EP0420899A1 - Multi-stage vacuum-pump set - Google Patents
Multi-stage vacuum-pump setInfo
- Publication number
- EP0420899A1 EP0420899A1 EP89907120A EP89907120A EP0420899A1 EP 0420899 A1 EP0420899 A1 EP 0420899A1 EP 89907120 A EP89907120 A EP 89907120A EP 89907120 A EP89907120 A EP 89907120A EP 0420899 A1 EP0420899 A1 EP 0420899A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- pump
- gas ring
- unit according
- pumps
- ring pump
- 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.)
- Pending
Links
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D25/00—Pumping installations or systems
- F04D25/16—Combinations of two or more pumps ; Producing two or more separate gas flows
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- 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
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
- F04C18/344—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
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- 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
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
- F04C23/005—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of dissimilar working principle
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- 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
- F04C25/00—Adaptations of pumps for special use of pumps for elastic fluids
- F04C25/02—Adaptations of pumps for special use of pumps for elastic fluids for producing high vacuum
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- 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
- F04D17/08—Centrifugal pumps
- F04D17/16—Centrifugal pumps for displacing without appreciable compression
- F04D17/168—Pumps specially adapted to produce a vacuum
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- 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
Definitions
- the invention relates to a multi-stage vacuum pump unit in which an oil-lubricated or dry-running mechanical displacement pump is provided in the last, atmospheric stage and this vacuum side is preceded by at least one further pump.
- Roots pumps are characterized by excellent efficiency because of the contact-free rotation of their Roots pumps compared to other mechanical vacuum pumps.
- an overall efficiency can be improved by providing a Roots pump.
- this only applies to pressure differences d 2 Roots pump of less than 50 mbar.
- the many narrow gaps of this pump do not allow larger pressure differences, because the greater heating associated with higher pressure differences causes thermal expansions which, due to the narrow gaps, can easily cause the roots to jam.
- the invention is based on the object of developing a multi-stage vacuum pump unit of the type described at the outset in such a way that on the one hand the oil consumption and thus the contaminated oil tightness is substantially reduced and on the other hand the efficiency is still improved compared to known multi-stage vacuum pump units.
- the upstream pump is a gas ring pump.
- the efficiency of a gas ring pump is only half as high as the efficiency of a Roots pump, tests have shown that by using a gas ring pump in a multi-stage vacuum pump unit, both the energy requirement and the cost can be significantly reduced, with none Losses with regard to the operational safety of the unit have to be accepted.
- gas ring pumps work oil-free in the compressor chamber, the amount of oil otherwise required when using a mechanical displacement pump is completely eliminated. Because of the higher pressure ratio that can be achieved with a gas ring pump, the size of the downstream positive displacement pump is reduced. Smaller sizes of these pumps also require smaller amounts of lubricating oil, and the power requirement also decreases. A corresponding cooling of the medium compressed by the gas ring pump or the gas ring pump itself also contributes to reducing the amount of lubricating oil.
- a further, very effective cooling of the gas ring pump is achieved in that cooling channels are provided for a jacket cooling on its housing and these cooling channels are connected to a coolant tank.
- the speed of each pump can be optimally adapted to the prevailing operating conditions. If only one drive motor is used for both pumps, the different speeds necessary for optimal adaptation of the two pumps can be achieved, that one of the two pumps is directly coupled to the drive motor and the other is coupled to the latter via a belt drive or a gear.
- a gas ring pump 2 driven by its own electric motor 1 has an intake pipe 3, via which the gas ring pump 2 is connected to a container (not shown in the drawing) to be evacuated. With its outlet 4, the Gasringpu pe 2 is connected via a connecting pipe 5 to the inlet opening 6 of a rotary vane pump 7. Through this rotary valve pu CT / EP89 / 00659
- the medium pre-compressed by the gas ring pump 2 is further compressed and expelled through the outlet opening 8.
- the size of the rotary vane pump, which compresses to atmosphere can be selected to be considerably smaller as a result of the pre-compression by the gas ring pump, as a result of which the amount of lubricating oil produced is significantly reduced compared to a multi-stage vacuum pump unit consisting only of rotary vane pumps . Since the gas ring pump 2 works completely oil-free in the compression chamber, the amount of oil otherwise required for the preliminary stage is also eliminated. In addition, a gas ring pump with only one shaft and without gear can be inexpensively built in multiple stages, so that a large pressure difference, i.e. high pre-compression, can be achieved.
- a gas ring pump is considerably less sensitive due to the fact that the gap is two to three times larger than Roots pumps, whereby the gap losses are not higher or even lower due to the division into several stages. Furthermore, due to its mode of operation (freely rotating impeller), the gas ring pump is only limited in the permissible speed by the type of material used for the impeller. With a multi-stage design of the gas ring pump, particularly good and intensive cooling can be achieved as a result of the larger surface area compared to a Roots pump, which contributes to an improvement in efficiency.
- Injection cooling is a further advantageous cooling option.
- a coolant is injected into the gas ring pump 2.
- the cooling of the volume of the medium to be compressed, which can be handled by the downstream rotary vane pump 7, is reduced, so that the subsequent rotary vane pump 7 can be designed correspondingly smaller.
- a very intensive cooling of the medium to be compressed is achieved by jacket cooling of the gas ring pump 2.
- cooling channels 10 are formed on the housing of the gas ring pump 2, through which a cooling liquid flows.
- the cooling channels 10 of the gas ring pump 2 are connected via pipes 12 to a cooling jacket 11 of the rotary vane pump 7 which also has the cooling liquid flowing through it.
- the cooling ducts 10 of the gas ring pump 2 are connected to one connection of a cooler 13 and the cooling jacket 11 of the rotary vane pump 7 to the other connection of the cooler 13 via further pipelines 12a and 12b.
- the cooler 13 has a fan 15 which is driven by an electric motor 14.
- a circulation pump 16 can be arranged in the course of the pipes 12a or 12b.
- a series connection of the coolant circuits of the two pumps 2 and 7 is shown.
- a parallel connection of these cooling circuits is also possible.
- a cooler for the two pumps 2 and 7 is sufficient, so that the construction work is kept to a minimum.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
- Non-Positive Displacement Air Blowers (AREA)
Abstract
Dans un agrégat de pompe à vide à plusieurs étages, une pompe volumétrique mécanique lubrifiée à l'huile ou fonctionnant à sec est agencée dans le dernier étage atmosphérique, et au moins une autre pompe est agencée en amont de celle-ci, du côté de génération du vide. On réduit la consommation d'huile tout en améliorant l'efficacité de l'agrégat lorsque la pompe en amont de la pompe volumétrique est une pompe annulaire à gaz (2).In a multi-stage vacuum pump assembly, a mechanical oil-lubricated or dry-running positive displacement pump is arranged in the last atmospheric stage, and at least one other pump is arranged upstream thereof, on the side of vacuum generation. Oil consumption is reduced while improving the efficiency of the aggregate when the pump upstream of the positive displacement pump is an annular gas pump (2).
Description
Mehrstufiges VakuumpumpenaggregatMulti-stage vacuum pump unit
Die Erfindung betrifft ein mehrstufiges Vakuumpumpenaggregat, bei dem in der letzten, atmosphärischen Stufe eine ölgeschmie t.e oder trockenlaufende mechanische Verdrängerpumpe vorgesehe und dieser vakuu seitig mindestens eine weitere Pumpe vorge- schaltet ist.The invention relates to a multi-stage vacuum pump unit in which an oil-lubricated or dry-running mechanical displacement pump is provided in the last, atmospheric stage and this vacuum side is preceded by at least one further pump.
Mechanische Verdrängerpumpen gelten als Vakuumpumpen mit dem besten Wirkungsgrad im gesamten Vakuumbereich. Daher ist es b kannt (DE-OS 35 45 982; DE-GM 84 27 615), bei einem ehrstufi gen Vakuumpumpenaggregat mehrere Drehschieberpumpen hinterein ander zu schalten. Derartige Pumpen benötigen in der Regel al Schmier- und Abdichtmedium öl, das in allen Verdichterstufen ständig frisch zugeführt wird. Wenn die zugeführten Mengen au relativ klein sind, so bedeutet die ständige oder gezielte Zu fuhr von frischem öl doch eine nicht unerhebliche Kostenbela¬ stung. Außerdem muß das verbrauchte Öl mittels gesonderter Ab scheider wieder aus dem geförderten Medium abgeschieden und schließlich beseitigt werden.Mechanical positive displacement pumps are considered to be vacuum pumps with the best efficiency in the entire vacuum range. Therefore, it is known b (DE-OS 35 45 982; DE-GM 84 27 615) to switch several rotary vane pumps in a row in an Ehrstufi gene vacuum pump unit. Such pumps generally require oil as a lubricating and sealing medium, which is constantly freshly supplied in all compressor stages. If the quantities supplied are also relatively small, the constant or targeted supply of fresh oil means a not inconsiderable cost burden. In addition, the used oil must be separated from the extracted medium using a separate separator and finally eliminated.
Es ist ferner bekannt (Sonderdruck "Auswahlkriterien für Pump zum Erzeugen von Vakuum" aus der Zeitschrift "Maschinenmarkt" Vogel-Verlag Würzburg, 88 JG., Heft 17 vom 02.03.1982), einer Drehschieberpumpe eine Wälzkolbenpumpe vorzuschalten. Bekannt weise zeichnen sich Wälzkolbenpumpen wegen der berührungsfrei Rotation ihrer Wälzkolben gegenüber anderen mechanischen Vaku pumpen durch einen hervorragenden Wirkungsgrad aus. Somit läß sich bei einem mehrstufigen Vakuumpumpenaggregat durch Vorsch ten einer Wälzkolbenpumpe eine Verbesserung des Gesamtwirkung grades erreichen. Dies gilt jedoch nur bei Druckdifferenzen d 2 Wälzkolbenpumpe von kleiner 50 mbar. Die vielen engen Spalte dieser Pumpe lassen größere Druckdifferenzen nicht zu, denn die mit höheren Druckdifferenzen verbundene stärkere Erwärmung ruft Wärmedehnungen hervor, die infolge der engen Spalte leicht zum Verklemmen der Wälzkolben führen können.It is also known (special print "Selection criteria for pumps to generate vacuum" from the magazine "Maschinenmarkt" Vogel-Verlag Würzburg, 88 JG., Issue 17 of 02.03.1982) to connect a Roots pump to a rotary vane pump. As is well known, Roots pumps are characterized by excellent efficiency because of the contact-free rotation of their Roots pumps compared to other mechanical vacuum pumps. Thus, in a multi-stage vacuum pump unit, an overall efficiency can be improved by providing a Roots pump. However, this only applies to pressure differences d 2 Roots pump of less than 50 mbar. The many narrow gaps of this pump do not allow larger pressure differences, because the greater heating associated with higher pressure differences causes thermal expansions which, due to the narrow gaps, can easily cause the roots to jam.
Eine größere Druckdifferenz ließe sich ohne die genannte Gefahr des Verklemmens durch eine intensive Kühlung oder durch die Hintereinanderschaltung mehrerer Wälzkolbenpumpen erzielen. Der Bauaufwand und im Betrieb dann der Wartungsaufwand für solche Lösungen wäre jedoch unverhältnismäßig hoch. Außerdem leidet die Betriebssicherheit.A greater pressure difference could be achieved without the aforementioned risk of jamming by intensive cooling or by connecting several Roots pumps in series. The construction effort and then the maintenance effort for such solutions would be disproportionately high. Operational safety also suffers.
Der Erfindung liegt die Aufgabe zugrunde, ein mehrstufiges Vakuumpumpenaggregat der eingangs beschriebenen Art so weiter¬ zubilden, daß einerseits der Ölverbrauch und damit die ver¬ schmutzte Öl enge wesentlich reduziert ist und andererseits der Wirkungsgrad gegenüber bekannten mehrstufigen Vakuumpumpen¬ aggregaten noch verbessert ist.The invention is based on the object of developing a multi-stage vacuum pump unit of the type described at the outset in such a way that on the one hand the oil consumption and thus the contaminated oil tightness is substantially reduced and on the other hand the efficiency is still improved compared to known multi-stage vacuum pump units.
Die Lösung der gestellten Aufgabe gelingt nach der Erfindung dadurch, daß die vorgeschaltete Pumpe eine Gasringpumpe ist. Obwohl der Wirkungsgrad einer Gasringpumpe etwa nur halb so hoch wie der Wirkungsgrad einer Wälzkolbenpumpe ist, wurde durch Versuche nachgewiesen, daß durch den Einsatz einer Gas¬ ringpumpe bei einem mehrstufigen Vakuumpumpenaggregat sowohl der Energiebedarf als auch der Kostenaufwand wesentlich vermin¬ dert werden können, wobei keine Einbußen im Hinblick auf die Be¬ triebssicherheit des Aggregates hingenommen werden müssen. Da Gasringpumpen im Verdichterraum δlfrei arbeiten, entfällt die ansonsten beim Einsatz einer mechanischen Verdrängerpumpe not¬ wendige Ölmenge vollständig. Wegen des mit einer Gasringpumpe erzielbaren höheren Druckverhältnisses ergibt sich eine Verklei¬ nerung der Baugröße der nachgeschalteten Verdrängerpumpe. Klei- nere Baugrδßen dieser Pumpen erfordern auch geringere Schmier¬ ölmengen, außerdem sinkt der Leistungsbedarf. Zur Verminderung der Schmierölmenge trägt auch eine entspre¬ chende Kühlung des durch die Gasringpumpe verdichteten Medium oder der Gasringpumpe selbst bei.The object is achieved according to the invention in that the upstream pump is a gas ring pump. Although the efficiency of a gas ring pump is only half as high as the efficiency of a Roots pump, tests have shown that by using a gas ring pump in a multi-stage vacuum pump unit, both the energy requirement and the cost can be significantly reduced, with none Losses with regard to the operational safety of the unit have to be accepted. Since gas ring pumps work oil-free in the compressor chamber, the amount of oil otherwise required when using a mechanical displacement pump is completely eliminated. Because of the higher pressure ratio that can be achieved with a gas ring pump, the size of the downstream positive displacement pump is reduced. Smaller sizes of these pumps also require smaller amounts of lubricating oil, and the power requirement also decreases. A corresponding cooling of the medium compressed by the gas ring pump or the gas ring pump itself also contributes to reducing the amount of lubricating oil.
Eine weitere, sehr wirksame Kühlung der Gasringpumpe wird da¬ durch erreicht, daß an ihrem Gehäuse Kühlkanäle für eine Mant kühlung vorgesehen und diese Kühlkanäle an einen Kühlmittelkr angeschlossen sind. Dadurch, daß die Gasringpumpe an den Kühl mittelkreislauf der Drehschieberpumpe angeschlossen ist, komm man mit einem einzigen Kühler bzw. Wärmetauscher für das Aggr gat aus.A further, very effective cooling of the gas ring pump is achieved in that cooling channels are provided for a jacket cooling on its housing and these cooling channels are connected to a coolant tank. The fact that the gas ring pump is connected to the cooling medium circuit of the rotary vane pump, you get by with a single cooler or heat exchanger for the Aggr gat.
Eine wesentliche Platz- und Materialersparnis wird dadurch er zielt, daß die Kühlmittelwege von Gasring- und Drehschieber- pumpe konstruktiv direkt miteinander verbunden sind.A significant space and material saving is achieved by the fact that the coolant paths of the gas ring and rotary vane pumps are directly connected to each other in terms of construction.
Durch die Zuordnung je eines eigenen, gegebenenfalls drehzahl regelbaren Antriebsmotors kann die Drehzahl jeder Pumpe optim den jeweils vorliegenden Betriebsverhältnissen angepaßt werde Bei der Verwendung nur eines Antriebsmotors für beide Pumpen lassen sich die für eine optimale Anpassung beider Pumpen ge¬ gebenenfalls notwendigen unterschiedlichen Drehzahlen dadurch erreichen, daß eine der beiden Pumpen mit dem Antriebsmotor direkt und die andere über einen Riementrieb oder ein Getrieb mit diesem gekuppelt ist.By assigning a separate, possibly speed-controllable drive motor, the speed of each pump can be optimally adapted to the prevailing operating conditions. If only one drive motor is used for both pumps, the different speeds necessary for optimal adaptation of the two pumps can be achieved, that one of the two pumps is directly coupled to the drive motor and the other is coupled to the latter via a belt drive or a gear.
Anhand eines in der Zeichnung dargestellten Ausführungsbeispi les wird der Anmeldungsgegenstand nachfolgend näher beschriebBased on a Ausführungsbeispi les shown in the drawing, the subject of the application is described in more detail below
Eine von einem eigenen Elektromotor 1 angetriebene Gasringpum 2 weist ein Ansaugrohr 3 auf, über das die Gasringpumpe 2 an einen in der Zeichnung nicht dargestellten, zu evakuierenden B hälter angeschlossen ist. Mit ihrem Auslaß 4 ist die Gasringpu pe 2 über ein Verbindungsrohr 5 an die Einlaßöffnung 6 einer Drehschieberpumpe 7 angeschlossen. Durch diese Drehschieberpu CT/EP89/00659A gas ring pump 2 driven by its own electric motor 1 has an intake pipe 3, via which the gas ring pump 2 is connected to a container (not shown in the drawing) to be evacuated. With its outlet 4, the Gasringpu pe 2 is connected via a connecting pipe 5 to the inlet opening 6 of a rotary vane pump 7. Through this rotary valve pu CT / EP89 / 00659
4 7 wird das durch die Gasringpumpe 2 vorverdichtete Medium weiter verdichtet und über die Auslaßöffnung 8 ausgestoßen.4 7, the medium pre-compressed by the gas ring pump 2 is further compressed and expelled through the outlet opening 8.
Durch die Vorschaltung einer Gasringpumpe 2 vor eine Drehschie- berpumpe 7 kann die Baugröße der auf Atmosphäre verdichtenden Drehschieberpumpe infolge der Vorverdichtung durch die Gasring¬ pumpe erheblich kleiner gewählt werden, wodurch die anfallende Schmierölmenge gegenüber einem nur aus Drehschieberpumpen be¬ stehenden mehrstufigen Vakuumpumpenaggregat wesentlich reduziert wird. Da die Gasringpumpe 2 im Verdichtungsraum vollkommen öl- frei arbeitet, entfällt auch die ansonsten für die Vorstufe not¬ wendige Ölmenge. Außerdem läßt sich eine Gasringpumpe mit nur einer Welle und ohne Getriebe kostengünstig mehrstufig bauen, so daß eine große Druckdifferenz, d.h. hohe Vorverdichtung, erziel- bar ist. Wegen der gegenüber Wälzkolbenpumpen um das zwei- bis dreifache größeren Spalten ist eine Gasringpumpe wesentlich unempfindlicher, wobei durch die Aufteilung auf mehrere Stufen die Spaltverluste nicht höher oder sogar geringer sind. Ferner ist die Gasringpumpe aufgrund ihrer Wirkungsweise (frei rotie- rendes Laufrad) in der zulässigen Drehzahl nur durch die Art des für das Laufrad verwendeten Materials begrenzt. Bei mehr¬ stufiger Ausführung der Gasringpumpe läßt sich darüber hinaus eine besonders gute und intensive Kühlung infolge der im Ver¬ gleich zu einer Wälzkolbenpumpe größeren-Oberfläche erzielen, was zu einer Verbesserung des Wirkungsgrades beiträgt.By connecting a gas ring pump 2 upstream of a rotary vane pump 7, the size of the rotary vane pump, which compresses to atmosphere, can be selected to be considerably smaller as a result of the pre-compression by the gas ring pump, as a result of which the amount of lubricating oil produced is significantly reduced compared to a multi-stage vacuum pump unit consisting only of rotary vane pumps . Since the gas ring pump 2 works completely oil-free in the compression chamber, the amount of oil otherwise required for the preliminary stage is also eliminated. In addition, a gas ring pump with only one shaft and without gear can be inexpensively built in multiple stages, so that a large pressure difference, i.e. high pre-compression, can be achieved. A gas ring pump is considerably less sensitive due to the fact that the gap is two to three times larger than Roots pumps, whereby the gap losses are not higher or even lower due to the division into several stages. Furthermore, due to its mode of operation (freely rotating impeller), the gas ring pump is only limited in the permissible speed by the type of material used for the impeller. With a multi-stage design of the gas ring pump, particularly good and intensive cooling can be achieved as a result of the larger surface area compared to a Roots pump, which contributes to an improvement in efficiency.
Es wurde ferner festgestellt, daß bei Ansaugdrücken unter 20 bar der Leistungs- und Kühlwasserbedarf der Gasringpumpe erheblich sinkt.It was also found that the power and cooling water requirements of the gas ring pump drop considerably at intake pressures below 20 bar.
Zur weiteren Verminderung der in der nachgeschalteten Drehschie¬ ber pumpe 7 anfallenden Schmierölmenge ist es vorteilhaft, mit einer Kühlung des durch die Gasringpumpe 2 geförderten Mediums zu arbeiten. Es besteht die Möglichkeit, zwischen der Gasring- pumpe 2 und der Drehschieberpumpe 7 einen Zwischenkühler 9 an- zuordnen, durch den das geförderte, vorverdichtete Medium ge¬ kühlt wird.To further reduce the amount of lubricating oil occurring in the downstream rotary slide pump 7, it is advantageous to work with a cooling of the medium conveyed by the gas ring pump 2. It is possible to connect an intercooler 9 between the gas ring pump 2 and the rotary vane pump 7. assign by which the delivered, pre-compressed medium is cooled.
Eine weitere vorteilhafte Kühlmöglichkeit stellt eine Einspritz- kühlung dar. Hierbei wird ein Kühlmittel in die Gasringpumpe 2 eingespritzt. Durch die Kühlung wird das von der nachgeschalte¬ ten Drehschieberpumpe 7 zu bewältigende Volumen des zu verdich- tetenden Mediums vermindert, so daß die nachgeschaltete Dreh¬ schieberpumpe 7 entsprechend kleiner ausgelegt werden kann.Injection cooling is a further advantageous cooling option. Here, a coolant is injected into the gas ring pump 2. The cooling of the volume of the medium to be compressed, which can be handled by the downstream rotary vane pump 7, is reduced, so that the subsequent rotary vane pump 7 can be designed correspondingly smaller.
Eine sehr intensive Kühlung des zu verdichtenden Mediums wird durch eine Mantelkühlung der Gasringpumpe 2 erreicht. Hierzu sind an dem Gehäuse der Gasringpumpe 2 Kühlkanäle 10 ausgebil¬ det, die von einer Kühlflüssigkeit durchströmt werden. Über Rohre 12 sind die Kühlkanäle 10 der Gasringpumpe 2 mit einem ebenfalls von der Kühlflüssigkeit durchströmten Kühlmantel 11 der Drehschieberpumpe 7 verbunden. Über weitere Rohrleitungen 12a und 12b sind die Kühlkanäle 10 der Gasringpumpe 2 mit dem einen Anschluß eines Kühlers 13 und der Kühlmantel 11 der Dreh- schieberpumpe 7 mit dem anderen Anschluß des Kühlers 13 verbun¬ den. Der Kühler 13 besitzt einen über einen Elektromotor 14 an¬ getriebenen Ventilator 15. Im Zuge der Rohrleitungen 12a bzw. 12b kann eine Umwälzpumpe 16 angeordnet werden.A very intensive cooling of the medium to be compressed is achieved by jacket cooling of the gas ring pump 2. For this purpose, cooling channels 10 are formed on the housing of the gas ring pump 2, through which a cooling liquid flows. The cooling channels 10 of the gas ring pump 2 are connected via pipes 12 to a cooling jacket 11 of the rotary vane pump 7 which also has the cooling liquid flowing through it. The cooling ducts 10 of the gas ring pump 2 are connected to one connection of a cooler 13 and the cooling jacket 11 of the rotary vane pump 7 to the other connection of the cooler 13 via further pipelines 12a and 12b. The cooler 13 has a fan 15 which is driven by an electric motor 14. A circulation pump 16 can be arranged in the course of the pipes 12a or 12b.
Bei dem Ausführuπgsbeispiel ist eine Reihenschaltung der Kühl¬ mittelkreise der beiden Pumpen 2 und 7 dargestellt. Es ist auch eine Parallelschaltung dieser Kühlkreise möglich. In beiden Fällen kommt man mit einem Kühler für die beiden Pumpen 2 und 7 aus, so daß der Bauaufwand kleingehalten wird.In the exemplary embodiment, a series connection of the coolant circuits of the two pumps 2 and 7 is shown. A parallel connection of these cooling circuits is also possible. In both cases, a cooler for the two pumps 2 and 7 is sufficient, so that the construction work is kept to a minimum.
Bei einer Mantelkühlung der Gasringpumpe 2 kann auf den Zwi¬ schenkühler 9 verzichtet werden. Eine Verminderung des Material¬ aufwandes ist auch dadurch möglich, daß die Drehschieberpumpe 7 mit ihrer Einlaßöffnung 6 direkt an den Auslaß 4 der Gasring- pumpe 2 angeschlossen wird. Dies ergibt außerdem eine gedrängte Bauweise des Verdichteraggregates. Die Ausrüstung jeder der beiden Pumpen 2 und 7 mit einem eigenen Antriebsmotor bietet die Möglichkeit einer optimalen Leistungs¬ steuerung, da jede Pumpe in ihrer Drehzahl so geregelt werden kann, daß sich optimale Verhältnisse einstellen. Bei der Gas- ringpumpe 2 wird ein optimaler Betrieb dadurch sichergestellt, daß die Drehzahl des ihr zugeordneten Elektromotors 1 so gere¬ gelt wird, daß die Stromaufnahme im gesamten Drehzahlbereich konstant bleibt. In the case of jacket cooling of the gas ring pump 2, there is no need for the intercooler 9. A reduction in the material expenditure is also possible by connecting the rotary vane pump 7 with its inlet opening 6 directly to the outlet 4 of the gas ring pump 2. This also results in a compact design of the compressor unit. Equipping each of the two pumps 2 and 7 with its own drive motor offers the possibility of optimal power control, since each pump's speed can be regulated in such a way that optimal conditions are established. With the gas ring pump 2, optimal operation is ensured by regulating the speed of the electric motor 1 assigned to it in such a way that the current consumption remains constant over the entire speed range.
Claims
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE3821437 | 1988-06-24 | ||
| DE3821437 | 1988-06-24 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| EP0420899A1 true EP0420899A1 (en) | 1991-04-10 |
Family
ID=6357218
Family Applications (2)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| EP89110607A Expired - Lifetime EP0347706B1 (en) | 1988-06-24 | 1989-06-12 | Multistage vacuum pump unit |
| EP89907120A Pending EP0420899A1 (en) | 1988-06-24 | 1989-06-12 | Multi-stage vacuum-pump set |
Family Applications Before (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| EP89110607A Expired - Lifetime EP0347706B1 (en) | 1988-06-24 | 1989-06-12 | Multistage vacuum pump unit |
Country Status (7)
| Country | Link |
|---|---|
| US (1) | US5244352A (en) |
| EP (2) | EP0347706B1 (en) |
| JP (1) | JPH0545827Y2 (en) |
| AT (1) | ATE75007T1 (en) |
| DE (1) | DE58901145D1 (en) |
| ES (1) | ES2030561T3 (en) |
| WO (1) | WO1989012751A1 (en) |
Families Citing this family (14)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP3386202B2 (en) * | 1993-09-08 | 2003-03-17 | 株式会社アルバック | Two-stage oil rotary vacuum pump |
| DK9300484U4 (en) * | 1993-11-02 | 1994-07-22 | Apv Rosista | Hygienic tanker pump and tanker fitted with one |
| DE19500823A1 (en) * | 1995-01-13 | 1996-07-18 | Sgi Prozess Technik Gmbh | Vacuum pumping station |
| DE19710098A1 (en) * | 1997-03-12 | 1998-09-17 | Paul Stehning Gmbh | Process for the production of recycled PET from flakes, as well as PET product produced by the process |
| US6692234B2 (en) * | 1999-03-22 | 2004-02-17 | Water Management Systems | Pump system with vacuum source |
| DE19929519A1 (en) * | 1999-06-28 | 2001-01-04 | Pfeiffer Vacuum Gmbh | Method for operating a multi-chamber vacuum system |
| DE102004010061B9 (en) * | 2004-03-02 | 2006-02-16 | Friedhelm Gevelhoff | Side channel rotary vane pump |
| DE102004038924B4 (en) * | 2004-03-02 | 2007-03-01 | Friedhelm Gevelhoff | Side channel rotary vane pump |
| US7033137B2 (en) | 2004-03-19 | 2006-04-25 | Ametek, Inc. | Vortex blower having helmholtz resonators and a baffle assembly |
| US20090142212A1 (en) * | 2007-12-03 | 2009-06-04 | Paul Xiubao Huang | Rotary blower with noise abatement jacket enclosure |
| FR2978214B1 (en) * | 2011-07-21 | 2013-08-16 | Adixen Vacuum Products | DRY TYPE MULTI-STAGE VACUUM PUMP |
| DE202012008133U1 (en) * | 2012-08-25 | 2013-11-27 | Oerlikon Leybold Vacuum Gmbh | vacuum pump |
| CN105756936A (en) * | 2016-04-29 | 2016-07-13 | 东莞市佛尔盛智能机电股份有限公司 | Gas ring type vacuum pump |
| CN118669343B (en) * | 2024-08-22 | 2024-10-25 | 中国空气动力研究与发展中心超高速空气动力研究所 | High-flow high-pressure ratio centrifugal vacuum pump unit |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE414133C (en) * | 1922-07-05 | 1925-05-23 | Der Maschinenfabriken Escher A | Multi-stage centrifugal compressor system |
| US2936107A (en) * | 1956-06-14 | 1960-05-10 | Nat Res Corp | High vacuum device |
| GB1248031A (en) * | 1967-09-21 | 1971-09-29 | Edwards High Vacuum Int Ltd | Two-stage rotary vacuum pumps |
| US3642384A (en) * | 1969-11-19 | 1972-02-15 | Henry Huse | Multistage vacuum pumping system |
| DE2138383A1 (en) * | 1971-07-31 | 1973-02-08 | Siemens Ag | PUMP UNIT FOR MULTI-STAGE COMPRESSION OF GASES |
| US3922110A (en) * | 1974-01-28 | 1975-11-25 | Henry Huse | Multi-stage vacuum pump |
| DE2430314C3 (en) * | 1974-06-24 | 1982-11-25 | Siemens AG, 1000 Berlin und 8000 München | Liquid ring vacuum pump with upstream compressor |
| US3956072A (en) * | 1975-08-21 | 1976-05-11 | Atlantic Fluidics, Inc. | Vapor distillation apparatus with two disparate compressors |
| JPS5267810A (en) * | 1975-12-03 | 1977-06-04 | Aisin Seiki Co Ltd | High vacuum pump |
| DE2614176A1 (en) * | 1976-04-02 | 1977-10-13 | Gutehoffnungshuette Sterkrade | MULTI-STAGE COMPRESSOR |
| DE2841906C2 (en) * | 1978-09-26 | 1980-02-21 | Siemens Ag, 1000 Berlin Und 8000 Muenchen | Liquid ring compressor or vacuum pump |
| US4588358A (en) * | 1984-07-02 | 1986-05-13 | Werner Rietschle Maschinen-Und Apparatebau Gmbh | Rotary vane evacuating pump |
| JPS62119946A (en) * | 1985-11-19 | 1987-06-01 | Mitsubishi Cable Ind Ltd | Manufacture of heat sink |
| DE3545982A1 (en) | 1985-12-23 | 1987-07-02 | Busch Gmbh K | ROTARY VALVE VACUUM PUMP |
| JPH0733834B2 (en) * | 1986-12-18 | 1995-04-12 | 株式会社宇野澤組鐵工所 | Inner partial-flow reverse-flow cooling multistage three-leaf vacuum pump in which the outer peripheral temperature of the housing with built-in rotor is stabilized |
| US5020969A (en) * | 1988-09-28 | 1991-06-04 | Hitachi, Ltd. | Turbo vacuum pump |
| FR2647853A1 (en) * | 1989-06-05 | 1990-12-07 | Cit Alcatel | DRY PRIMARY PUMP WITH TWO FLOORS |
| US5131817A (en) * | 1990-03-22 | 1992-07-21 | The Nash Engineering Company | Two-stage pumping system |
-
1989
- 1989-06-12 DE DE8989110607T patent/DE58901145D1/en not_active Expired - Lifetime
- 1989-06-12 US US07/635,148 patent/US5244352A/en not_active Expired - Fee Related
- 1989-06-12 EP EP89110607A patent/EP0347706B1/en not_active Expired - Lifetime
- 1989-06-12 EP EP89907120A patent/EP0420899A1/en active Pending
- 1989-06-12 AT AT89110607T patent/ATE75007T1/en not_active IP Right Cessation
- 1989-06-12 ES ES198989110607T patent/ES2030561T3/en not_active Expired - Lifetime
- 1989-06-12 JP JP1991600004U patent/JPH0545827Y2/ja not_active Expired - Lifetime
- 1989-06-12 WO PCT/EP1989/000659 patent/WO1989012751A1/en not_active Application Discontinuation
Non-Patent Citations (1)
| Title |
|---|
| See references of WO8912751A1 * |
Also Published As
| Publication number | Publication date |
|---|---|
| JPH0545827Y2 (en) | 1993-11-26 |
| EP0347706B1 (en) | 1992-04-15 |
| JPH03500007U (en) | 1991-12-05 |
| DE58901145D1 (en) | 1992-05-21 |
| ES2030561T3 (en) | 1992-11-01 |
| EP0347706A1 (en) | 1989-12-27 |
| ATE75007T1 (en) | 1992-05-15 |
| WO1989012751A1 (en) | 1989-12-28 |
| US5244352A (en) | 1993-09-14 |
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