EP1317627B1 - Pump comprising a water supply - Google Patents
Pump comprising a water supply Download PDFInfo
- Publication number
- EP1317627B1 EP1317627B1 EP01980376A EP01980376A EP1317627B1 EP 1317627 B1 EP1317627 B1 EP 1317627B1 EP 01980376 A EP01980376 A EP 01980376A EP 01980376 A EP01980376 A EP 01980376A EP 1317627 B1 EP1317627 B1 EP 1317627B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- pump
- pump chamber
- pressure port
- pressure
- cooling agent
- 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.)
- Expired - Lifetime
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/04—Heating; Cooling; Heat insulation
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/04—Heating; Cooling; Heat insulation
- F04C29/042—Heating; Cooling; Heat insulation by injecting a fluid
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2270/00—Control; Monitoring or safety arrangements
- F04C2270/19—Temperature
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
- Compressor (AREA)
- Details And Applications Of Rotary Liquid Pumps (AREA)
- Nozzles (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
- Percussion Or Vibration Massage (AREA)
- Rotary Pumps (AREA)
Abstract
Description
Die Erfindung betrifft eine Pumpe zur Erzeugung von Druck und/oder Unterdruck, gemäß dem Oberbegriff des Patentanspruchs 1.The invention relates to a pump for generating pressure and / or Vacuum, according to the preamble of claim 1.
Solche Pumpen gibt es in verschiedenen Bauarten. Man unterscheidet beispielsweise sogenannte Schraubenverdichter und sogenannte Klauenverdichter.Such pumps are available in different designs. One differentiates for example so-called screw compressors and so-called claw compressors.
Bei den Schraubenverdichtem ist es bekannt, ein Kühlmedium direkt in die Pumpenkammer einzuspeisen. Insbesondere offenbart die US-A-3 795 117 einen Schraubenverdichter, der zur Verdichtung von Kühlmittel dient. Auf der Seite des Niederdruck-Anschlusses wird diesem Schraubenverdichter gasförmiges bzw. dampfförmiges Kühlmittel zugeführt. Das aus dem Schraubenverdichter auf der Seite des Hochdruck-Anschlusses austretende Kühlmittel wird über einen Kondensor und einen daran anschließenden Verdampfer zur Seite des Niederdruck-Anschlusses des Schraubenverdichters zurückgeführt. Zur Kühlung des Schraubenverdichters ist vorgesehen, daß geringe Mengen des von dem Kondensor abströmenden flüssigen Kühlmittels direkt in die Arbeitskammer des Schraubenverdichters eingespeist werden. Die einzuspeisende Menge wird mittels eines Expansionsventils in Abhängigkeit der Temperatur auf der Seite des Hochdruck-Anschlusses gesteuert.In the case of screw compressors, it is known to place a cooling medium directly in the Feed the pump chamber. In particular, US-A-3 795 117 discloses one Screw compressor used to compress coolant. On the side of the Low pressure connection, this screw compressor becomes gaseous or vapor coolant supplied. That from the screw compressor on the The coolant escaping from the high-pressure connection is fed through a Condenser and an adjoining evaporator to the side of the Low pressure connection of the screw compressor returned. For cooling of the screw compressor is provided that small amounts of the Liquid coolant flowing out condenser directly into the working chamber of the Screw compressor can be fed. The amount to be fed is determined by an expansion valve depending on the temperature on the side of the High pressure connection controlled.
Bei den bekannten Klauenverdichtem wird dagegen die anfallende Verdichtungswärme durch einen Kühlluftstrom an der mit Kühlrippen versehenen Außenfläche des Gehäuses oder durch einen im Gehäuse integrierten Kühlwasserkreislauf abgeführt.In the known claw compressors, on the other hand, the resultant Heat of compression through a cooling air flow at the with cooling fins provided outer surface of the housing or by one in the housing integrated cooling water circuit.
Durch die Erfindung wird eine Pumpe der oben angegebenen Art geschaffen, die außerdem die Merkmale des Kennzeichens des Anspruchs 1 aufweist. Durch die temperaturabhängige Regelung des eingespeisten Kühlmedium-Volumenstroms wird eine Überhitzung der Pumpe unter harten Einsatzbedingungen zuverlässig vermieden. Daher ist die erfindungsgemäße Pumpe insbesondere zur Verwendung in Verbindung mit Brennstoffzellen bei Kraftfahrzeugen geeignet. Weitere wesentliche Vorteile gegenüber bekannten Klauenverdichtern sind:
- kompakte Bauweise duch verminderten Bedarf an externer Kühlung;
- geringe Temperaturdifferenzen im Betrieb, da die Verdichtungswärme direkt am Ort ihrer Entstehung abgebaut wird;
- kleinere Spalte zwischen Rotoren und Gehäuse, dadurch verbesserter Wirkungsgrad;
- Befeuchtung der verdichteten Luft, wie bei bestimmten Prozessen vorteilhaft.
- compact design due to reduced need for external cooling;
- low temperature differences during operation, since the heat of compression is dissipated directly at the point where it is generated;
- smaller gaps between rotors and housing, resulting in improved efficiency;
- Humidification of the compressed air, which is advantageous in certain processes.
Als Kühlmedium ist Wasser besonders geeignet.Water is particularly suitable as the cooling medium.
Bei der bevorzugten Ausführungsform der Erfindung ist eine Zweistoff-Zerstäuberdüse, vorgesehen der außer dem flüssigen Kühlmedium ein gasförmiger Volumenstrom zugeführt wird, der vom Hochdruck-Anschluß abgezweigt ist. Die Zweistoff-Zerstäuberdüse ist mit einem Durchfluss-Regulierelement versehen, an dem ein Stellantrieb angreift.In the preferred embodiment of the invention a two-substance atomizer nozzle, provided the besides that A gaseous volume flow is supplied to the liquid cooling medium is branched off from the high pressure connection. The two-component atomizer nozzle is provided with a flow regulating element on which an actuator attacks.
Einzelheiten der Erfindung sind den beigefügten Zeichnungen
entnehmbar. In den Zeichnungen zeigen:
In dem in Figur 1 dargestellten Prinzipschema ist eine durch einen
Elektromotor M betriebene Pumpe 12 gezeigt, die eingangsseitig mit
einer Saugleitung 14 und ausgangsseitig mit einer Druckleitung 16
verbunden ist. Über die Saugleitung 14 kann ein gasförmiges Medium mit
Druck P0 und Temperatur T0 der Pumpe 12 zugeführt und über die
Druckleitung 16 ein gasförmiges Medium mit Druck P2 und Temperatur T2
von der Pumpe abgeführt werden. In die Saugleitung 14 mündet eine
Zweistoff-Zerstäuberdüse 18, der über einen Kühlmittelzulauf 20
Kühlwasser 21 und über einen Druckluftanschluß 22 Druckluft zugeführt
werden kann. Die Zweistoff-Zerstäuberdüse 18 ist mit einem Durchfluß-Regulierelement
versehen, das über einen angreifenden Stellantrieb 24
betätigt werden kann. Die einzuspeisende Kühlwassermenge wird über
einen Regelkreis bestimmt. Zur Regelung ist in der Druckleitung 16 ein
Temperatursensor vorgesehen, der die Temperatur T2 des aus der Pumpe 12
austretenden gasförmigen Mediums mißt. Die gemessene Temperatur T2 wird
mit einen Sollwert Ts verglichen, und die Temperaturdifferenz T2-Ts
wird über Durchfluß des flüssigen Kühlmittels durch Ansteuerung des
Stellantriebs 24 ausgeregelt.1 shows a
In Figur 2 ist die erfindungsgemäße Pumpe von Figur 1 in einer
schematischen Schnittansicht gezeigt. Die Pumpe 12 weist ein Gehäuse 30
auf, in der eine Pumpenkammer 32 gebildet ist. In der Pumpenkammer 32
sind zwei zweiflügelige Rotoren 34, 36 jeweils auf einer Welle 38, 40
gelagert. Die Wellen 38, 40 sind parallel und gegeneinander versetzt
angeordnet. Die Rotoren 34, 36 wälzen bei einer Drehung berührungslos
aufeinander ab und bilden dabei Zellen 42 variabler Größe, wobei eine
innere Verdichtung stattfindet. Die im Betrieb dieses sogenannten
Klauen-Verdichters 12 anfallende Wärme wird im wesentlichen durch die
in Figur 1 beschriebene temeraturgeregelte Wassereinspeisung abgeführt.
Die zur Kühlung benötigte Wassermenge wird über die Zweistoff-Zerstäuberdüse
18 direkt in die Pumpenkammer 32 verdüst.In Figure 2, the pump of Figure 1 according to the invention is in one
schematic sectional view shown. The
Der in Figur 3 abgebildete Klauen-Verdichter 112 entspricht dem in
Figur 2 abgebildeten Klauen-Verdichter 12. Im Unterschied zu dem in
Figur 2 abgebildeten Kühlregelkreis wird hier der der Zweistoff-Zerstäuberdüse
118 zugeführte gasförmige Volumenstrom von der
Druckleitung 116 abgezweigt und über eine Leitung 144 zur Zweistoff-Zerstäuberdüse
118 zurückgeführt. Der auslaßseitige Systemdruck wird so
zur Verdüsung des eingespeisten Kühlwassers 121 ausgenutzt. The
Gemäß einer weiteren erfindungsgemäßen Ausführungsform ist vorgesehen, daß das flüssige Kühlmedium von der steuerbaren Einspritzpumpe nicht direkt in die Pumpenkammer eingespeist wird, sondern über eine zwischen Pumpenkammer und Einspritzpumpe geschaltete Einspritzdüse eingespeist wird.According to a further embodiment according to the invention provided that the liquid cooling medium from the controllable Injection pump is not fed directly into the pump chamber, but via a switch between the pump chamber and the injection pump Injector is fed.
Erfindungsgemäß ist ferner vorgesehen, daß die Einspritzdüse im Bereich der Druckleitung in die Pumpenkammer mündet bzw. daß eine zu der Einspritzdüse im Bereich der Saugleitung zusätzliche Einspritzdüse im Bereich der Druckleitung in die Pumpenkammer mündet.According to the invention it is further provided that the injection nozzle in Area of the pressure line opens into the pump chamber or that one too additional injection nozzle in the area of the suction line opens into the pump chamber in the area of the pressure line.
Durch die temperaturgeregelte Einspeisung des Kühlwassers direkt in die Pumpenkammer wird eine Überhitzung der Pumpe auch unter harten Einsatzbedingungen zuverlässig vermieden. Die erfindungsgemäße Pumpe hat im Vergleich zu aus dem Stand der Technik bekannten Pumpen mit externer Kühlung den Vorteil, daß sie durch ihre kompakte Bauweise einen verminderten Platzbedarf aufweist. Da die Verdichtungswärme direkt am Ort ihrer Entstehung, nämlich in der Pumpenkammer abgebaut wird, treten im Vergleich zur Pumpe mit externer Kühlung nur kleine Temperaturdifferenzen zwischen Gehäuse und Rotoren auf. Dadurch ist die im Betrieb auftretende Temperaturdehnung der Rotoren minimal, so daß die Pumpe mit sehr kleinen Spalten zwischen Rotor und Gehäuse ausgelegt werden kann. Durch die Spaltreduzierung werden Rückströmungen minimiert und der Wirkungsgrad optimiert.Due to the temperature-controlled feeding of the cooling water directly into The pump chamber will overheat the pump even under hard conditions Conditions of use reliably avoided. The pump according to the invention has in comparison to pumps known from the prior art external cooling has the advantage that its compact design has a reduced space requirement. Because the heat of compression directly at the place of their creation, namely dismantled in the pump chamber compared to the pump with external cooling, only small Temperature differences between the housing and rotors. This is the thermal expansion of the rotors occurring during operation is minimal, so that the pump is designed with very small gaps between the rotor and housing can be. Backflows are minimized by reducing the gap and optimized the efficiency.
Claims (6)
- A pump (12; 112) for generating pressure and/or negative pressure, comprising a pump chamber (32; 132) having a high-pressure port (16; 116) and a low-pressure port (14; 114), with a supply of a cooling agent (21; 121) into the pump chamber (32; 132) being provided, the supply being closed-loop controlled by the temperature on the side of the high-pressure port (16; 116), characterized in that at least one injection nozzle (18; 118) for the cooling agent in the form of a two-component atomizer nozzle is arranged to open into the pump chamber (32; 132) and the pump further comprises two at least two-blade rotors (34, 36; 134, 136) which are mounted in the pump chamber (32; 132) on two parallel shafts (38, 40; 138, 140) offset in relation to each other, the rotors rolling off onto each other free of contact during rotation while forming cells (42; 142) with an internal compression.
- The pump as claimed in claim 1, characterized in that the cooling agent (21; 121) is water.
- The pump as claimed in claim 1 or 2, characterized in that at least one injection nozzle (18; 118) opens into the pump chamber (32; 132) in the area of the low-pressure port (14; 114).
- The pump as claimed in any of claims 1 to 3, characterized in that at least one injection nozzle (18; 118) opens into the pump chamber (32; 132) in the area of the high-pressure port (16; 116).
- The pump as claimed in any of the preceding claims, characterized in that in addition to the liquid cooling agent (121) a gaseous volume flow which is branched off from the high-pressure port (116) is supplied to the two-component atomizer nozzle (118).
- The pump as claimed in any of the preceding claims, characterized in that the two-component atomizer nozzle (18) is provided with a flow regulating member which is engaged by an actuating drive (24).
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE20015744U | 2000-09-12 | ||
DE20015744U DE20015744U1 (en) | 2000-09-12 | 2000-09-12 | Pump with water feed |
PCT/EP2001/010536 WO2002023046A1 (en) | 2000-09-12 | 2001-09-12 | Pump comprising a water supply |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1317627A1 EP1317627A1 (en) | 2003-06-11 |
EP1317627B1 true EP1317627B1 (en) | 2004-10-06 |
Family
ID=7946355
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP01980376A Expired - Lifetime EP1317627B1 (en) | 2000-09-12 | 2001-09-12 | Pump comprising a water supply |
Country Status (9)
Country | Link |
---|---|
US (1) | US7077635B2 (en) |
EP (1) | EP1317627B1 (en) |
JP (1) | JP2004509271A (en) |
KR (1) | KR20030032018A (en) |
CN (1) | CN1252389C (en) |
AT (1) | ATE278875T1 (en) |
CA (1) | CA2421988A1 (en) |
DE (2) | DE20015744U1 (en) |
WO (1) | WO2002023046A1 (en) |
Families Citing this family (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
SE0202111D0 (en) * | 2002-07-05 | 2002-07-05 | Delaval Holding Ab | An arrangement and a method for the treatment of a vacuum pump |
DE10258363A1 (en) * | 2002-12-12 | 2004-06-24 | Daimlerchrysler Ag | Device for supplying air to fuel cells has claw compressor with at least two mutually engaged compressor wheels, claw expansion device with at least two mutually engaged expansion device wheels |
US7375719B2 (en) | 2003-12-29 | 2008-05-20 | Lg. Philips Lcd. Co., Ltd | Method and apparatus for driving liquid crystal display |
DE102008030788A1 (en) * | 2008-06-28 | 2009-12-31 | Oerlikon Leybold Vacuum Gmbh | Method for cleaning vacuum pumps |
DE102009017887A1 (en) * | 2009-04-17 | 2010-10-21 | Oerlikon Leybold Vacuum Gmbh | Coarse pumping process for a positive displacement pump |
DE102009043133B4 (en) * | 2009-09-23 | 2012-08-09 | Roth & Rau Ag | Device and method for cleaning a pump chamber of a vacuum pump |
JP5765862B2 (en) * | 2013-08-30 | 2015-08-19 | 株式会社アンレット | Low pressure steam recycling equipment |
CN104632630B (en) * | 2013-11-13 | 2017-01-11 | 中国科学院沈阳科学仪器股份有限公司 | System and method for controlling thermal expansion of Roots dry pump |
CN105443391A (en) * | 2015-12-26 | 2016-03-30 | 广州市心德实业有限公司 | Anti-corrosion device for alleviating corrosion of Roots compressor |
GB2557681A (en) * | 2016-12-15 | 2018-06-27 | Edwards Ltd | A claw pump and method of operation |
Family Cites Families (13)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2906448A (en) * | 1954-10-28 | 1959-09-29 | W C Heraus G M B H | Roots type vacuum pumps |
GB1172993A (en) | 1966-02-23 | 1969-12-03 | Plessey Co Ltd | Improvements in or relating to Rotary-Positive Displacement Machines |
US3759348A (en) * | 1971-11-08 | 1973-09-18 | Maekawa Seisakusho Kk | Method of compressing chlorine gas |
US3795117A (en) * | 1972-09-01 | 1974-03-05 | Dunham Bush Inc | Injection cooling of screw compressors |
FR2401338B1 (en) * | 1977-06-17 | 1980-03-14 | Cit Alcatel | |
DE3427117A1 (en) * | 1984-07-23 | 1986-02-20 | Aerzener Maschinenfabrik Gmbh, 3251 Aerzen | METHOD FOR COOLING A SCREW COMPRESSOR AND SCREW COMPRESSOR FOR CARRYING OUT THE METHOD |
JPS6368793A (en) * | 1986-09-10 | 1988-03-28 | Mazda Motor Corp | Supercharger for engine |
US4861246A (en) * | 1988-01-07 | 1989-08-29 | Bernard Zimmern | Injected compressor with liquid switch |
DE59402988D1 (en) * | 1993-08-11 | 1997-07-10 | Siemens Ag | Mechanical compressor system |
DE4447097A1 (en) * | 1994-12-29 | 1996-07-04 | Guenter Kirsten | Compressor system |
DE19806346C2 (en) | 1998-02-12 | 2000-05-18 | Gardner Denver Wittig Gmbh | Device for cooling and shaft sealing of a compressor |
JP2000291579A (en) * | 1998-10-16 | 2000-10-17 | Toyota Autom Loom Works Ltd | Water-cooled type gas feeding device |
DE10153459B9 (en) * | 2001-10-30 | 2004-09-09 | Kaeser Kompressoren Gmbh | Arrangement for controlling the flow of cooling fluid in compressors |
-
2000
- 2000-09-12 DE DE20015744U patent/DE20015744U1/en not_active Expired - Lifetime
-
2001
- 2001-09-12 WO PCT/EP2001/010536 patent/WO2002023046A1/en active IP Right Grant
- 2001-09-12 AT AT01980376T patent/ATE278875T1/en not_active IP Right Cessation
- 2001-09-12 US US10/363,130 patent/US7077635B2/en not_active Expired - Fee Related
- 2001-09-12 DE DE50104032T patent/DE50104032D1/en not_active Expired - Fee Related
- 2001-09-12 CA CA002421988A patent/CA2421988A1/en not_active Abandoned
- 2001-09-12 JP JP2002527662A patent/JP2004509271A/en active Pending
- 2001-09-12 KR KR10-2003-7003507A patent/KR20030032018A/en not_active Application Discontinuation
- 2001-09-12 EP EP01980376A patent/EP1317627B1/en not_active Expired - Lifetime
- 2001-09-12 CN CNB018155243A patent/CN1252389C/en not_active Expired - Fee Related
Also Published As
Publication number | Publication date |
---|---|
ATE278875T1 (en) | 2004-10-15 |
EP1317627A1 (en) | 2003-06-11 |
CN1455849A (en) | 2003-11-12 |
CN1252389C (en) | 2006-04-19 |
DE50104032D1 (en) | 2004-11-11 |
JP2004509271A (en) | 2004-03-25 |
KR20030032018A (en) | 2003-04-23 |
US20040037727A1 (en) | 2004-02-26 |
DE20015744U1 (en) | 2001-01-25 |
WO2002023046A1 (en) | 2002-03-21 |
CA2421988A1 (en) | 2003-03-11 |
US7077635B2 (en) | 2006-07-18 |
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