EP0178645A1 - Ventilateur transversal pour le transport de gaz - Google Patents

Ventilateur transversal pour le transport de gaz Download PDF

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Publication number
EP0178645A1
EP0178645A1 EP85113116A EP85113116A EP0178645A1 EP 0178645 A1 EP0178645 A1 EP 0178645A1 EP 85113116 A EP85113116 A EP 85113116A EP 85113116 A EP85113116 A EP 85113116A EP 0178645 A1 EP0178645 A1 EP 0178645A1
Authority
EP
European Patent Office
Prior art keywords
impeller
conveying
housing
cross
flow fan
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
EP85113116A
Other languages
German (de)
English (en)
Other versions
EP0178645B1 (fr
Inventor
Rolf Dipl.-Ing. Fichter
Karl Schips
Gerd-Eugen Dr. Ing. Schaal
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.)
LTG Lufttechnische GmbH
Original Assignee
LTG Lufttechnische GmbH
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 LTG Lufttechnische GmbH filed Critical LTG Lufttechnische GmbH
Priority to AT85113116T priority Critical patent/ATE42613T1/de
Publication of EP0178645A1 publication Critical patent/EP0178645A1/fr
Application granted granted Critical
Publication of EP0178645B1 publication Critical patent/EP0178645B1/fr
Expired 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
    • F04D29/08—Sealings
    • F04D29/16—Sealings between pressure and suction sides
    • F04D29/161—Sealings between pressure and suction sides especially adapted for elastic fluid pumps
    • F04D29/162—Sealings between pressure and suction sides especially adapted for elastic fluid pumps of a centrifugal flow wheel
    • 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
    • F04D17/02—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps having non-centrifugal stages, e.g. centripetal
    • F04D17/04—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps having non-centrifugal stages, e.g. centripetal of transverse-flow type
    • 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

Definitions

  • the invention relates to a cross-flow fan according to the preamble of claim 1.
  • the impeller of the cross-flow fan is always understood to mean the impeller without the drive shaft and without the bearing journal.
  • the conveying gas is understood to be the gas for the conveyance of which the cross-flow fan is used in each case and which is not cooling air which is used only for cooling.
  • the impeller diameter is also understood to mean the diameter of the outer circle of rotation of the blades of the impeller in its conveying region serving to convey conveying gas.
  • a cross-flow fan 10 which is obviously marketed by the applicant in the Federal Republic of Germany, of the type mentioned in the preamble of claim 1 is shown in broken and partially longitudinal section in FIG. It has a metallic housing 11, which has a central region 12, in which the impeller 14, which has mutually parallel blades 13, is located.
  • This middle area 12 has a suction opening 16 extending approximately over the axial length of the impeller 14 extending from the end face 15 to the end face 15 'and a blowout opening 17 for the conveying gas also extending over the axial length of the impeller.
  • These metallic end ring disks 15, 15 'of the impeller 14 are located at the level of the axial ends 19, 20, 21, 22 of the suction opening 16 and the blow-out opening 17.
  • the metallic drive shaft 23 of the impeller engaging on the end face disc 15 is long and in two parts. It consists of a relatively large diameter hollow shaft 24 directly attached to the end face 15 and the rotor shaft 25 of the electric drive motor 26 inserted into the bore of this hollow shaft 24.
  • This motor 26, which drives the impeller 14, is on the outside of the housing 11 coaxial with the axis of rotation the impeller 14 attached.
  • the impeller 14 is rotatably supported by means of a long two-part shaft 27, which consists of a thick shaft piece 27 'which is attached directly to the end face disk 15' and a shaft piece 27 '' of smaller diameter inserted into a bore of the latter.
  • the bearings for the drive shaft 23 are by the bearings in the motor 26 for the rotor shaft 25 and the bearing for the shaft 27 by means of metal disks and radial rubber spokes 31 elastically suspended and lubricated by lubricant-impregnated felt disks 29, located on the left end of the housing 11, the plain bearing bush 30, which supports the shaft piece 27 ".
  • This cross-flow fan 10 can be used to convey hot gases as well as very cold gases, the temperatures of which, however, are too extreme for the bearing points of the impeller as well as for the drive motor, since at these temperatures the bearing points would overheat or become stiff and the drive motor would also suffer damage could.
  • the drive shaft 23 is extended by the hollow shaft 24, likewise the shaft piece 27 "by the shaft piece 27 'and in addition the heat-insulating disks 33 are immovably arranged in the housing bulges 32, 32'.
  • These parts 24, 27 'and 33 thus form heat protection means for the bearing points and the motor 26.
  • the hollow shaft 24 as well as the shaft piece 27' must be made relatively thick and made of metal and they therefore conduct the high or low temperatures of the pumped gas still relatively good through the heat insulation washers 33 to the bearings and the drive motor 26.
  • the impeller is extended axially into the pot-shaped bulges of the housing beyond its conveying region, which is used only for conveying the conveying gas, and the drive shaft and the bearing journal on the free ends of the extension attack areas and ends, there are no more shafts penetrating the pot-shaped bulges over their full axial lengths. It is therefore possible and advantageous to have the rotatably mounted rotor shaft of the drive motor act directly on the axial end of the relevant wheel extension region. Likewise, only a one-piece, short, preferably circular-cylindrical bearing journal is required for the rotary mounting of the end face of the impeller facing away from the drive shaft, which engages on the axial end of the relevant impeller extension region.
  • the bearing journal can expediently be designed as a short, relatively thin shaft which is fixedly arranged on this impeller end face and is rotatably mounted in a slide bearing bush arranged on the relevant housing end wall or by means of a roller bearing.
  • a bearing journal on the relevant front end of the housing and to mount it rotatably in a slide bearing bush or by means of a roller bearing which is arranged on the relevant front end of the impeller.
  • the invention also makes it possible for the housing of the cross-flow fan according to the invention to correspond to that of the cross-flow fan 10 shown in FIG. 1 or to require only minor changes which cause only low costs.
  • All other parts of the impeller can also consist of metal, in particular aluminum, and yet there is very good thermal insulation.
  • a cross-flow fan 40 according to FIG. 2 which is designed according to an exemplary embodiment of the invention and has been tried and tested, good thermal protection was obtained even if the conveying area of the impeller from its two extension areas was not through gas-tight intermediate disks but through central holes of approx .3cm diameter intermediate washers made of aluminum was separated from about 9an outer diameter.
  • extension areas of the impeller resulted in surprisingly good thermal protection, which is due to the fact that the extension areas do not serve to convey the conveying gas and also to the gas located in the extension areas and the arrangement of the drive shaft or the bearing journal directly at the axial ends of the impeller extension areas located in the cup-shaped bulges, so that the drive shaft and the bearing journal had correspondingly large distances from the impeller delivery area. It may also play a role in this that gases located in the pot-shaped bulges of the housing are caused to circulate by the impeller extension areas. It is also advantageous if the cup-shaped bulges of the housing consist of metal.
  • the heat protection can be further improved if it is provided that the conveying area of the impeller is separated from the two impeller extension areas on at least one side, preferably on both sides by a completely or essentially gas-impermeable intermediate disk or by completely or essentially gas-impermeable intermediate disks.
  • a labyrinth seal is arranged at least at a transition from the impeller conveying region to an impeller extension region on the circumference of the impeller. If the impeller conveying area is sealed off from the interior of the cup-shaped bulges of the housing both by means of such labyrinth seals and also by means of completely or essentially gas-impermeable intermediate disks, particularly good heat protection results.
  • the heat protection can also be further improved in a simple manner by arranging heat-insulating means, preferably a heat-insulating disk, in at least one extension area of the impeller.
  • heat insulation means are also possible, for example inserting heat-insulating pads, for example. made of glass fibers or the like, in at least one extension area of the impeller.
  • an end section of at least one impeller extension area can convey cooling air through an end chamber of the pot-shaped housing bulge in question and that this end section of the impeller extension area is separated from the conveying area of the impeller by the remaining section of this impeller extension area.
  • This cooling air is therefore not a conveying gas in the sense of the definition of the conveying gas given above.
  • the blades and disks of the impeller can be made of metal, preferably aluminum.
  • M ATE rial product that was insulated or has poor thermal conductivity, such as plastic or the like. By the latter measures the thermal protection can also be further improved.
  • At least one of the two impeller extension regions extends over at least half, preferably over at least 3/4 of the axial length of the cup-shaped housing bulge.
  • the cross-flow fan 40 shown in FIG. 2 has a preferably metallic housing 41 similar to the housing 11 of the cross-flow fan 10 according to FIG. 1, which has a central area 44 with a suction opening 42 and a blow-out opening 43 for the entire conveying gas.
  • This central region 44 over the axial length of which the blow-out opening 43 and the suction opening 42 extend, is laterally connected by cup-shaped, substantially circular-cylindrical bulges 45, 45 ′ of the housing 41.
  • the impeller 46 extends with extension areas 48, 48 'on both sides far into the cup-shaped bulges 45, 45', so that its two axial ends 49, 49 ', as shown, are only relatively small Distances from the approximately flat, thin-walled end faces 47, 47 'of these cup-shaped bulges 45, 45', which distances are somewhat less than 1/4 of the axial length of the bulges 45 and 45 'in question. Because of the thin walls of the end faces 47, 47 ', the axial length of the bulges 48, 48' can practically be equated with the axial length of their interior spaces.
  • the diameters of the extension areas 48, 48 ' are only slightly smaller, preferably only about 2 to 6 mm smaller than the inner diameter of the bulges 45, 45 ', which causes or contributes to the fact that these extension regions 48, 48' do not participate in the conveyance of the conveying gas flowing in through the inlet opening 44.
  • the blades 50 of the impeller 46 which are preferably made of aluminum, in this exemplary embodiment expediently extend over the full length of the impeller 46, that is to say from the front end 49 to the front end 49 'of the impeller 46, where they are in thin end ring disks 51, 51' of the impeller 46 , which can also be made of metal.
  • the only the conveying of the production gas through the housing 41 serving conveyor area 52 of the impeller 46 extends in the axial direction from a metallic washer 53 to a metallic washer 53 '.
  • These two intermediate plates 53, 53 'of the impeller 46, which are penetrated by the blades 50, are located approximately at the level of the lateral ends 54, 55, 56, 57 of the two intake and exhaust openings 42, 43 which serve solely for the inlet and outlet of the entire conveying gas Housing 41.
  • These intermediate disks 53, 53 ' can be disks that have no air passage openings, or also ring disks, each of which has a small central opening of preferably max. about 3 cm in diameter, which openings serve to center or clamp these disks when assembled on a mandrel.
  • An elastic ring 58 made of steel, silicone rubber or the like is inserted into a central opening of the right-hand end ring disk 51, into which a rigid hub 59 is inserted, into which the rotor shaft 60 of the electric drive motor 61 fastened to the outside of the housing end wall 47 is firmly inserted , so that the bearings in the motor 61 for the shaft 60 support the impeller 46 on the right side.
  • the shaft 60 thus ends, as shown, at the outer axial end of the impeller extension region 48 formed by the hub 59.
  • a hub 62 is inserted in the end ring disk 51 'thereof, into which a bearing pin 64 in the form of a short cylindrical shaft is inserted in a rotationally fixed manner.
  • the bearing journal 64 thus ends, as shown, at the outer axial end of the impeller extension region 48 ′ formed by the hub 62.
  • This journal 64 protrudes to its rotary bearing in a metallic sliding-bearing bushing 65 in which at the left end wall 47 'of the housing 41 by metal discs 89 (see ig F. 3) and radial elastic spokes 63 or is resiliently mounted in its place by means of a resilient washer.
  • the elastic suspension of the impeller 46 by the members 58, 63 improves, among other things, its smoothness.
  • the plain bearing bush 65 is still surrounded by lubricant-soaked felt rings 68 for their lubrication.
  • the left extension area 48 'of the impeller 46 is located entirely within the cup-shaped bulge 45' and extends almost over its axial length. It begins at the intermediate disk 53 'separating it from the conveying area 52 and extends to the left end 49' of the impeller.
  • the right extension region 48 of the impeller 46 is located completely in the right-hand cup-shaped bulge 45 of the housing 41 and begins at the intermediate disk 53 and extends to the right-hand end 49 of the impeller 46.
  • these two impeller extension areas 48, 48 ' circulate the gases located in these cup-shaped bulges 45, 45', which are normally air, but do not convey these gases through the housing. It is therefore a question of gases located in the lateral cup-shaped bulges 45, 45 'which, due to their poor thermal conductivity or nonexistent thermal conductivity, have a very good thermal insulation effect.
  • the cross-flow fan can preferably convey Serve air.
  • Luft. is a good thermal insulator in the bulges 45, 45 '.
  • the depth, ie the interior depth or the approximately equal axial length of each of the bulges 45, 45 ' can expediently be at least 0.1 times, preferably at least 0.3 times the impeller diameter.
  • each of the bulges 45, 45 'can particularly advantageously be at least 0.5 times, particularly advantageously approximately 0.6 to 1.2 times the impeller diameter.
  • the cross-flow fan is used or designed, the greater the depth or axial length of the bulges 45, 45 'can be.
  • the intermediate disks 53, 53 ' had an outer diameter of approximately 9 cm in the center of circular openings of approximately 3 cm in diameter, so that communication between the hot gas flowing through the conveying region 52 and the gases in the two cup-shaped bulges was to a certain extent Extent can take place, and in addition also through the narrow annular gaps between the two washers 53, 53 'and the cup-shaped housing bulges 45, 45'.
  • the Not right-hand heat protection areas shown can be approximately designed to correspond to the left-hand heat protection areas.
  • the cross-flow fans according to these exemplary embodiments of FIGS. 3-5 can correspond to the cross-flow fan 40 according to FIG. 2, with the exception of the differences explained below which only concern the heat protection means.
  • the intermediate disk 53 'of the impeller 46 delimited on the left side by the conveying area 52 of the cross-flow fan is a gas-impermeable disk, which therefore has no air passage openings .
  • a labyrinth seal 74 is also provided which encompasses the circumference of the impeller 46 at the transition region from the conveying region 52 to the relevant extension region 48 'of the impeller 46, which, in addition to the outer circumferential region of the intermediate disk 53', also through the outer circumferential region of one arranged close to it formed as a gas-impermeable washer 75 and formed by arranged on the inner periphery of the housing 41 washers 76, one washer 76 engages in the space between the two washers 53 ', 75 and the other washer 76 is arranged on the left side of the washer 75 near it .
  • a corresponding labyrinth seal cannot As shown, the other transition area between the conveying area 52 of the cross-flow fan and the pot-shaped bulge on the right-hand side of the housing can also be provided accordingly.
  • a further gas-impermeable washer 77 is also inserted, namely at approximately equal axial distances from the washer 75 and the end ring washer 51'. This further intermediate disc '77 improves the heat insulating effect of the 45 in this pot-shaped bulge' gas contained by additional axial restraining further.
  • the left-hand end ring disk 51 ' together with the hub 62 inserted into it and the bearing pins 64 firmly inserted therein, forms an airtight seal for the left front end 49' of the impeller 46.
  • the right-hand end end of the impeller 46 can also be sealed accordingly and in the right-hand side Extension region of the impeller 46 can also be used at least one washer such as the washer 77.
  • FIG. 4 shows a variant of the section of a cross-flow fan shown in FIG. 3, which differs from the embodiment according to FIG. 3 in that the space between the two intermediate disks 75, 77 located within the blade ring of the impeller 46 is made of a heat insulation material 79 is filled out.
  • This can be heat-insulating, high-temperature-resistant plastic, a glass fiber cushion or the like. This further improves thermal protection.
  • a corresponding measure can of course also be provided in the extension region of the impeller 46 on the right, not shown. Otherwise, this cross-flow fan according to FIG. 4 corresponds to that according to FIG. 3.
  • FIG. 5 shows a variant of the section of the cross-flow fan according to FIG. 4.
  • the interior of the cup-shaped bulge 45 ' is divided by additional sealing rings 80, 81 on the housing and on the impeller, as shown, into two chambers 82, 83, which are essentially sealed off from one another and are arranged axially one behind the other, of which the left end Cooling air can flow through chamber 83, which is conveyed by the section 50 ′ of the blade ring of the impeller 46 located in this chamber, in that this section 50 ′ sucks in cooling air like a radial impeller and conveys it radially outward, thereby providing additional heat protection for the left-hand plain bearing bush 65 shown is effected.
  • a corresponding air cooling can also be provided in the other cup-shaped housing bulge on the right-hand side.
  • the cooling air described is not a conveying gas in the sense of the invention, since it only serves to cool the fan and is not the conveying gas to be conveyed by the fan from the suction opening 42 to the exhaust opening 43.
  • the end regions of the blades 50 which project beyond the sealing disc 81 to the left, are used to convey the cooling air, since large segment-shaped air inlet openings 87 are present in the left end ring disc 51 ', through which these blade end regions suck air through cooling air inlet openings 85 provided in the housing end wall. This cooling air is blown out radially through circumferential air outlet slots 86 of the chamber 83 of the housing 41.
  • the pot-shaped bulges 45, 45 'need not have any ventilation openings, but ventilation openings can often also be expediently provided, preferably in the end walls of the housing 41.
  • the drive of the impeller 46 is formed by the motor 61.
  • other drives are also possible, for example a belt drive or the like.
  • the drive shaft which is connected in a rotationally fixed manner to the impeller 46 can correspond to the shaft 60 with the difference that it does not carry the rotor shaft but a drive shaft carrying a belt pulley of the belt drive for the impeller 46.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Rigid Pipes And Flexible Pipes (AREA)
  • Feeding, Discharge, Calcimining, Fusing, And Gas-Generation Devices (AREA)
EP85113116A 1984-10-17 1985-10-16 Ventilateur transversal pour le transport de gaz Expired EP0178645B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT85113116T ATE42613T1 (de) 1984-10-17 1985-10-16 Querstromventilator zum foerdern von foerdergas.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19843438039 DE3438039A1 (de) 1984-10-17 1984-10-17 Querstromventilator zum foerdern von foerdergas
DE3438039 1984-10-17

Publications (2)

Publication Number Publication Date
EP0178645A1 true EP0178645A1 (fr) 1986-04-23
EP0178645B1 EP0178645B1 (fr) 1989-04-26

Family

ID=6248104

Family Applications (1)

Application Number Title Priority Date Filing Date
EP85113116A Expired EP0178645B1 (fr) 1984-10-17 1985-10-16 Ventilateur transversal pour le transport de gaz

Country Status (3)

Country Link
EP (1) EP0178645B1 (fr)
AT (1) ATE42613T1 (fr)
DE (2) DE3438039A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0643226A1 (fr) * 1993-08-30 1995-03-15 Ltg Lufttechnische Gmbh Ventilateur traversal insérable
DE4412836A1 (de) * 1994-04-14 1995-10-19 Ltg Lufttechnische Gmbh Querstromventilator mit elastischer Kupplung
US20150024675A1 (en) * 2007-03-07 2015-01-22 Sine Kon Hu Airflow Boosting Assembly for a Forced Air Circulation and Delivery System

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1374975A (fr) * 1962-05-30 1964-10-16 Ventilateur d'appartement ou analogue
DE2126832A1 (de) * 1971-05-29 1972-12-14 Hanning Elektro Werke Querstromgebläse mit motorisch angetriebener Lüfterwalze
DE2602933A1 (de) * 1975-01-28 1976-07-29 Nissan Motor Vorrichtung zur fluidfoerderung mit waermeaustauschereigenschaft

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1374975A (fr) * 1962-05-30 1964-10-16 Ventilateur d'appartement ou analogue
DE2126832A1 (de) * 1971-05-29 1972-12-14 Hanning Elektro Werke Querstromgebläse mit motorisch angetriebener Lüfterwalze
DE2602933A1 (de) * 1975-01-28 1976-07-29 Nissan Motor Vorrichtung zur fluidfoerderung mit waermeaustauschereigenschaft

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
PATENTS ABSTRACTS OF JAPAN, Band 4, Nr. 169 (M-43) [651], 21. November 1980; & JP - A - 55 119 998 (NIPPON BUROAA K.K.) 16-09-1980 *
PATENTS ABSTRACTS OF JAPAN, Band 6, Nr. 17 (M-109) [895], 30. Januar 1982; & JP - A - 56 135 791 (HITACHI SEISAKUSHO K.K.) 23-10-1981 *

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0643226A1 (fr) * 1993-08-30 1995-03-15 Ltg Lufttechnische Gmbh Ventilateur traversal insérable
DE4412836A1 (de) * 1994-04-14 1995-10-19 Ltg Lufttechnische Gmbh Querstromventilator mit elastischer Kupplung
US20150024675A1 (en) * 2007-03-07 2015-01-22 Sine Kon Hu Airflow Boosting Assembly for a Forced Air Circulation and Delivery System
US10132514B2 (en) * 2007-03-07 2018-11-20 Sine Kon Hu Airflow boosting assembly for a forced air circulation and delivery system

Also Published As

Publication number Publication date
DE3438039A1 (de) 1986-04-24
DE3569793D1 (en) 1989-06-01
EP0178645B1 (fr) 1989-04-26
ATE42613T1 (de) 1989-05-15

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