EP1589229A1 - Ventilateur - Google Patents

Ventilateur Download PDF

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Publication number
EP1589229A1
EP1589229A1 EP05006644A EP05006644A EP1589229A1 EP 1589229 A1 EP1589229 A1 EP 1589229A1 EP 05006644 A EP05006644 A EP 05006644A EP 05006644 A EP05006644 A EP 05006644A EP 1589229 A1 EP1589229 A1 EP 1589229A1
Authority
EP
European Patent Office
Prior art keywords
region
rotation
conveying
blower
channel
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.)
Granted
Application number
EP05006644A
Other languages
German (de)
English (en)
Other versions
EP1589229B1 (fr
Inventor
Arne Fischer
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.)
Eberspaecher Climate Control Systems GmbH and Co KG
Original Assignee
J Eberspaecher GmbH and Co KG
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
Application filed by J Eberspaecher GmbH and Co KG filed Critical J Eberspaecher GmbH and Co KG
Publication of EP1589229A1 publication Critical patent/EP1589229A1/fr
Application granted granted Critical
Publication of EP1589229B1 publication Critical patent/EP1589229B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F04D23/00—Other rotary non-positive-displacement pumps
    • F04D23/008—Regenerative pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/08—Sealings
    • F04D29/16—Sealings between pressure and suction sides
    • F04D29/161—Sealings between pressure and suction sides especially adapted for elastic fluid pumps

Definitions

  • the present invention relates to a fan, in particular combustion air blower for a heater comprising a blower housing, one formed in the blower housing, about a rotation axis ring-like extending and open on one axial side conveyor channel, a Conveyor, which on the fan housing the delivery channel at its axial overlapping open side and is rotatably supported about the rotation axis and a plurality of circumferentially successive ones Conveying blades which, upon rotation of the impeller in a Move the direction of rotation above the conveyor channel, and an inlet area to the entry of air to be conveyed in the delivery channel.
  • Such generally also as a side channel fan designating blower are preferably used to drive in vehicle heaters, such.
  • the air to be conveyed in the conveyor channel in a helical Staggered flow wherein during movement along the conveying channel of the inlet region to one in the flow direction or rotation direction the delivery wheel before the interruption area lying exit area a gradual increase in pressure occurs.
  • Part of the in the circumferential direction funded air volume is not in the exit area by a Outlet exit through and, for example, towards one Boosted combustion chamber, but remains trapped in the between formed two circumferentially successive conveyor blades Volumes.
  • conveying blades or Conveyor wheel on the one hand and interruption area on the other hand so on each other are tuned to avoid pressure loss between the inlet area and the outlet area with the conveyor blades the smallest possible distance over the substantially planar surface of the Crossing the interruption area, leaving a near-perfect finish the addressed volumes occurs.
  • these volumes is enclosed the air with the pressure prevailing at the exit area, which is significantly higher than the prevailing at the inlet pressure. If such a volume moves over the interruption area away and sweeps over in the direction of rotation ahead, the Volume limiting bucket the circumferential end of the interruption area, so opens up such a volume with the inside pressurized gas toward the entrance area.
  • a fan in particular Combustion air blower for a vehicle heater, with the aforementioned Design in such a way that an improved performance can be achieved.
  • a blower in particular A combustion air blower for a vehicle heater, comprising Blower housing, one formed in the blower housing to a Axis of rotation extending in a ring-like manner and open on one axial side Delivery channel, a feed wheel, which on the fan housing the delivery channel overlapping on its axially open side and about the axis of rotation is rotatably supported and a plurality of each other in the circumferential direction Having the following conveying blades, which upon rotation of the feed wheel moving in a rotational direction over the conveyor channel, an entrance area for the entry of air to be conveyed into the delivery channel, in the direction of rotation lying in front of the entrance area an interruption area, in which the conveying channel is interrupted in the circumferential direction, wherein a lying in the direction of rotation before the inlet region Peripheral end of the interruption area with a radially outer Section in the direction of rotation in front of a radially inner and / or radial middle section lies.
  • the codessend Scheme the interruption area with curved Contour is formed.
  • Another increase in efficiency the blower according to the invention by more efficient design of the air flow in the delivery channel can be achieved by that in the entry area an inlet opening is provided with respect to a radial dimension, So radial width, the conveying channel smaller radial dimension and that a radially inner end portion of the entrance opening in or near a radially inner end portion of the conveying channel is located. It is preferable further provided that a circumferential dimension of the inlet opening is greater than a radial dimension thereof.
  • the circumferential end of the interruption area in the circumferential direction, the inlet opening substantially not covered.
  • the at least the circumferential distance between two Conveying blades should also be necessary or advantageous, when the circumferential end portion of the interrupting portion is in the rotational direction Covered front end of the inlet opening.
  • the entry of air in the inlet area As little as possible, it is further suggested that at the perennialsend Scheme the interruption area in the Conveying channel entering air approximately in the direction of rotation deflecting Guiding surface is formed.
  • the guide surface can be curved be.
  • a blower in particular combustion air blower for a vehicle heater
  • a blower housing one formed in the fan housing, about an axis of rotation extending in a ring-like manner and open on one axial side Delivery channel
  • a feed wheel which on the fan housing the delivery channel overlapping on its axially open side and about the axis of rotation is rotatably supported and a plurality of each other in the circumferential direction Having the following conveying blades, which upon rotation of the feed wheel moving in a rotational direction over the conveyor channel, an entrance area for the entry of air to be conveyed into the delivery channel, in the direction of rotation lying in front of the entrance area an interruption area, in which the conveying channel is interrupted in the circumferential direction, wherein the Conveyor blades and a circumferential direction in front of the inlet area lying circumferential end of the interruption area to each other in such a way are tuned that when moving in the direction of rotation the Conveyor
  • a blower in particular combustion air blower for a vehicle heater, comprising a fan housing, one in the fan housing trained to ring-like around a rotation axis and on an axial side open conveying channel, a conveying wheel, which on the Blower housing covering the delivery channel at its axially open side and is rotatably supported about the rotation axis and a plurality of in Circumferential direction comprises successive conveyor blades, which upon rotation of the feed wheel in a rotational direction above the Moving conveyor channel, an inlet area for the entry of promotional Air in the conveying channel, lying in the rotational direction in front of the inlet area an interruption area in which the delivery channel in Circumferential direction is interrupted, wherein a peripheral end of the Interruption area and provided on the conveyor wheel Conveyor blades are coordinated so that upon rotation of the Conveyor wheel a respective between two in the circumferential direction immediately After successive conveyor blades formed volume after Passing the interruption area first at the
  • FIGs. 1 and 3 is a first embodiment variant of an inventive Blower 10 shown.
  • This blower 10 comprises a generally 12th designated fan housing, in which a circular about an axis of rotation A. extending delivery channel 14 is formed. How to look in particular recognizes in Fig. 3, this conveyor channel 14 is on one axial side 16 of the housing 12 open and thus has in its substantial circumferential extent a semicircular cross-sectional geometry.
  • a conveyor wheel 18 is opposite.
  • This feed wheel 18 is in Essentially designed annular or circular disk-like and carries in his radially outer region, with one of the geometry of the delivery channel 14th corresponding geometry is configured, a plurality of circumferentially Radial on the inside is the Conveyor 18 on a shaft 22 of a drive motor 24, for example carried by an electric motor, so that upon energization of the electric motor 24th the feed wheel 18 in the illustration of FIG. 1 in the direction of rotation R will turn.
  • the delivery channel 14 has an inlet region 26, in which an inlet opening 28 is formed. Through this inlet opening 28, as indicated by an arrow P 1 in FIG. 3, the air to be delivered and compressed can enter.
  • the inlet opening 28 is designed in such a way that it has a radial extension which is smaller than the radial extent of the conveying channel 14. Furthermore, the inlet opening 28 is designed with a circumferential extension which is longer than its radial extent, so that the in Fig. 1 recognizable, circumferentially elongated configuration results. Further, the inlet opening 28 is positioned in the conveying channel 14 in the radial direction so that its radially inner end portion 30 is located near the radially inner end portion 32 of the conveying channel 14. In the variant shown in FIGS.
  • the radially inner end region 30 of the inlet opening 28 has a slight distance from the radially inner end region 32 of the conveying channel 14. This is due to the fact that here an electric motor 24 is used, whose outer diameter is slightly larger than the minimum inner diameter of the conveying channel 14. This, too, can be clearly seen in FIG.
  • the geometry or positioning of the inlet opening 28 is thus predetermined so that the electric motor 24 substantially covers no areas of the inlet opening 28 and thus the air to be guided into the delivery channel 14 along the outer peripheral region of the electric motor 24 and through the inlet opening 28 in the delivery channel 14 can flow.
  • the passing through the inlet opening 28 in the conveying channel 14 air is by the circumferential movement of the conveyor blades 20 for movement in the circumferential direction taken along, so can basically in the delivery channel 14th move in the direction of rotation R.
  • the pressure of the extracted air decreases until it finally reaches an exit area 34.
  • the exit area 34 is from inlet region 26 through a generally designated 36 Break area separated. This interruption area one is substantially flush with the axial side 16 of the housing 12 final surface 38 ready to receive the conveyor 20 in the Sweep conveyor wheel 18 with a small axial distance. In this manner and way, a pressure loss between the inlet region 26 and the Exit region 34 largely prevented. From the exit region 34 leads below the addressed surface 38 of the interruption area 36 passing through an outlet opening 40 away to those in the exit region 34th arrived, now under increased pressure air to one with such Air to be supplied system, so for example the burner one Heating device, to promote.
  • a circumferential end region 42 of the interruption region 40 located in front of the entrance region 26 is shaped such that a radially outer section 44 thereof projects in the direction of rotation R. a radially central portion 46 and also a radially inner portion 48 lies.
  • the radially outer portion 44 has a greater distance, in opposite to the direction of rotation R, as the radially middle portion 46 and of course also the radially inner portion 48.
  • the processorsend Scheme 42 has a sickle-like, convexly curved contour.
  • this helical flow now supports the air flowing radially outward from the volumes initially enclosed above the interruption region 36.
  • the efficiency of the delivery and the pressure build-up can additionally be increased by the inventive design of the interruption region 36.
  • a smaller sized blower can be used, that with lower speed of the feed wheel 18 and thus lower energy consumption can be used and that, moreover, in addition to an increase in the entire service life and the noise level can be reduced.
  • defined operating points defined in terms of pressure and volume
  • the entrance opening 28 as shown in Fig. 1 dimensioned and positioned is 22 mm, the corresponding radial width of Inlet opening 28 in the range of between 7 and 10 mm, preferably 7.5 and 9 mm.
  • an outer diameter of the delivery channel 14 of 75 mm are assumed. That is, that Ratio of the radial width of the conveying channel 14 to the radial width of Inlet opening 28 is preferably in a range of 2 to 3.
  • the circumferential extent of the inlet opening 28 in an angular range of 55 ° to 65 ° to choose.
  • the circumferential end region 42 of the interruption region 36 is positioned so that it is in the circumferential direction, d. H. Rotation direction R, the inlet opening 28 practically not covered. Consequently can the inlet opening 28 with its entire opening cross-section 28 efficiently be used for air introduction. It can, however, be constructed Be necessary reasons that in the circumferential direction, the inlet opening 28th and the interruption area 36 must move closer together. These Situation is shown in Fig. 2. Here you can see that the radially inner section 48 of the peripheral end portion 22 at least the radially inner portion of the Inlet opening 28 in a lying in the direction of rotation R front End area 50 of the same covered. In the illustrated in Figs.
  • the inlet opening 28 in its entrance area is formed with a nozzle-like inlet surface 52, so that in turn an overall improvement of the flow conditions can be achieved which is so obvious in the case of the variant shown in Figs. 1 and 3 Case can be.
  • inlet opening 28 and interruption area 36 are required to an even greater extent, a variant shown in FIG. 5 and in FIG. 6 can be selected.
  • the end region 50 of the inlet opening 28 is relatively strongly covered, so that the central section 46 of the circumferential end region 42 also covers the inlet opening 50.
  • the interruption region 36 can be formed in its circumferential end region 42 with a guide surface 54 which can be seen in FIG.
  • convex curved guide surface 54 ensures that the newly introduced into the region of the conveying channel 14 air flow P 1 is deflected in the circumferential direction and thus approximately in the direction of rotation R. The occurrence of unwanted turbulence in this inlet region 26 can thus be largely avoided.
  • This curved in a radial view or inclined guide surface 54 may at the interruption region 36 over the entire radial extent the same can be configured, but can also be present only there, where the interruption area 36 the inlet opening 28 in the circumferential direction covered.
  • Such geometry also in the in FIGS. 2 and 4 are shown.
  • the interruption region 36 were configured with a peripheral end region 42 which ends with the imaginary radial line L R , then it could also be achieved that the initially trapped volumes are only opened radially outward and this opening then increases successively and also expands radially inward becomes.
  • the conveying blades can also be combined with the geometry of the peripheral end region 42 shown in FIGS. 1 to 6.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP05006644A 2004-04-23 2005-03-24 Ventilateur Not-in-force EP1589229B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102004019868A DE102004019868A1 (de) 2004-04-23 2004-04-23 Gebläse, insbesondere Verbrennungsluftgebläse für ein Heizgerät
DE102004019868 2004-04-23

Publications (2)

Publication Number Publication Date
EP1589229A1 true EP1589229A1 (fr) 2005-10-26
EP1589229B1 EP1589229B1 (fr) 2009-05-20

Family

ID=34934530

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05006644A Not-in-force EP1589229B1 (fr) 2004-04-23 2005-03-24 Ventilateur

Country Status (2)

Country Link
EP (1) EP1589229B1 (fr)
DE (2) DE102004019868A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110397627A (zh) * 2019-07-22 2019-11-01 浙江泰福泵业股份有限公司 水泵进水结构

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008056105B4 (de) 2008-11-06 2011-02-03 Pierburg Gmbh Seitenkanalgebläse, insbesondere Sekundärluftgebläse für eine Verbrennungskraftmaschine
DE102021005466A1 (de) 2021-11-04 2023-05-04 Truma Gerätetechnik GmbH & Co. KG Vorrichtung zum Erhitzen einer Flüssigkeit und/oder zum Erwärmen von Luft sowie Seitenkanalgebläse

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE902074C (de) * 1937-08-08 1954-01-18 Fritz Oesterlen Dr Ing Umlaufverdichter mit einem gleichachsig zum Laufrad gelegenen Seitenkanal
US3951567A (en) * 1971-12-18 1976-04-20 Ulrich Rohs Side channel compressor
EP0586934A1 (fr) * 1992-09-08 1994-03-16 Firma J. Eberspächer Soufflante à canal latéral avec génération de bruit reduit
DE4424629C1 (de) * 1994-07-13 1995-03-09 Becker Kg Gebr Seitenkanalverdichter
DE19818667A1 (de) * 1998-04-27 1999-10-28 Becker Kg Gebr Kreiselverdichter

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2258737A1 (de) * 1972-11-30 1974-06-06 Elektror Karl W Mueller Elektr Seitenkanalverdichter
DE3822267A1 (de) * 1988-03-06 1989-12-07 Webasto Ag Fahrzeugtechnik Ringkanalgeblaese
DE3906852A1 (de) * 1989-03-03 1990-09-06 Webasto Ag Fahrzeugtechnik Ringkanalgeblaese
DE19906515C1 (de) * 1999-02-17 2000-02-03 Webasto Thermosysteme Gmbh Seitenkanalgebläse

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE902074C (de) * 1937-08-08 1954-01-18 Fritz Oesterlen Dr Ing Umlaufverdichter mit einem gleichachsig zum Laufrad gelegenen Seitenkanal
US3951567A (en) * 1971-12-18 1976-04-20 Ulrich Rohs Side channel compressor
EP0586934A1 (fr) * 1992-09-08 1994-03-16 Firma J. Eberspächer Soufflante à canal latéral avec génération de bruit reduit
DE4424629C1 (de) * 1994-07-13 1995-03-09 Becker Kg Gebr Seitenkanalverdichter
DE19818667A1 (de) * 1998-04-27 1999-10-28 Becker Kg Gebr Kreiselverdichter

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110397627A (zh) * 2019-07-22 2019-11-01 浙江泰福泵业股份有限公司 水泵进水结构
CN110397627B (zh) * 2019-07-22 2024-03-26 浙江泰福泵业股份有限公司 水泵进水结构

Also Published As

Publication number Publication date
EP1589229B1 (fr) 2009-05-20
DE102004019868A1 (de) 2005-11-24
DE502005007301D1 (de) 2009-07-02

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