EP0635643A2 - Turbo-compresseur pour fluide de réfrigération - Google Patents

Turbo-compresseur pour fluide de réfrigération Download PDF

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Publication number
EP0635643A2
EP0635643A2 EP94108502A EP94108502A EP0635643A2 EP 0635643 A2 EP0635643 A2 EP 0635643A2 EP 94108502 A EP94108502 A EP 94108502A EP 94108502 A EP94108502 A EP 94108502A EP 0635643 A2 EP0635643 A2 EP 0635643A2
Authority
EP
European Patent Office
Prior art keywords
blade
impeller
refrigerant
hub
blades
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.)
Withdrawn
Application number
EP94108502A
Other languages
German (de)
English (en)
Other versions
EP0635643A3 (fr
Inventor
Peter Dr.-Ing. Albring
Rainer Dipl.-Ing. Apley
Klaus Dr.-Ing.habil. Döge
Günter Prof. Dr.-Ing. Heinrich
Ernst Prof. Dr.-Ing. Lindner
Norbert Müller
Reinhardt Dr.-Ing. Pauer
Eberhard Pilling
Rainer Dipl.-Ing. Rudischer
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.)
Institut fuer Luft und Kaeltetechnik Gemeinnuetzige GmbH
Original Assignee
Institut fuer Luft und Kaeltetechnik Gemeinnuetzige 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 Institut fuer Luft und Kaeltetechnik Gemeinnuetzige GmbH filed Critical Institut fuer Luft und Kaeltetechnik Gemeinnuetzige GmbH
Publication of EP0635643A2 publication Critical patent/EP0635643A2/fr
Publication of EP0635643A3 publication Critical patent/EP0635643A3/fr
Withdrawn legal-status Critical Current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
    • F04D29/26—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
    • 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
    • F04D29/02—Selection of particular materials
    • F04D29/023—Selection of particular materials especially adapted for elastic fluid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2300/00—Materials; Properties thereof
    • F05D2300/40—Organic materials
    • F05D2300/43—Synthetic polymers, e.g. plastics; Rubber
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2300/00—Materials; Properties thereof
    • F05D2300/60—Properties or characteristics given to material by treatment or manufacturing
    • F05D2300/603—Composites; e.g. fibre-reinforced

Definitions

  • the invention relates to a refrigerant turbocompressor, preferably of a radial type, for the compression of water vapor under vacuum conditions, which has a large number of blades.
  • the density of water vapor in refrigeration systems is up to 3 orders of magnitude lower than that in vapor compression and also in the compression of classic refrigerants. Due to the extremely low density of water vapor, very large volume flows have to be pumped in refrigeration systems. Process conditions also require pressure ratios of ⁇ 5.
  • Displacement compressors such as known screw compressors, indeed achieve the required pressure ratio, but are severely limited in the maximum flow rate and are considerably too expensive.
  • Flow compressors for example turbo compressors of radial design, do not reach the required pressure ratio in one stage for the conditions of refrigeration systems.
  • These compressors are expensive because they are almost always designed for the compression of gases or vapors of a much higher density (eg air) and thus designed for a comparatively significantly higher specific drive power.
  • the blades of known radial impellers are usually connected to the supporting disk by welding or riveting, and the rivets can be inserted or milled through the blade.
  • the difficulties increase because the flow cross section is blocked by the blades, the supporting disk is weakened and the structure is changed during welding.
  • Radial compressor impellers that are subjected to high mechanical loads are mainly cast from steel or duralumin, forged and machined by milling and thus consist of one piece. To achieve a bumpless entry, the bending of the blade entry area in the circumferential direction or the use of a mostly cast front runner have proven effective. These face rotors form the blade entry area, have a small diameter in relation to the outer diameter and are therefore comparatively little mechanically loaded. The subsequent radial blade (radial fiber blade) is superior to all others in terms of strength. It is used where a large static pressure increase with the smallest dimensions and without particularly high efficiencies is required for large pressure ratios. Circumferential speeds of up to 600 m / s are carried out.
  • Centrifugal compressors of radial design for high-performance steam chillers have very high centrifugal forces due to the extraordinarily high peripheral speeds (in the range around 500 m / s). These are the main load for the impeller, since the forces that have to be transferred to the pumped medium are comparatively low.
  • the object of the invention is to design the impeller of a radial turbocompressor in such a way that, given the low density of the conveying medium, preferably water vapor, the necessary high volume flows can be conveyed at the required pressure conditions and that the strength problems resulting from the high peripheral speeds are effectively solved .
  • the conveying medium preferably water vapor
  • turbocompressors can be produced that meet the above technical requirements.
  • the higher pressure ratios that can be achieved are sufficient for all refrigeration applications with evaporation temperatures ⁇ 0 ° C, single-stage or max. two-stage turbo compressor radial design.
  • this leads to a significant reduction in the cost of the compressor compared to conventional designs, the impellers of which are made of stainless steel or titanium.
  • further savings result from the fact that the turbocompressor can be driven directly and no costly gear is required.
  • the connecting line between the blade 1 and the impeller segment 2 is, as can be seen from FIG. 1, purely radially or displaced in the circumferential direction, as shown in FIG. 2.
  • the centrifugal forces acting on the blades 1 are transmitted via the shoulders 3 from the impeller segments 2 to the blade-carrying elements 4, 5 and to the hub 6.
  • the connection of the inner blade-carrying element 4 to the hub 6 is also non-positive and positive.
  • An adjustment of the impeller segments 2 is carried out with the outer blade-carrying element 5.
  • the reinforcing material made of carbon fibers is oriented radially in the blades 1 and the impeller segments 2 and in the blade-bearing elements 4 and 5 in the circumferential direction.
  • the lugs 3 on the impeller segments 2 also contain reinforcing material.
  • the blades 1 and the impeller segments 2 can be divided into elements.
  • FIG. 3 shows a further exemplary embodiment of a radial refrigerant turbocompressor in axial section.
  • the blades 1 are connected to the impeller segments 2.
  • the impeller segments 2 have lugs 3, via which they are non-positively and positively connected to the hub 6.
  • the blade-carrying elements 4 are partially arranged axially next to one another and partially radially one above the other.
  • the reinforcing material lies in the blades 1 and in the impeller segments 2 in accordance with the stress, preferably radially and in the blade-carrying elements 4 in the circumferential direction.
  • the fibers are oriented both radially and in the circumferential direction in accordance with the stress.
  • impeller segments 2 can also be subdivided in such a way that elements thereof form a continuous disk.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP94108502A 1993-06-25 1994-06-03 Turbo-compresseur pour fluide de réfrigération. Withdrawn EP0635643A3 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4321173A DE4321173C2 (de) 1993-06-25 1993-06-25 Radiallaufrad
DE4321173 1993-06-25

Publications (2)

Publication Number Publication Date
EP0635643A2 true EP0635643A2 (fr) 1995-01-25
EP0635643A3 EP0635643A3 (fr) 1995-03-08

Family

ID=6491233

Family Applications (1)

Application Number Title Priority Date Filing Date
EP94108502A Withdrawn EP0635643A3 (fr) 1993-06-25 1994-06-03 Turbo-compresseur pour fluide de réfrigération.

Country Status (3)

Country Link
US (1) US5464325A (fr)
EP (1) EP0635643A3 (fr)
DE (1) DE4321173C2 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2004046559A1 (fr) * 2002-11-15 2004-06-03 Daimlerchrysler Ag Roue de roulement
EP2955386A4 (fr) * 2013-06-04 2016-03-02 Mitsubishi Heavy Ind Ltd Impulseur, machine tournante, et procédé pour assembler une machine tournante
WO2026068607A1 (fr) * 2024-09-26 2026-04-02 Everllence Se Turbine d'un compresseur, compresseur et son utilisation

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DE19525829A1 (de) * 1995-07-15 1997-01-16 Abb Research Ltd Lüfter
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DE19705407A1 (de) * 1997-02-13 1998-08-20 Inst Luft Kaeltetech Gem Gmbh Wasserdampf-Turboverdichter
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DE19723844A1 (de) * 1997-06-06 1998-12-10 Abb Research Ltd Laufrad
DE19723845A1 (de) * 1997-06-06 1998-12-10 Abb Research Ltd Verfahren zur Herstellung von Schaufeln aus polymerem Verbundmaterial
DE19742023B4 (de) * 1997-09-24 2006-07-13 Beez, Günther, Dipl.-Ing. Laufrad
FR2776030B1 (fr) * 1998-03-11 2000-07-13 Abb Solyvent Ventec Roue de ventilation centrifuge en materiaux composites
RU2189502C2 (ru) * 2000-07-12 2002-09-20 Открытое акционерное общество Научно-производственное объединение "Искра" Центробежный компрессор
FI111290B (fi) * 2001-11-12 2003-06-30 Flaekt Woods Ab Korkeapainepuhallin
RU2239100C2 (ru) * 2002-10-30 2004-10-27 Федеральное государственное унитарное предприятие "Центральный институт авиационного моторостроения им. П.И.Баранова" Рабочее колесо центробежного компрессора из композиционного материала и способ его изготовления
RU2227235C1 (ru) * 2003-01-13 2004-04-20 Орловский государственный технический университет Импеллерное уплотнение
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US20070119572A1 (en) 2005-11-30 2007-05-31 Raytheon Company System and Method for Boiling Heat Transfer Using Self-Induced Coolant Transport and Impingements
US20070119568A1 (en) * 2005-11-30 2007-05-31 Raytheon Company System and method of enhanced boiling heat transfer using pin fins
US20070119199A1 (en) * 2005-11-30 2007-05-31 Raytheon Company System and method for electronic chassis and rack mounted electronics with an integrated subambient cooling system
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US7908874B2 (en) 2006-05-02 2011-03-22 Raytheon Company Method and apparatus for cooling electronics with a coolant at a subambient pressure
US8651172B2 (en) 2007-03-22 2014-02-18 Raytheon Company System and method for separating components of a fluid coolant for cooling a structure
RU2345252C1 (ru) * 2007-06-15 2009-01-27 Открытое акционерное общество Научно-производственное объединение "Искра" Центробежный компрессор
US7934386B2 (en) 2008-02-25 2011-05-03 Raytheon Company System and method for cooling a heat generating structure
US7907409B2 (en) 2008-03-25 2011-03-15 Raytheon Company Systems and methods for cooling a computing component in a computing rack
RU2382910C1 (ru) * 2008-11-18 2010-02-27 Федеральное государственное унитарное предприятие "Центральный институт авиационного моторостроения имени П.И. Баранова" Рабочее колесо компрессора
RU2395727C1 (ru) * 2009-05-22 2010-07-27 Открытое акционерное общество Научно-производственное объединение "Искра" Устройство для установки и снятия элементов концевого уплотнительного узла центробежного компрессора
RU2400650C1 (ru) * 2009-07-01 2010-09-27 Открытое акционерное общество Научно-производственное объединение "Искра" Устройство для контроля монтажа "сухих" газодинамических уплотнений центробежного компрессора
RU2426010C1 (ru) * 2010-03-30 2011-08-10 Открытое акционерное общество Научно-производственное объединение "Искра" Центробежный компрессор
RU2432502C1 (ru) * 2010-08-02 2011-10-27 Открытое акционерное общество Институт технологии и организации производства (ОАО НИИТ) Способ изготовления рабочего колеса центробежного компрессора из композиционного материала
US20120051924A1 (en) * 2010-08-31 2012-03-01 General Electric Company Turbine Blade Assembly
WO2012116285A2 (fr) 2011-02-25 2012-08-30 Board Of Trustees Of Michigan State University Appareil de moteur à disque à ondes
RU2459980C1 (ru) * 2011-03-23 2012-08-27 Закрытое акционерное общество "Научно-исследовательский и конструкторский институт центробежных и роторных компрессоров им. В.Б. Шнеппа" Способ изготовления рабочих колес центробежных копрессоров
NO334130B1 (no) * 2012-09-07 2013-12-16 Dynavec As Anordning ved løpehjul for hydraulisk strømningsmaskin
US10193430B2 (en) 2013-03-15 2019-01-29 Board Of Trustees Of Michigan State University Electromagnetic device having discrete wires
JP6270280B2 (ja) * 2014-12-03 2018-01-31 三菱重工業株式会社 インペラ、及び回転機械
JP6288516B2 (ja) * 2014-12-03 2018-03-07 三菱重工業株式会社 インペラ、及び回転機械
JP2016156302A (ja) * 2015-02-24 2016-09-01 三菱重工業株式会社 羽根車
RU2576716C1 (ru) * 2015-03-25 2016-03-10 Александр Владимирович Грибановский Способ изготовления рабочего колеса центробежного компрессора из композиционного материала
RU2576725C1 (ru) * 2015-04-07 2016-03-10 Александр Владимирович Грибановский Способ изготовления рабочего колеса центробежного компрессора из композиционного материала
RU2652269C2 (ru) * 2016-02-29 2018-04-25 Акционерное общество "Институт технологии и организации производства" (АО НИИТ) Способ изготовления рабочего колеса центробежного компрессора из композиционного материала
RU2651903C1 (ru) * 2016-12-23 2018-04-24 Владимир Александрович Грибановский Рабочее колесо центробежного компрессора из композиционного материала
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RU2769595C1 (ru) * 2021-03-30 2022-04-04 Владимир Александрович Грибановский Способ изготовления рабочего колеса авиационного двигателя из композиционного материала
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Publication number Priority date Publication date Assignee Title
WO2004046559A1 (fr) * 2002-11-15 2004-06-03 Daimlerchrysler Ag Roue de roulement
EP2955386A4 (fr) * 2013-06-04 2016-03-02 Mitsubishi Heavy Ind Ltd Impulseur, machine tournante, et procédé pour assembler une machine tournante
US10514045B2 (en) 2013-06-04 2019-12-24 Mitsubishi Heavy Industries Compressor Corporation Impeller, rotating machine, and method for assembling rotating machine
WO2026068607A1 (fr) * 2024-09-26 2026-04-02 Everllence Se Turbine d'un compresseur, compresseur et son utilisation

Also Published As

Publication number Publication date
US5464325A (en) 1995-11-07
EP0635643A3 (fr) 1995-03-08
DE4321173C2 (de) 1996-02-22
DE4321173A1 (de) 1995-01-12

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