EP1643133A1 - Turbocharger - Google Patents
Turbocharger Download PDFInfo
- Publication number
- EP1643133A1 EP1643133A1 EP05020638A EP05020638A EP1643133A1 EP 1643133 A1 EP1643133 A1 EP 1643133A1 EP 05020638 A EP05020638 A EP 05020638A EP 05020638 A EP05020638 A EP 05020638A EP 1643133 A1 EP1643133 A1 EP 1643133A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- compressor
- variable element
- annular gap
- turbocharger
- turbocharger according
- 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
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D17/00—Regulating or controlling by varying flow
- F01D17/10—Final actuators
- F01D17/12—Final actuators arranged in stator parts
- F01D17/14—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits
- F01D17/141—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits by means of shiftable members or valves obturating part of the flow path
- F01D17/143—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits by means of shiftable members or valves obturating part of the flow path the shiftable member being a wall, or part thereof of a radial diffuser
-
- 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
- F04D29/44—Fluid-guiding means, e.g. diffusers
- F04D29/46—Fluid-guiding means, e.g. diffusers adjustable
- F04D29/462—Fluid-guiding means, e.g. diffusers adjustable especially adapted for elastic fluid pumps
- F04D29/464—Fluid-guiding means, e.g. diffusers adjustable especially adapted for elastic fluid pumps adjusting flow cross-section, otherwise than by using adjustable stator blades
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- 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
- F05D2220/00—Application
- F05D2220/40—Application in turbochargers
-
- 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
- F05D2250/00—Geometry
- F05D2250/50—Inlet or outlet
- F05D2250/52—Outlet
-
- 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
- F05D2270/00—Control
- F05D2270/01—Purpose of the control system
- F05D2270/06—Purpose of the control system to match engine to driven device
Definitions
- the invention relates to a turbocharger with the features of the preamble of claim 1.
- a compressor of a turbocharger for an internal combustion engine is described.
- the compressor is located in a compressor housing and is driven by a turbine.
- the compressor promotes the intake air for the internal combustion engine through an annular gap radially outward and on to the combustion chambers of the internal combustion engine.
- the compressor housing has a radially encircling actuator with an axially displaceable position variable element. By changing the width, d. H. the clear width of the circumferential annular gap whose flow-influencing property is adapted to the speed of the compressor.
- a disadvantage of the described embodiment is a risk of contamination between the position-variable element and the compressor housing, which can lead to the blocking of the sliding movement.
- Object of the present invention is to show a generic compressor whose position variable element is insensitive to contamination.
- the overall efficiency of the turbocharger is increased by the inventive design of the compressor outlet region (annular gap), which can be optimally adapted to any air mass flow rate, without acting as a resistor in the flow field. This further leads to improved dynamics of the turbocharger.
- an increase in performance of the internal combustion engine, and the expansion of the usable speed range is possible by a larger compressor. Also, the required space requirement is minimized due to the inventive design.
- the position-variable element may be made of a metal or a plastic. While the benefits of the metal are in temperature resistance, the plastic is particularly easily deformed.
- the preferred mounting options for the position-variable element to the compressor housing according to claim 4 by means of press connection and / or by the use of form-fitting elements.
- a particularly good efficiency of adjusting the clearance of the annular gap is achieved in an arrangement according to claim 5, characterized in that the position-variable element is arranged on both sides of the annular gap.
- FIG. 1 shows a section through a compressor housing 2 of a turbocharger 1 designed according to the invention. Since a compressor is largely radially symmetrical, only one half, starting from a longitudinal axis 5 of the turbocharger 1, is shown. Radially about the longitudinal axis 5, a compressor 6 is arranged. The compressor 6 is in turn largely radially enveloped by the compressor housing 2. The drive of the compressor 6, in the present case an exhaust gas turbine, is not shown in FIG.
- the compressor 6 sucks intake air according to a double arrow direction shown, compresses them and conveys them radially outwardly through an annular gap 3 further into an annular space 7, characterized by a single arrow extending radially around the compressor 6 and also is sheathed by the compressor housing 2.
- the condensed Intake air from the annular space 7 is conveyed in the direction of combustion chambers of an internal combustion engine, not shown.
- a suction-side side wall of the annular gap 3 has a position-variable element 4.
- the position-variable element 4 consists of a high-strength fluorosilicone, and extends radially circumferentially along the side wall of the annular gap 3.
- the variable-position element 4 is arranged by means of a press connection (radially inside) and form-locking elements (radially outside) to the compressor housing 2.
- an adjusting element 8 is arranged, with an axially displaceable plunger 8 '. With the adjusting element 8 and the plunger 8 ', the position-variable element 4 is slidable into the annular gap 3, wherein the flow cross-section is reduced. Due to the elastic properties of the position-variable element 4, the return is passive until the maximum flow cross-section is reached again.
- the compressor map is expanded to high mass flow rates while ensuring good efficiency at low mass flows.
- the overall efficiency of the turbocharger 1 is increased by the inventive design of the compressor output range, which can be optimally adapted to any mass flow rate, without acting as a resistor in the flow field. This results in an improved dynamics of the turbocharger 1 with simultaneous increase in performance and expansion of the usable speed range, since larger compressors can be used, while requiring little space.
- the position-variable element 4 can also be made of metal instead of plastic. Suitable for this example, spring plates, the attachment to the compressor housing is adjusted accordingly. In a further preferred embodiment is located axially on both sides of the annular gap 3 each a variable position element 4. With this embodiment, particularly good efficiencies are achieved because the annular gap 3 can be designed as a Lavall nozzle.
- the actuator 8 may be operated electrically and / or mechanically and / or hydraulically, wherein in hydraulic operation of the plunger 8 'is replaced by hydraulic channels.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Supercharger (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
Description
Die Erfindung betrifft einen Turbolader mit den Merkmalen aus dem Oberbegriff des Patentanspruches 1.The invention relates to a turbocharger with the features of the preamble of
Sie geht von der US-Patentschrift 4,403,914 aus. In dieser ist ein Verdichter eines Turboladers für eine Brennkraftmaschine beschrieben. Der Verdichter befindet sich in einem Verdichtergehäuse und wird von einer Turbine angetrieben. Hierbei fördert der Verdichter die Ansaugluft für die Brennkraftmaschine durch einen Ringspalt radial nach außen und weiter zu den Brennräumen der Brennkraftmaschine. Um das Verdichterkennfeld auszuweiten, verfügt das Verdichtergehäuse über ein radial umlaufendes Stellelement mit einem axial verschiebbaren lageveränderbarem Element. Durch die Veränderung der Breite, d. h. der lichten Weite des umlaufenden Ringspaltes wird dessen strömungsbeeinflussende Eigenschaft an die Drehzahl des Verdichters angepasst.It is based on US Pat. No. 4,403,914. In this, a compressor of a turbocharger for an internal combustion engine is described. The compressor is located in a compressor housing and is driven by a turbine. Here, the compressor promotes the intake air for the internal combustion engine through an annular gap radially outward and on to the combustion chambers of the internal combustion engine. In order to expand the compressor map, the compressor housing has a radially encircling actuator with an axially displaceable position variable element. By changing the width, d. H. the clear width of the circumferential annular gap whose flow-influencing property is adapted to the speed of the compressor.
Nachteilig bei der beschriebenen Ausgestaltung ist eine Verschmutzungsgefahr zwischen dem lageveränderbaren Element und dem Verdichtergehäuse, was zum Blockieren der Verschiebebewegung führen kann.A disadvantage of the described embodiment is a risk of contamination between the position-variable element and the compressor housing, which can lead to the blocking of the sliding movement.
Aufgabe der vorliegenden Erfindung ist es, einen gattungsgemäßen Verdichter aufzuzeigen, dessen lageveränderbares Element verschmutzungsunempfindlich ist.Object of the present invention is to show a generic compressor whose position variable element is insensitive to contamination.
Diese Aufgabe wird durch die Merkmale im kennzeichnenden Teil des Patentanspruchs 1 gelöst.
Durch die Verwendung eines elastischen Materials für das lageveränderbare Element werden jegliche Ringspalte oder Bewegungsfugen, die im Stand der Technik für die Verschiebung des Elementes notwendig sind, vermieden. In vorteilhafter Weise ist der Stellantrieb bei der erfindungsgemäßen Ausgestaltung auf der dem Ringspalt abgewandten Seite des lageveränderbaren Elementes angeordnet, so dass auch hier keine Verschmutzung durch Ansaugluft eintreten kann. Weiter ergibt sich der Vorteil, dass der Ringspalt zu einer stetig veränderbaren Lavalldüse ausgestaltet werden kann. Dies gewährleistet eine Ausweitung des Verdichterkennfeldes zu hohen Massendurchsätzen bei gleichzeitiger Gewährleistung eines guten Wirkungsgrades bei niedrigen Massenströmen, da die Strömungsverluste minimiert sind. Gleichzeitig wird der Gesamtwirkungsgrad des Turboladers durch die erfindungsgemäße Ausgestaltung des Verdichterausgangsbereiches (Ringspalt) erhöht, der jedem Luftmassendurchsatz optimal angepasst werden kann, ohne dabei als Widerstand im Strömungsfeld zu wirken. Dies führt weiter zu einer verbesserten Dynamik des Turboladers. Weiter ist eine Leistungssteigerung der Brennkraftmaschine, sowie die Ausweitung des nutzbaren Drehzahlbandes durch einen größeren Verdichter möglich. Auch wird aufgrund der erfindungsgemäßen Ausgestaltung der benötigte Bauraumbedarf minimiert.This object is solved by the features in the characterizing part of
The use of an elastic material for the positionally variable element avoids any annular gaps or expansion joints which are necessary in the prior art for the displacement of the element. Advantageously, the actuator is arranged in the embodiment according to the invention on the side facing away from the annular gap side of the variable-position element, so that even here no pollution can occur by intake air. Next there is the advantage that the annular gap can be configured to a continuously variable Lavall nozzle. This ensures an expansion of the compressor map to high mass flow rates while ensuring good efficiency at low mass flows, since the flow losses are minimized. At the same time, the overall efficiency of the turbocharger is increased by the inventive design of the compressor outlet region (annular gap), which can be optimally adapted to any air mass flow rate, without acting as a resistor in the flow field. This further leads to improved dynamics of the turbocharger. Next, an increase in performance of the internal combustion engine, and the expansion of the usable speed range is possible by a larger compressor. Also, the required space requirement is minimized due to the inventive design.
Gemäß den Patentansprüchen 2 und 3 kann das lageveränderbare Element aus einem Metall oder einem Kunststoff sein. Während die Vorzüge des Metalls in der Temperaturbeständigkeit liegen, ist der Kunststoff besonders leicht deformierbar.According to the
Um eine Verschmutzungsanfälligkeit noch weiter zu reduzieren, sind die bevorzugten Montagemöglichkeiten für das lageveränderbare Element an das Verdichtergehäuse gemäß Patentanspruch 4 mittels Pressverbindung und/oder mittels der Verwendung von Formschlusselementen.In order to further reduce susceptibility to soiling, the preferred mounting options for the position-variable element to the compressor housing according to claim 4 by means of press connection and / or by the use of form-fitting elements.
Eine besonders gute Effizienz der Einstellung der lichten Weite des Ringspaltes wird bei einer Anordnung gemäß Patentanspruch 5 dadurch erreicht, dass das lageveränderbare Element beidseitig des Ringspaltes angeordnet ist.A particularly good efficiency of adjusting the clearance of the annular gap is achieved in an arrangement according to claim 5, characterized in that the position-variable element is arranged on both sides of the annular gap.
Zur axialen Verstellung des lageveränderbaren Elementes bieten sich insbesondere elektrisch und/oder mechanisch und/oder hydraulisch betreibbare Stellelemente gemäß Patentanspruch 6 an.For the axial adjustment of the position-variable element are in particular electrically and / or mechanically and / or hydraulically operated actuators according to claim 6 at.
Im Folgenden ist ein bevorzugtes Ausführungsbeispiel in einer einzigen Figur näher erläutert.In the following, a preferred embodiment is explained in more detail in a single figure.
Figur 1 zeigt einen Schnitt durch ein Verdichtergehäuse 2 eines erfindungsgemäß ausgestalteten Turboladers 1. Da ein Verdichter weitgehend radialsymmetrisch ist, ist nur eine Hälfte, ausgehend von einer Längsachse 5 des Turboladers 1 dargestellt. Radial um die Längsachse 5 ist ein Verdichter 6 angeordnet. Der Verdichter 6 ist wiederum von dem Verdichtergehäuse 2 weitgehend radial umhüllt. Der Antrieb des Verdichters 6, im vorliegenden Fall eine Abgasturbine, ist in Figur 1 nicht dargestellt. Beim Betrieb des Turboladers 1 saugt der Verdichter 6 Ansaugluft entsprechend einer dargestellten Doppelpfeilrichtung an, verdichtet diese und befördert sie radial nach außen durch einen Ringspalt 3 weiter in einen Ringraum 7, gekennzeichnet durch einen Einfachpfeil, der sich radial um den Verdichter 6 erstreckt und auch noch von dem Verdichtergehäuse 2 ummantelt ist. Weiter wird die verdichtete Ansaugluft aus dem Ringraum 7 in Richtung von Brennräumen einer nicht dargestellten Brennkraftmaschine gefördert.FIG. 1 shows a section through a
Erfindungsgemäß weist eine ansaugseitige Seitenwand des Ringspaltes 3 ein lageveränderbares Element 4 auf. Das lageveränderbare Element 4 besteht aus einem hochfesten Fluorsilikon, und erstrecket sich radial umlaufend entlang der Seitenwand des Ringspaltes 3. Das lageveränderbare Element 4 ist mittels einer Pressverbindung (radial innen) und Formschlusselementen (radial außen) an das Verdichtergehäuse 2 angeordnet. Außerhalb des Verdichtergehäuses 2 befindet ist ein Stellelement 8 angeordnet, mit einem axial verschiebbaren Stößel 8'. Mit dem Stellelement 8 und dem Stößel 8' ist das lageveränderbare Element 4 in den Ringspalt 3 schiebbar, wobei dessen Strömungsquerschnitt verringert wird. Aufgrund der elastischen Eigenschaften des lageveränderbaren Elementes 4 erfolgt die Rückstellung passiv, bis der maximale Strömungsquerschnitt wieder erreicht ist.According to the invention, a suction-side side wall of the annular gap 3 has a position-variable element 4. The position-variable element 4 consists of a high-strength fluorosilicone, and extends radially circumferentially along the side wall of the annular gap 3. The variable-position element 4 is arranged by means of a press connection (radially inside) and form-locking elements (radially outside) to the
Durch diese Strömungsquerschnittsveränderung im Ringspalt 3 wird das Verdichterkennfeld zu hohen Massendurchsätzen bei gleichzeitiger Gewährleistung eines guten Wirkungsgrades bei niedrigen Massenströmen ausgeweitet. Weiter wird der gesamte Wirkungsgrad des Turboladers 1 durch die erfindungsgemäße Ausgestaltung des Verdichterausgangsbereiches, der jedem Massendurchsatz optimal angepasst werden kann, ohne dabei als Widerstand im Strömungsfeld zu wirken, erhöht. Hieraus resultiert eine verbesserte Dynamik des Turboladers 1 bei gleichzeitiger Leistungssteigerung und Ausweitung des nutzbaren Drehzahlbandes, da größere Verdichter eingesetzt werden können, bei gleichzeitig geringem Bauraumbedarf.By this flow cross-section change in the annular gap 3, the compressor map is expanded to high mass flow rates while ensuring good efficiency at low mass flows. Further, the overall efficiency of the
In einer weiteren bevorzugten Ausführungsform kann das lageveränderbare Element 4 anstelle aus Kunststoff auch aus Metall sein. Geeignet sind hierfür beispielsweise Federbleche, wobei die Befestigung am Verdichtergehäuse entsprechend angepasst wird. In einer weiteren bevorzugten Ausführungsform befindet sich axial beidseitig des Ringspaltes 3 jeweils ein lageveränderbares Element 4. Mit dieser Ausführungsform werden besonders gute Wirkungsgrade erzielt, da der Ringspalt 3 als Lavalldüse ausgeführt werden kann. Das Stellelement 8 kann elektrisch und/oder mechanisch und/oder hydraulisch betrieben sein, wobei bei hydraulischem Betrieb der Stößel 8' durch Hydrokanäle ersetzt wird.In a further preferred embodiment, the position-variable element 4 can also be made of metal instead of plastic. Suitable for this example, spring plates, the attachment to the compressor housing is adjusted accordingly. In a further preferred embodiment is located axially on both sides of the annular gap 3 each a variable position element 4. With this embodiment, particularly good efficiencies are achieved because the annular gap 3 can be designed as a Lavall nozzle. The
- 1.1.
- Turboladerturbocharger
- 2.Second
- Verdichtergehäusecompressor housing
- 3.Third
- Ringspaltannular gap
- 4.4th
- Lageveränderbares ElementPositionable element
- 5.5th
- Längsachselongitudinal axis
- 6.6th
- Verdichtercompressor
- 7.7th
- Ringraumannulus
- 8.8th.
- Stellelementactuator
- 8'.8th'.
- Stößeltappet
Claims (6)
dadurch gekennzeichnet, dass das lageveränderbare Element (4) aus einem elastischen Material ist.A turbocharger (1) for an internal combustion engine, comprising a compressor disposed in a compressor housing (2) and rotatable by a compressor for compressing an intake air for the internal combustion engine, wherein the compressed intake air from the compressor radially outwardly through an annular gap (3) in the compressor housing (2) is conveyed and wherein an open width (A) of the annular gap of a position-variable element (4) is variable,
characterized in that the position-variable element (4) is made of an elastic material.
dadurch gekennzeichnet, dass das elastische Material ein Metall ist.Turbocharger according to claim 1,
characterized in that the elastic material is a metal.
dadurch gekennzeichnet, dass das elastische Material ein Kunststoff ist.Turbocharger according to claim 1,
characterized in that the elastic material is a plastic.
dadurch gekennzeichnet, dass das lageveränderbare Element mittels Pressverbindung und/oder Formschlusselementen im Verdichtergehäuse (2) fixiert ist.Turbocharger according to one of the claims 1 to 3,
characterized in that the position-variable element is fixed by means of press connection and / or positive-locking elements in the compressor housing (2).
dadurch gekennzeichnet, dass das lageveränderbare Element (4) beidseitig des Ringspaltes (3) angeordnet ist.Turbocharger according to one of the claims 1 to 4,
characterized in that the position-variable element (4) is arranged on both sides of the annular gap (3).
dadurch gekennzeichnet, dass eine Lageveränderung des lageveränderbaren Elementes (4) mit einem elektrisch und/oder mechanisch und/oder hydraulisch betriebenen Stellelement erfolgt.Turbocharger according to one of claims 1 to 5,
characterized in that a change in position of the position-variable element (4) takes place with an electrically and / or mechanically and / or hydraulically operated actuator.
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102004047103A DE102004047103A1 (en) | 2004-09-29 | 2004-09-29 | turbocharger |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| EP1643133A1 true EP1643133A1 (en) | 2006-04-05 |
| EP1643133B1 EP1643133B1 (en) | 2008-03-05 |
Family
ID=35219327
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| EP05020638A Ceased EP1643133B1 (en) | 2004-09-29 | 2005-09-22 | Turbocharger |
Country Status (2)
| Country | Link |
|---|---|
| EP (1) | EP1643133B1 (en) |
| DE (2) | DE102004047103A1 (en) |
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2008065447A1 (en) * | 2006-12-01 | 2008-06-05 | Parsons Brinckerhoff Limited | Flow control device |
| US7900431B2 (en) | 2005-11-04 | 2011-03-08 | Parsons Brinckerhoff Limited | Process and plant for power generation |
| CN102080577A (en) * | 2010-12-24 | 2011-06-01 | 康跃科技股份有限公司 | Section-variable turbine |
| CN103511063A (en) * | 2013-10-29 | 2014-01-15 | 汉美综合科技（常州）有限公司 | Adjustable back-to-back bilateral-pressure impeller turbocharger |
| CN104632646A (en) * | 2014-03-12 | 2015-05-20 | 珠海格力电器股份有限公司 | Centrifugal compressor and centrifugal unit with same |
| CN112112838A (en) * | 2019-06-19 | 2020-12-22 | 开利公司 | Diffuser system and centrifugal compressor comprising same |
| CN112412809A (en) * | 2020-11-20 | 2021-02-26 | 潘碧琼 | Centrifugal pump capable of reducing internal pressure pulsation |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102011088032A1 (en) * | 2011-12-08 | 2013-06-13 | Bosch Mahle Turbo Systems Gmbh & Co. Kg | loader |
| DE102012104479B4 (en) * | 2012-05-24 | 2016-05-25 | Woco Industrietechnik Gmbh | Compressor housing, in particular turbocharger housing, and method for producing a compressor housing |
| DE202014101614U1 (en) | 2014-04-07 | 2015-07-09 | Woco Industrietechnik Gmbh | actuator |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4403914A (en) * | 1981-07-13 | 1983-09-13 | Teledyne Industries, Inc. | Variable geometry device for turbomachinery |
| DE4218229C1 (en) * | 1992-06-03 | 1993-03-04 | Man B & W Diesel Ag, 8900 Augsburg, De | Turbocharger with radial flow through impeller - has blade retaining recesses, into which blades are insertable after axial shift of adjuster |
| US6139262A (en) * | 1998-05-08 | 2000-10-31 | York International Corporation | Variable geometry diffuser |
| US20040109757A1 (en) * | 2002-12-06 | 2004-06-10 | York International Corporation | Variable geometry diffuser mechanism |
Family Cites Families (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CH125547A (en) * | 1927-02-21 | 1928-04-16 | Oscar Simmen | Gyroscope. |
| US3071347A (en) * | 1959-12-30 | 1963-01-01 | Garrett Corp | Variable area nozzle device |
| US3150650A (en) * | 1961-09-29 | 1964-09-29 | Caterpillar Tractor Co | Variable area diffuser for compressor |
| JP2000213496A (en) * | 1999-01-20 | 2000-08-02 | Ishikawajima Harima Heavy Ind Co Ltd | Centrifugal compressor |
| JP4573074B2 (en) * | 2000-05-24 | 2010-11-04 | 株式会社Ｉｈｉ | Centrifugal compressor with variable diffuser and its control method |
-
2004
- 2004-09-29 DE DE102004047103A patent/DE102004047103A1/en not_active Withdrawn
-
2005
- 2005-09-22 EP EP05020638A patent/EP1643133B1/en not_active Ceased
- 2005-09-22 DE DE502005003064T patent/DE502005003064D1/en active Active
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4403914A (en) * | 1981-07-13 | 1983-09-13 | Teledyne Industries, Inc. | Variable geometry device for turbomachinery |
| DE4218229C1 (en) * | 1992-06-03 | 1993-03-04 | Man B & W Diesel Ag, 8900 Augsburg, De | Turbocharger with radial flow through impeller - has blade retaining recesses, into which blades are insertable after axial shift of adjuster |
| US6139262A (en) * | 1998-05-08 | 2000-10-31 | York International Corporation | Variable geometry diffuser |
| US20040109757A1 (en) * | 2002-12-06 | 2004-06-10 | York International Corporation | Variable geometry diffuser mechanism |
Cited By (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US7900431B2 (en) | 2005-11-04 | 2011-03-08 | Parsons Brinckerhoff Limited | Process and plant for power generation |
| WO2008065447A1 (en) * | 2006-12-01 | 2008-06-05 | Parsons Brinckerhoff Limited | Flow control device |
| US8206089B2 (en) | 2006-12-01 | 2012-06-26 | Parsons Brinckerhoff Limited | Flow control device |
| CN102080577A (en) * | 2010-12-24 | 2011-06-01 | 康跃科技股份有限公司 | Section-variable turbine |
| CN103511063A (en) * | 2013-10-29 | 2014-01-15 | 汉美综合科技（常州）有限公司 | Adjustable back-to-back bilateral-pressure impeller turbocharger |
| CN103511063B (en) * | 2013-10-29 | 2017-12-05 | 汉美综合科技（常州）有限公司 | Adjustable back-to-back bilateral-pressure impeller turbocharger |
| CN104632646A (en) * | 2014-03-12 | 2015-05-20 | 珠海格力电器股份有限公司 | Centrifugal compressor and centrifugal unit with same |
| WO2015135282A1 (en) * | 2014-03-12 | 2015-09-17 | 珠海格力电器股份有限公司 | Centrifugal compressor and centrifugal facility having same |
| US10323653B2 (en) | 2014-03-12 | 2019-06-18 | Gree Electric Appliances, Inc. Of Zhuhai | Centrifugal compressor and centrifugal unit having the same |
| CN112112838A (en) * | 2019-06-19 | 2020-12-22 | 开利公司 | Diffuser system and centrifugal compressor comprising same |
| WO2020257047A1 (en) * | 2019-06-19 | 2020-12-24 | Carrier Corporation | Diffuser system and centrifugal compressor comprising the same |
| CN112412809A (en) * | 2020-11-20 | 2021-02-26 | 潘碧琼 | Centrifugal pump capable of reducing internal pressure pulsation |
Also Published As
| Publication number | Publication date |
|---|---|
| DE102004047103A1 (en) | 2006-04-13 |
| EP1643133B1 (en) | 2008-03-05 |
| DE502005003064D1 (en) | 2008-04-17 |
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