molded Products Company Blower housing
JP2001027199A (ja) * 1999-07-15 2001-01-30 Mitsubishi Heavy Ind Ltd 両吸込多翼送風装置
US9574568B2 (en) * 2011-10-20 2017-02-21 Henkel IP & Holding GmbH Double inlet centrifugal blower with a solid center plate

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

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Publication number Publication date
DE102017126912A1 (de) 2019-05-16
CN207999390U (zh) 2018-10-23
EP3486494A1 (fr) 2019-05-22

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