EP1021653B1 - Cooled screw vacuum pump - Google Patents

Cooled screw vacuum pump Download PDF

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Publication number
EP1021653B1
EP1021653B1 EP98937514A EP98937514A EP1021653B1 EP 1021653 B1 EP1021653 B1 EP 1021653B1 EP 98937514 A EP98937514 A EP 98937514A EP 98937514 A EP98937514 A EP 98937514A EP 1021653 B1 EP1021653 B1 EP 1021653B1
Authority
EP
European Patent Office
Prior art keywords
rotor
pump according
pump
cooling
coolant
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
Application number
EP98937514A
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German (de)
French (fr)
Other versions
EP1021653A1 (en
Inventor
Rudolf Bahnen
Thomas Dreifert
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.)
Leybold GmbH
Original Assignee
Leybold Vakuum GmbH
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Filing date
Publication date
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Publication of EP1021653A1 publication Critical patent/EP1021653A1/en
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Anticipated expiration legal-status Critical
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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
    • 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
    • F04C23/001—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 similar working principle
    • 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
    • F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C18/14—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F04C18/16—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
    • 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
    • F04C2240/00—Components
    • F04C2240/50—Bearings
    • F04C2240/51—Bearings for cantilever assemblies

Definitions

  • the invention relates to a cooled screw vacuum pump with two rotating systems, each consist of a screw rotor and a shaft with a flying rotor bearing on every shaft has two spaced apart bearings, and with a cavity open on the bearing side in each rotor, in which is each a rotor internal cooling (see FR-A-1 290 239).
  • the amount of oil that the screw vacuum pump produces after State of the art passed through the cavity can be limited because in this cavity is not only the bearing but also the bearing bracket must become. There is therefore a risk of insufficient cooling of the pressure side area of the Screw vacuum pump, especially in this area Development of heat due to the compression work performed is greatest. Because of the existing cavity in the rotor is also the wall thickness of the rotor limited in the area of the bearing cavity. This succeeds es only at very high temperature gradients arising in the area of the screw threads on the pressure side Heat over the suction side area of the rotor, to drain the shaft and the cooling oil.
  • a high Temperature or insufficient cooling of the pressure side Range of a screw vacuum pump has to Consequence that there is uneven expansion of the rotors and thus to local game consumption between the rotors and between each of the rotors and the housing comes.
  • the rotors may start up relatively large games can be avoided.
  • Relatively large Games have a deterioration in pump characteristics result.
  • There is also the previously known Screw vacuum pump the risk of overheating of the bearing in the cavity, especially since it only can be lubricated with relatively warm oil. Finally can only use the known screw vacuum pump vertically arranged shafts are operated.
  • the present invention is based on the object a screw vacuum pump of the type mentioned to be equipped with improved cooling.
  • this object is achieved in that the bearing on the rotor side of the bearing outside the Cavity is located in the rotor.
  • the invention enables it, the rotor from the inside without obstruction by bearings and cool the bearing bracket effectively, so that the unwanted Game consumption especially in this critical Area no longer occur.
  • Each rotor expediently consists of two sections different thread profiles, the depth of the Thread of the pressure side section is smaller than the depth of the thread of the suction-side section. A smaller thread depth in the pressure side section creates more space for housing the cavity with the internal cooling.
  • Figure 1 shows a section through an embodiment for a screw vacuum pump 1 according to the invention, namely at the level of that of the two rotating ones Systems equipped with the drive motor 2 is. The synchronization of the two rotating systems takes place with the help of gear wheels 3.
  • the rotating systems housed in housing 4 are each comprised of the rotor 5 and the shaft 6. Each Rotor 5 is flying, that is, supported on one side.
  • the shaft 6 is supported by the bearings 7 and 8 as well as the bearing bracket 11 and 12 in the housing 4.
  • face side housing covers 13, 14 are provided, of which the rotor-side cover 13 with an inlet connector 15 is equipped.
  • Part of the transmission side Cover 14 is the bearing bracket 12.
  • the rotor 5 consists of two form-fitting with each other connected rotor sections 17, 18 with different Profiles 19, 20.
  • the suction-side rotor section 17 has a large-volume profile 19 to achieve high Volume flows in the helical scoop.
  • the pressure side section 18 of the rotor 5 has both a reduced profile volume as well as a lower one Diameter. This takes the cross section of the helical Scooping rooms. An inner compression will achieved, the compaction work reduced.
  • the inner wall of the housing 4 is the rotor gradation adjusted (gradation 21).
  • Gradation 21 The inner wall of the housing 4 is the rotor gradation adjusted (gradation 21).
  • dash-dotted line Line 22 indicates that the housing is at the height of the Gradation 21 can be formed divisible. This is it is possible to the suction-side rotor section 17 and suction-side part 4 'of the housing 4 by rotor sections with other profiles, lengths and / or diameters as well as adapted housing sections 4 ' replace the pump to different applications to be able to adapt.
  • the one following the pressure side end of the threads Outlet of the pump 1 is designated 24. It is led out to the side. Flows into the outlet also a housing bore 25 which the scoop in the height at which its cross-section - be it by gradation and / or by changing the thread profile - decreases, connects to the outlet. In the housing bore 25 there is a check valve 26, which is at overpressure opens in the scoop and the suction thread of rotor section 17 with outlet 24 shorts. For sealing the helical scoops shaft seals 27 are provided from the bearing, which is between the bearing 7 and the rotor section 18 are located.
  • the cooling system of the illustrated embodiment includes an internal rotor cooling and a casing jacket cooling.
  • the rotor is used to achieve internal rotor cooling 5 with a cavity open to its bearing side 31 equipped, which extends almost through the entire rotor 5 can extend.
  • the pressure side Section 18 is hollow.
  • the suction side Section 17 closes the suction end of the cavity 31.
  • the shaft 6, which is expedient with the rotor 5 or with the pressure-side section 18 of the rotor 5 is integrally formed, is also hollow (Cavity 32). Is in the cavities 31, 32 a central cooling tube 33, the bearing side of the Shaft 6 is brought out and on the rotor side just before suction-side end of the cavity 31 opens.
  • the cooling pipe 33 and that formed by the cooling pipe 33 and the hollow shaft 6 Annulus stand for the supply and discharge of a Coolant available.
  • the sump 37 and the line system 38 are designed such that the pump 1 shown in any position can be operated between vertical and horizontal. Coolant levels that are at horizontal and at Set the vertical position of pump 1 are shown.
  • the coolant pump 36 outside (as shown) or inside (e.g. on the second, invisible shaft of the pump 1 in height of the drive motor 2) of the housing 4 is located the opening 34 of the cooling tube 33 outside or inside the housing 4.
  • Coolant is used to operate the internal cooling of the rotor 5 from the coolant pump 36 from the coolant sump 37 via the cooling tube 33 into the cavity 31 in the rotor 5 promoted. From there it flows over the annulus between cooling pipe 33 and shaft 6 back into the swamp 37.
  • the cavity 31 is at the level of the pressure side Range of threads of pump 1 so that this area is effectively cooled.
  • the cross section of the annular space is expediently reduced between cooling pipe 33 and shaft 6 in the area of his pressure side end e.g. in that the cooling pipe 33 has a larger outside diameter in this area. This creates a narrow passage 39. This constriction ensures a complete filling of the coolant leading spaces.
  • cooling tube 3 It can be useful as a material for the cooling tube 3 a poorly heat-conducting material (e.g. plastic / stainless steel or the like.) This will a more effective cooling of the rotor 5 and a more uniform Temperature control of the pump components close to the shaft 1 reached.
  • a poorly heat-conducting material e.g. plastic / stainless steel or the like.
  • the housing jacket cooling shown includes cavities or channels in the housing 4. Provided in the area of the rotor 5 Cooling channels are at 41, in the area of the engine 2 located cooling channels designated 42.
  • the cooling channels 41 located in the area of the rotor 5 have the task, in particular, in the print side Area of the rotor 5 to dissipate heat generated. On the other hand, they should the housing 4 in height temper the entire rotor as evenly as possible. After all, they are supposed to replenish the heat absorbed hand in outside.
  • the cavities through which the coolant flows 41 therefore extend the full length of the rotor 5.
  • the housing cover 13 serves as a suction side Completion of the cavities 41. Also on the outlet side the housing 4 effectively cooled.
  • the cooling channels located at the level of the drive motor 2 42 also have the tasks described. she cause temperature control of the drive motor (winding side) and the bearing bracket 7. Finally they significantly increase the heat emission outer surfaces of the pump 1. This is useful at least at the level of the cooling channels 41 and 42 with ribs 44 equipped.
  • the cooling channels 41, 42 are supplied with coolant also with the help of the coolant pump 36, and via lines 45 and 46 if they are parallel should be flowed through. Depending on the thermal requirements there is also the possibility of using them one by one to supply with coolant. One of the lines 45 or 46 could then be omitted. About not shown in detail The coolant comes out of the holes Cavities 41, 42 back into the sump 37.
  • FIG. 1 In the exemplary embodiment shown in FIG. 1 are - as already mentioned - the housing 4 and the rotor 5 divisible at the level of line 22. Thereby there is the possibility of the suction-side sections of rotor 5 (section 17) and housing 4 (section 4 ') to be replaced by other components.
  • Pump 1 can be on Different applications can be customized by using rotor sections 17 with different profiles 19, different Length, different slope and / or different diameters, each together with an adapted housing section become. Different sized profiles can be placed on the Suction side to achieve high pumping speeds, various long profiles on the suction side to achieve this lower final pressures and / or different volume gradations to achieve e.g.
  • the coolant flowing through the screw vacuum pump 1 can water, oil (mineral oil, PTFE oil or the like) or some other liquid. Is expedient the use of oil to make bearings 7, 8 and to be able to lubricate the gears 3. A separate tour of coolant and lubricant as well as corresponding This eliminates the need for seals. It must only for a metered supply of oil to the bearings 7, 8 are taken care of.
  • the rotors 5 and the housing 4 made of relatively inexpensive aluminum materials consist.
  • the proposed cooling and above all cause uniform temperature control of pump 1, that it is even at different operating temperatures and relatively small columns not too local Game consumption comes up, one starting rotor to rotor and / or rotor on housing result.
  • a further reduction of the column is possible if for the inner, more thermally stressed components (Rotors, bearings, bearing brackets, gears) of the pump 1 Materials are used that have a smaller coefficient of thermal expansion have as the material for the less thermally stressed housing 4.
  • An example of one Material selection is steel (e.g. CrNi steel) for the internal components and aluminum for the housing.
  • Materials for the internal components can also be bronze, Brass or nickel silver are used.
  • the internal cooling comprises of the rotor 5, a cooling sleeve 51, which is supported on the bearing side on the housing 4 and in the cavity 31 protrudes.
  • the cooling bush 51 surrounds the shaft 6, which is no longer hollow, the cavity (31) and in the area of its suction end carries the rotor 5.
  • One or more cooling channels 52 are provided for coolant, which in a manner not shown in detail by the coolant pump 36 are supplied.
  • the gap 53 is between Cooling sleeve 51 and rotor 5 chosen as small as possible.
  • the bushing 51 with a thread 54 provided, the one directed towards the scoop Has pumping action. There are dirt particles present there thereby held back.
  • the gap 55 between the socket 51 and the shaft 6 is also relatively small to use the thread 56 on the inside the socket 51 to produce a pumping effect. It acts in the direction of seal 27 / bearing 7 and stops Oil particles away from the pumping chamber.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Description

Die Erfindung bezieht sich auf eine gekühlte Schraubenvakuumpumpe mit zwei rotierenden Systemen, die jeweils aus einem Schraubenrotor und einer Welle bestehen, mit einer fliegenden Rotor-Lagerung, die auf jeder Welle zwei voneinander beabstandete Lager aufweist, und mit einem lagerseitig offenen Hohlraum in jedem Rotor, in welchem sich jeweils eine Rotorinnenkühlung befindet (Siehe FR-A-1 290 239).The invention relates to a cooled screw vacuum pump with two rotating systems, each consist of a screw rotor and a shaft with a flying rotor bearing on every shaft has two spaced apart bearings, and with a cavity open on the bearing side in each rotor, in which is each a rotor internal cooling (see FR-A-1 290 239).

Bei einer bereits vorgeschlagenen Schraubenvakuumpumpe dieser Art befindet sich das rotorseitige Lager der fliegenden Lagerung innerhalb des zentralen, zur Lagerseite hin offenen Hohlraumes im Rotor. Die Kühlung erfolgt mit Hilfe von Schmieröl, das innerhalb eines zentralen Kanals in der Welle zunächst zum rotorseitigen Lager geführt wird. In an sich bekannter Weise ist die geförderte Ölmenge größer als es zur Schmierung der Lager notwendig ist, um möglichst viel Wärme abführen zu können.With a screw vacuum pump already proposed this type is the rotor-side bearing of the flying storage within the central, to the warehouse side open cavity in the rotor. The cooling takes place with the help of lubricating oil that is within a central Channel in the shaft first to the rotor side Camp is run. In a manner known per se The amount of oil extracted is greater than that used to lubricate the bearings is necessary to dissipate as much heat as possible can.

Die Ölmenge, die bei der Schraubenvakuumpumpe nach dem Stand der Technik durch den Hohlraum hindurchgeführt werden kann, ist begrenzt, da in diesem Hohlraum nicht nur das Lager sondern auch noch der Lagerträger untergebracht werden muss. Es besteht deshalb die Gefahr einer ungenügenden Kühlung des druckseitigen Bereichs der Schraubenvakuumpumpe, da gerade in diesem Bereich die Wärmeentwicklung auf Grund der geleisteten Kompressionsarbeit am größten ist. Wegen des vorhandenen Hohlraumes im Rotor ist außerdem die Wandstärke des Rotors im Bereich des Lager-Hohlraumes begrenzt. Dadurch gelingt esnur bei sehr hohen Temperaturgradienten, die gerade im druckseitigen Bereich der Schraubengänge entstehende Wärme über den saugseitigen Bereich des Rotors, die Welle und das Kühlöl abzuführen. Eine hohe Temperatur bzw. eine ungenügende Kühlung des druckseitigen Bereichs einer Schraubenvakuumpumpe hat zur Folge, dass es zu ungleichmäßigen Ausdehnungen der Rotoren und damit zu lokalen Spielaufzehrungen zwischen den Rotoren und zwischen jedem der Rotoren und dem Gehäuse kommt. Ein Anlaufen der Rotoren kann zwar durch relativ große Spiele vermieden werden. Relativ große Spiele haben jedoch eine Verschlechterung der Pumpeigenschaften zur Folge. Weiterhin besteht bei der vorbekannten Schraubenvakuumpumpe die Gefahr einer Überhitzung des im Hohlraum befindlichen Lagers, zumal es nur mit relativ warmem Öl geschmiert werden kann. Schließlich kann die vorbekannte Schraubenvakuumpumpe nur mit vertikal angeordneten Wellen betrieben werden.The amount of oil that the screw vacuum pump produces after State of the art passed through the cavity can be limited because in this cavity is not only the bearing but also the bearing bracket must become. There is therefore a risk of insufficient cooling of the pressure side area of the Screw vacuum pump, especially in this area Development of heat due to the compression work performed is greatest. Because of the existing cavity in the rotor is also the wall thickness of the rotor limited in the area of the bearing cavity. This succeeds es only at very high temperature gradients arising in the area of the screw threads on the pressure side Heat over the suction side area of the rotor, to drain the shaft and the cooling oil. A high Temperature or insufficient cooling of the pressure side Range of a screw vacuum pump has to Consequence that there is uneven expansion of the rotors and thus to local game consumption between the rotors and between each of the rotors and the housing comes. The rotors may start up relatively large games can be avoided. Relatively large Games, however, have a deterioration in pump characteristics result. There is also the previously known Screw vacuum pump the risk of overheating of the bearing in the cavity, especially since it only can be lubricated with relatively warm oil. Finally can only use the known screw vacuum pump vertically arranged shafts are operated.

Der vorliegenden Erfindung liegt die Aufgabe zugrunde, eine Schraubenvakuumpumpe der eingangs erwähnten Art mit einer verbesserten Kühlung auszurüsten.The present invention is based on the object a screw vacuum pump of the type mentioned to be equipped with improved cooling.

Erfindungsgemäß wird diese Aufgabe dadurch gelöst, dass sich das rotorseitige Lager der Lagerung außerhalb des Hohlraumes im Rotor befindet. Die Erfindung ermöglicht es, den Rotor von innen her ohne Behinderung durch Lager und Lagerträger wirksam zu kühlen, so dass die unerwünschten Spielaufzehrungen gerade in diesem kritischen Bereich nicht mehr auftreten.According to the invention, this object is achieved in that the bearing on the rotor side of the bearing outside the Cavity is located in the rotor. The invention enables it, the rotor from the inside without obstruction by bearings and cool the bearing bracket effectively, so that the unwanted Game consumption especially in this critical Area no longer occur.

Zweckmäßig besteht jeder Rotor aus zwei Abschnitten mit unterschniedlichen Gewindeprofilen, wobei die Tiefe des Gewindes des druckseitigen Abschnittes kleiner ist als die Tiefe des Gewindes des saugseitigen Abschnittes. Eine geringere Gewindetiefe im druckseitigen Abschnitt schafft mehr Platz für die Unterbringung des Hohlraumes mit der Innenkühlung.Each rotor expediently consists of two sections different thread profiles, the depth of the Thread of the pressure side section is smaller than the depth of the thread of the suction-side section. A smaller thread depth in the pressure side section creates more space for housing the cavity with the internal cooling.

Sind darüberhinaus Rotor und Gehäuse derart gestuft, dass der druckseitige Rotorabschnitt einen kleineren Durchmesser hat als der saugseitige Rotorabschnitt, so schafft diese Maßnahme mehr Platz im Gehäuse für die Unterbringung einer Mantelkühlung.If the rotor and housing are also stepped in such a way that the pressure side rotor section has a smaller one Has diameter than the suction side rotor section, so this measure creates more space in the case for the Housing a jacket cooling.

Nach einem weiteren Merkmal der Erfindung ist es zweckmäßig, zusätzlich in der Wandung des Gehäuses der Pumpe, und zwar zumindest in Höhe des Rotors, von einem Kühlmittel durchströmte Kanäle vorzusehen. Ein Kühlmantel dieser Art erlaubt es, insbesondere zusammen mit der erfindungsgemäßen Innenkühlung des Rotors, die gesamte Pumpe gleichmäßig zu temperieren. Sie kann dadurch bei unterschiedlichen Belastungen unterschiedliche Temperaturen annehmen, ohne dass es zu Spaltreduzierungen kommt. Zweckmäßig ist es, auch die Lager, die Lagerträger und den Antriebsmotor in eine solche Temperierung einzubeziehen, um Probleme durch unterschiedliche Temperaturdehnungen zu vermeiden. Eine Mantelkühlung der vorgeschlagenen Art hat schließlich noch den Vorteil, dass sie die Wirkung einer guten Schalldämmung hat.According to a further feature of the invention, it is expedient additionally in the wall of the housing Pump, at least at the level of the rotor, by one Provide channels through which coolant flows. A cooling jacket this type allows, especially together with the internal cooling of the rotor according to the invention, the entire Temper the pump evenly. It can different for different loads Accept temperatures without reducing gaps comes. It is expedient, also the camp that Bearing bracket and the drive motor in such a temperature control to involve problems through different Avoid thermal expansion. A jacket cooling the proposed species has finally Advantage that they have the effect of good sound insulation Has.

Weitere Vorteile und Einzelheiten der Erfindung sollen an Hand von in den Figuren 1 und 2 dargestellten Ausführungsbeispielen erläutert werden. Es zeigen

  • Figur 1 einen Schnitt durch eine Schraubenvakuumpumpe mit einer Kühlung nach der Erfindung und
  • Figur 2 einen Teilschnitt nach Figur 1 mit einer weiteren Ausführung für eine erfindungsgemäße Kühlung.
Further advantages and details of the invention will be explained with reference to the exemplary embodiments shown in FIGS. 1 and 2. Show it
  • 1 shows a section through a screw vacuum pump with a cooling according to the invention and
  • Figure 2 shows a partial section of Figure 1 with a further embodiment for a cooling according to the invention.

Figur 1 zeigt einen Schnitt durch ein Ausführungsbeispiel für eine Schraubenvakuumpumpe 1 nach der Erfindung, und zwar in Höhe desjenigen der beiden rotierenden Systeme, das mit dem Antriebsmotor 2 ausgerüstet ist. Die Synchronisation der beiden rotierenden Systeme erfolgt mit Hilfe von Zahnrädern 3.Figure 1 shows a section through an embodiment for a screw vacuum pump 1 according to the invention, namely at the level of that of the two rotating ones Systems equipped with the drive motor 2 is. The synchronization of the two rotating systems takes place with the help of gear wheels 3.

Die rotierenden Systeme, die im Gehäuse 4 untergebracht sind, umfassen jeweils den Rotor 5 und die Welle 6. Jeder Rotor 5 ist fliegend, das heisst, einseitig gelagert. Die Welle 6 stützt sich über die Lager 7 und 8 sowie die Lagerträger 11 und 12 im Gehäuse 4 ab. Stirnseitig sind Gehäusedeckel 13, 14 vorgesehen, von denen der rotorseitige Deckel 13 mit einem Einlassstutzen 15 ausgerüstet ist. Bestandteil des getriebeseitigen Deckels 14 ist der Lagerträger 12.The rotating systems housed in housing 4 are each comprised of the rotor 5 and the shaft 6. Each Rotor 5 is flying, that is, supported on one side. The shaft 6 is supported by the bearings 7 and 8 as well as the bearing bracket 11 and 12 in the housing 4. face side housing covers 13, 14 are provided, of which the rotor-side cover 13 with an inlet connector 15 is equipped. Part of the transmission side Cover 14 is the bearing bracket 12.

Der Rotor 5 besteht aus zwei formschlüssig miteinander verbundenen Rotorabschnitten 17, 18 mit unterschiedlichen Profilen 19, 20. Der saugseitige Rotorabschnitt 17 weist ein großvolumiges Profil 19 zur Erzielung hoher Volumenströme im wendelförmigen Schöpfraum auf. Der druckseitige Abschnitt 18 des Rotors 5 hat sowohl ein reduziertes Profilvolumen als auch einen geringeren Durchmesser. Dadurch nimmt der Querschnitt der wendelförmigen Schöpfräume ab. Eine innere Kompression wird erreicht, die Verdichtungsarbeit reduziert.The rotor 5 consists of two form-fitting with each other connected rotor sections 17, 18 with different Profiles 19, 20. The suction-side rotor section 17 has a large-volume profile 19 to achieve high Volume flows in the helical scoop. The pressure side section 18 of the rotor 5 has both a reduced profile volume as well as a lower one Diameter. This takes the cross section of the helical Scooping rooms. An inner compression will achieved, the compaction work reduced.

Die Innenwandung des Gehäuses 4 ist der Rotorabstufung angepasst (Abstufung 21). Durch eine strichpunktierte Linie 22 ist angedeutet, dass das Gehäuse in Höhe der Abstufung 21 teilbar ausgebildet sein kann. Dadurch ist es möglich, den saugseitigen Rotorabschnitt 17 und den saugseitigen Teil 4' des Gehäuses 4 durch Rotorabschnitte mit anderen Profilen, Längen und/oder Durchmessern sowie daran angepasste Gehäuseabschnitte 4' zu ersetzen, um die Pumpe an unterschiedliche Applikationen anpassen zu können.The inner wall of the housing 4 is the rotor gradation adjusted (gradation 21). Through a dash-dotted line Line 22 indicates that the housing is at the height of the Gradation 21 can be formed divisible. This is it is possible to the suction-side rotor section 17 and suction-side part 4 'of the housing 4 by rotor sections with other profiles, lengths and / or diameters as well as adapted housing sections 4 ' replace the pump to different applications to be able to adapt.

Der sich an das druckseitige Ende der Gewindegänge anschließende Auslass der Pumpe 1 ist mit 24 bezeichnet. Er ist seitlich herausgeführt. In den Auslass mündet außerdem eine Gehäusebohrung 25, die den Schöpfraum in der Höhe, in der sein Querschnitt - sei es durch Stufung und/oder durch Wechsel des Gewindeprofils - abnimmt, mit dem Auslass verbindet. In der Gehäusebohrung 25 befindet sich ein Rückschlagventil 26, das bei Überdrücken im Schöpfraum öffnet und den saugseitigen Gewindegang des Rotorabschnittes 17 mit dem Auslass 24 kurzschließt. Zur Abdichtung der wendelförmigen Schöpfräume von der Lagerung sind Wellendichtungen 27 vorgesehen, die sich zwischen dem Lager 7 und dem Rotorabschnitt 18 befinden.The one following the pressure side end of the threads Outlet of the pump 1 is designated 24. It is led out to the side. Flows into the outlet also a housing bore 25 which the scoop in the height at which its cross-section - be it by gradation and / or by changing the thread profile - decreases, connects to the outlet. In the housing bore 25 there is a check valve 26, which is at overpressure opens in the scoop and the suction thread of rotor section 17 with outlet 24 shorts. For sealing the helical scoops shaft seals 27 are provided from the bearing, which is between the bearing 7 and the rotor section 18 are located.

Das Kühlsystem der dargestellten Ausführungsform umfasst eine Rotorinnenkühlung und eine Gehäusemantelkühlung.The cooling system of the illustrated embodiment includes an internal rotor cooling and a casing jacket cooling.

Zur Verwirklichung der Rotorinnenkühlung ist der Rotor 5 mit einem zu seiner Lagerseite hin offenen Hohlraum 31 ausgerüstet, der sich nahezu durch den gesamten Rotor 5 erstrecken kann. Bei einem aus zwei Abschnitten 17 und 18 bestehenden Rotor 5 ist zweckmäßig der druckseitige Abschnitt 18 hohl ausgebildet. Der saugseitige Abschnitt 17 verschließt das saugseitige Ende des Hohlraumes 31. Die Welle 6, die zweckmäßig mit dem Rotor 5 bzw. mit dem druckseitigen Abschnitt 18 des Rotors 5 einstückig ausgebildet ist, ist ebenfalls hohl (Hohlraum 32). In den Hohlräumen 31, 32 befindet sich ein zentrales Kühlrohr 33, das lagerseitig aus der Welle 6 herausgeführt ist und rotorseitig kurz vor dem saugseitigen Ende des Hohlraumes 31 mündet. Das Kühlrohr 33 und der vom Kühlrohr 33 und der Hohlwelle 6 gebildete Ringraum stehen für die Zu- bzw. Abführung eines Kühlmittels zur Verfügung.The rotor is used to achieve internal rotor cooling 5 with a cavity open to its bearing side 31 equipped, which extends almost through the entire rotor 5 can extend. In one of two sections 17 and 18 existing rotor 5 is expediently the pressure side Section 18 is hollow. The suction side Section 17 closes the suction end of the cavity 31. The shaft 6, which is expedient with the rotor 5 or with the pressure-side section 18 of the rotor 5 is integrally formed, is also hollow (Cavity 32). Is in the cavities 31, 32 a central cooling tube 33, the bearing side of the Shaft 6 is brought out and on the rotor side just before suction-side end of the cavity 31 opens. The cooling pipe 33 and that formed by the cooling pipe 33 and the hollow shaft 6 Annulus stand for the supply and discharge of a Coolant available.

Beim dargestellten Ausführungsbeispiel steht die lagerseitige Öffnung 34 des Kühlrohres 3 über die Leitung 35 mit dem Auslass einer Kühlmittelpumpe 36 in Verbindung. Außerdem befindet sich im Bereich des Gehäusedeckels 14 ein Kühlmittelsumpf 37, der über das Leitungssystem 38 mit dem Einlass der Kühlmittelpumpe 36 verbunden ist. Der Sumpf 37 und das Leitungssystem 38 sind derart ausgebildet, dass die dargestellte Pumpe 1 in jeder Lage zwischen vertikal und horizontal betrieben werden kann. Kühlmittelstände, die sich bei horizontaler und bei vertikaler Lage der Pumpe 1 einstellen, sind dargestellt. Je nach dem, ob sich die Kühlmittelpumpe 36 außerhalb (wie dargestellt) oder innerhalb (z.B. auf der zweiten, nicht sichtbaren Welle der Pumpe 1 in Höhe des Antriebsmotors 2) des Gehäuses 4 befindet, liegt die Öffnung 34 des Kühlrohres 33 außerhalb oder innerhalb des Gehäuses 4.In the illustrated embodiment, the bearing side Opening 34 of cooling tube 3 via line 35 connected to the outlet of a coolant pump 36. It is also located in the area of the housing cover 14 a coolant sump 37, which via the line system 38 is connected to the inlet of the coolant pump 36. The sump 37 and the line system 38 are designed such that the pump 1 shown in any position can be operated between vertical and horizontal. Coolant levels that are at horizontal and at Set the vertical position of pump 1 are shown. Depending on whether the coolant pump 36 outside (as shown) or inside (e.g. on the second, invisible shaft of the pump 1 in height of the drive motor 2) of the housing 4 is located the opening 34 of the cooling tube 33 outside or inside the housing 4.

Zum Betrieb der Innenkühlung des Rotors 5 wird Kühlmittel von der Kühlmittelpumpe 36 aus dem Kühlmittelsumpf 37 über das Kühlrohr 33 in den Hohlraum 31 im Rotor 5 gefördert. Von dort aus strömt es über den Ringraum zwischen Kühlrohr 33 und Welle 6 zurück in den Sumpf 37. Der Hohlraum 31 befindet sich in Höhe des druckseitigen Bereichs der Gewindegänge der Pumpe 1, so dass gerade dieser Bereich wirksam gekühlt wird. Das außerhalb des Kühlrohres 33 zurückströmende Kühlmittel temperiert u.a. die Hohlwelle 6, die Lager 7 und 8, den Antriebsmotor 2 (ankerseitig) und die Zahnräder 3, so dass Wärmedehnungsprobleme reduziert sind. Coolant is used to operate the internal cooling of the rotor 5 from the coolant pump 36 from the coolant sump 37 via the cooling tube 33 into the cavity 31 in the rotor 5 promoted. From there it flows over the annulus between cooling pipe 33 and shaft 6 back into the swamp 37. The cavity 31 is at the level of the pressure side Range of threads of pump 1 so that this area is effectively cooled. The outside of the cooling pipe 33, coolant flowing back et al the hollow shaft 6, the bearings 7 and 8, the Drive motor 2 (anchor side) and the gears 3, see above that thermal expansion problems are reduced.

Zweckmäßig verringert sich der Querschnitt des Ringraumes zwischen Kühlrohr 33 und Welle 6 im Bereich seines druckseitigen Endes z.B. dadurch, dass das Kühlrohr 33 in diesem Bereich einen größeren Außendurchmesser hat. Dadurch entsteht ein verengter Durchlass 39. Diese Engstelle sichert eine vollständige Füllung der das Kühlmittel führenden Räume.The cross section of the annular space is expediently reduced between cooling pipe 33 and shaft 6 in the area of his pressure side end e.g. in that the cooling pipe 33 has a larger outside diameter in this area. This creates a narrow passage 39. This constriction ensures a complete filling of the coolant leading spaces.

Es kann zweckmäßig sein, als Werkstoff für das Kühlrohr 3 ein schlecht wärmeleitendes Material (z.B. Kunststoff/Edelstahl o. dgl.) auszuwählen. Dadurch werden eine wirksamere Kühlung des Rotors 5 und eine gleichmäßige Temperierung der wellennahen Bauteile der Pumpe 1 erreicht.It can be useful as a material for the cooling tube 3 a poorly heat-conducting material (e.g. plastic / stainless steel or the like.) This will a more effective cooling of the rotor 5 and a more uniform Temperature control of the pump components close to the shaft 1 reached.

Die dargestellte Gehäusemantelkühlung umfasst Hohlräume bzw. Kanäle im Gehäuse 4. Im Bereich des Rotors 5 vorgesehene Kühlkanäle sind mit 41, im Bereich des Motors 2 befindliche Kühlkanäle mit 42 bezeichnet.The housing jacket cooling shown includes cavities or channels in the housing 4. Provided in the area of the rotor 5 Cooling channels are at 41, in the area of the engine 2 located cooling channels designated 42.

Die im Bereich des Rotors 5 befindlichen Kühlkanäle 41 haben zum einen die Aufgabe, die insbesondere im druckseitigen Bereich des Rotors 5 entstehende Wärme abzuführen. Zum anderen sollen sie das Gehäuse 4 in Höhe des gesamten Rotors möglichst gleichmäßig temperieren. Schließlich sollen sie die aufgenommene Wärme nach außen abgeben. Die vom Kühlmittel durchströmten Hohlräume 41 erstrecken sich deshalb über die volle Länge des Rotors 5. Der Gehäusedeckel 13 dient als saugseitiger Abschluss der Hohlräume 41. Auch auslassseitig ist das Gehäuse 4 wirksam gekühlt.The cooling channels 41 located in the area of the rotor 5 have the task, in particular, in the print side Area of the rotor 5 to dissipate heat generated. On the other hand, they should the housing 4 in height temper the entire rotor as evenly as possible. After all, they are supposed to replenish the heat absorbed hand in outside. The cavities through which the coolant flows 41 therefore extend the full length of the rotor 5. The housing cover 13 serves as a suction side Completion of the cavities 41. Also on the outlet side the housing 4 effectively cooled.

Die in Höhe des Antriebsmotors 2 befindlichen Kühlkanäle 42 haben ebenfalls die geschilderten Aufgaben. Sie bewirken eine Temperierung des Antriebsmotors (wicklungsseitig) sowie des Lagerträgers 7. Schließlich vergrößern sie im erheblichen Maße die Wärmeabgabe über äußere Oberflächen der Pumpe 1. Zweckmäßig ist diese zumindest in Höhe der Kühlkanäle 41 und 42 mit Rippen 44 ausgerüstet.The cooling channels located at the level of the drive motor 2 42 also have the tasks described. she cause temperature control of the drive motor (winding side) and the bearing bracket 7. Finally they significantly increase the heat emission outer surfaces of the pump 1. This is useful at least at the level of the cooling channels 41 and 42 with ribs 44 equipped.

Die Versorgung der Kühlkanäle 41, 42 mit Kühlmittel erfolgt ebenfalls mit Hilfe der Kühlmittelpumpe 36, und zwar über die Leitungen 45 und 46, wenn sie parallel durchströmt sein sollen. Je nach den thermischen Anforderungen besteht auch die Möglichkeit, sie nacheinander mit Kühlmittel zu versorgen. Eine der Leitungen 45 oder 46 könnte dann entfallen. Über im einzelnen nicht dargestellte Bohrungen gelangt das Kühlmittel aus den Hohlräumen 41, 42 in den Sumpf 37 zurück.The cooling channels 41, 42 are supplied with coolant also with the help of the coolant pump 36, and via lines 45 and 46 if they are parallel should be flowed through. Depending on the thermal requirements there is also the possibility of using them one by one to supply with coolant. One of the lines 45 or 46 could then be omitted. About not shown in detail The coolant comes out of the holes Cavities 41, 42 back into the sump 37.

Bei vertikaler Anordnung der Welle 6 übernimmt das im Sumpf befindliche Kühlmittel die Temperierung des in den Sumpf 37 hineinragenden Lagerträgers 12. Bei horizontaler Anordnung ist es zweckmäßig, das zurückströmende Kühlmittel über die Innenseite des Deckels 14 strömen zu lassen, um sowohl den Lagersitz 12 zu temperieren als auch die Wärmeabgabe nach außen zu verbessern.With a vertical arrangement of the shaft 6 in the Coolant located in the sump tempering the the sump 37 protruding bearing bracket 12. With horizontal The arrangement is expedient, the backflow Coolant through the inside of cover 14 to flow to both temper the bearing seat 12 as well as to improve the heat emission to the outside.

Beim dargestellten Ausführungsbeispiel nach Figur 1 sind - wie bereits erwähnt - das Gehäuse 4 und der Rotor 5 in Höhe der Linie 22 teilbar ausgebildet. Dadurch besteht die Möglichkeit, die saugseitigen Abschnitte von Rotor 5 (Abschnitt 17) und Gehäuse 4 (Abschnitt 4') durch andere Bauteile zu ersetzen. Die Pumpe 1 kann an verschiedene Applikationen angepasst werden, indem Rotorabschnitte 17 mit unterschiedlichen Profilen 19, unterschiedlicher Länge, unterschiedlicher Steigung und/oder unterschiedlichem Durchmesser, jeweils zusammen mit einem angepassten Gehäuseabschnitt, montiert werden. Es können verschieden große Profile auf der Saugseite zur Erreichung hoher Saugvermögen, verschieden lange Profile auf der Saugseite zur Erreichung niedriger Enddrücke und/oder verschiedene Volumenabstufungen zur Erreichung z.B. bei geringerer Abstufung eine höhere Fluidverträglichkeit oder bei höherer Stufung ein hohes Saugvermögen bei relativ kleiner Leistungsaufnahme ausgewählt werden. Schließlich besteht die Möglichkeit, in Höhe einer Reduzierung des Durchmessers des Rotors 5 eine Umfangsnut vorzusehen, um bei bestimmten Applikationen in diesem Bereich eine Druckentlastung zu erzielen.In the exemplary embodiment shown in FIG. 1 are - as already mentioned - the housing 4 and the rotor 5 divisible at the level of line 22. Thereby there is the possibility of the suction-side sections of rotor 5 (section 17) and housing 4 (section 4 ') to be replaced by other components. Pump 1 can be on Different applications can be customized by using rotor sections 17 with different profiles 19, different Length, different slope and / or different diameters, each together with an adapted housing section become. Different sized profiles can be placed on the Suction side to achieve high pumping speeds, various long profiles on the suction side to achieve this lower final pressures and / or different volume gradations to achieve e.g. with a lower gradation one higher fluid compatibility or higher grading high pumping speed with relatively low power consumption to be selected. Finally, there is Possibility of reducing the diameter the rotor 5 to provide a circumferential groove to certain Applications in this area relieve pressure to achieve.

Das die Schraubenvakuumpumpe 1 durchströmende Kühlmittel kann Wasser, Öl (Mineralöl, PTFE-Öl oder dergleichen) oder eine andere Flüssigkeit sein. Zweckmäßig ist die Verwendung von Öl, um damit auch die Lager 7, 8 und die Zahnräder 3 schmieren zu können. Eine separate Führung von Kühlmittel und Schmiermittel sowie entsprechende Abdichtungen können dadurch entfallen. Es muss lediglich für eine dosierte Zuführung von Öl zu den Lagern 7, 8 gesorgt werden.The coolant flowing through the screw vacuum pump 1 can water, oil (mineral oil, PTFE oil or the like) or some other liquid. Is expedient the use of oil to make bearings 7, 8 and to be able to lubricate the gears 3. A separate tour of coolant and lubricant as well as corresponding This eliminates the need for seals. It must only for a metered supply of oil to the bearings 7, 8 are taken care of.

Die beschriebenen Lösungen erlauben eine vorteilhafte Werkstoffauswahl. Beispielsweise können die Rotoren 5 und das Gehäuse 4 aus relativ preiswerten Aluminiumwerkstoffen bestehen. Die vorgeschlagene Kühlung und vor allem gleichmäßige Temperierung der Pumpe 1 bewirken, dass es selbst bei unterschiedlichen Betriebstemperaturen und relativ kleinen Spalten nicht zu lokalen Spielaufzehrungen kommt, die ein Anlaufen Rotor an Rotor und/oder Rotor an Gehäuse zur Folge haben. Eine weitere Reduzierung der Spalte ist möglich, wenn für die inneren, thermisch höher belasteten Bauteile (Rotoren, Lager, Lagerträger, Zahnräder) der Pumpe 1 Werkstoffe eingesetzt werden, die einen kleineren Wärmeausdehnungskoeffizienten haben als der Werkstoff für das weniger thermisch belastete Gehäuse 4. Eine Vergleichsmäßigung der Dehnung aller Bauteile der Pumpe 1 wird dadurch erreicht. Ein Beispiel für eine solche Werkstoffauswahl ist Stahl (z.B. CrNi-Stahl) für die inneren Bauteile und Aluminium für das Gehäuse. Als Werkstoffe für die inneren Bauteile können auch Bronze, Messing oder Neusilber dienen.The solutions described allow an advantageous one Material selection. For example, the rotors 5 and the housing 4 made of relatively inexpensive aluminum materials consist. The proposed cooling and above all cause uniform temperature control of pump 1, that it is even at different operating temperatures and relatively small columns not too local Game consumption comes up, one starting rotor to rotor and / or rotor on housing result. A further reduction of the column is possible if for the inner, more thermally stressed components (Rotors, bearings, bearing brackets, gears) of the pump 1 Materials are used that have a smaller coefficient of thermal expansion have as the material for the less thermally stressed housing 4. A comparison the expansion of all components of the pump 1 is achieved. An example of one Material selection is steel (e.g. CrNi steel) for the internal components and aluminum for the housing. As Materials for the internal components can also be bronze, Brass or nickel silver are used.

Beim Ausführungsbeispiel nach Figur 2 umfasst die Innenkühlung des Rotors 5 eine Kühlbuchse 51, die sich lagerseitig auf dem Gehäuse 4 abstützt und in den Hohlraum 31 hineinragt. Die Kühlbuchse 51 umgibt die Welle 6, die nicht mehr hohl ausgebildet ist, den Hohlraum (31) durchsetzt und im Bereich ihres saugseitigen Endes den Rotor 5 trägt. Zur Versorgung der Kühlbuchse 51 mit Kühlmittel sind ein oder mehrere Kühlkanäle 52 vorgesehen, die in im einzelnden nicht dargestellter Weise von der Kühlmittelpumpe 36 versorgt werden.In the exemplary embodiment according to FIG. 2, the internal cooling comprises of the rotor 5, a cooling sleeve 51, which is supported on the bearing side on the housing 4 and in the cavity 31 protrudes. The cooling bush 51 surrounds the shaft 6, which is no longer hollow, the cavity (31) and in the area of its suction end carries the rotor 5. To supply the cooling bush 51 with One or more cooling channels 52 are provided for coolant, which in a manner not shown in detail by the coolant pump 36 are supplied.

Um zu erreichen, dass die Kühlbuchse 51 möglichst viel Wärme vom Rotor 5 aufnimmt, ist der Spalt 53 zwischen Kühlbuchse 51 und Rotor 5 möglichst klein gewählt. In diesem Bereich ist die Buchse 51 mit einem Gewinde 54 versehen, das eine in Richtung Schöpfraum gerichtete Pumpwirkung hat. Dort vorhandene Schmutzteilchen werden dadurch zurückgehalten.To achieve that the cooling sleeve 51 as much as possible Receives heat from the rotor 5, the gap 53 is between Cooling sleeve 51 and rotor 5 chosen as small as possible. In this area is the bushing 51 with a thread 54 provided, the one directed towards the scoop Has pumping action. There are dirt particles present there thereby held back.

Auch der Spalt 55 zwischen Buchse 51 und Welle 6 ist relativ klein, um mit Hilfe des Gewindes 56 auf der Innenseite der Buchse 51 eine Pumpwirkung zu erzeugen. Sie wirkt in Richtung Dichtung 27 / Lager 7 und hält Ölpartikel vom Schöpfraum fern.The gap 55 between the socket 51 and the shaft 6 is also relatively small to use the thread 56 on the inside the socket 51 to produce a pumping effect. It acts in the direction of seal 27 / bearing 7 and stops Oil particles away from the pumping chamber.

Claims (21)

  1. A cooled screw vacuum pump (1) with two rotating systems (5, 6) which each consist of a screw rotor (5) and a shaft (6), with an overhung rotor support which comprises on each shaft two bearings (7, 8) which are spaced from one another, and with a cavity (31) in each rotor (5) which is open on the bearing side and within each of which there is located an internal rotor-cooling arrangement, characterised in that the rotor-side bearing (7) of the support is located outside the cavity (31) within the rotor (5).
  2. Pump according to Claim 1, characterised in that each rotor (5) consists of two segments (17, 18) with different thread profiles (19, 20) and in that the depth of the thread (20) of the pressure-side segment (18) is less than the depth of the thread (19) of the suction-side segment (17).
  3. Pump according to Claim 1 or 2, characterised in that each rotor (5) is of stepped design such that the pressure-side segment (18) of the rotor (5) has a smaller diameter than the suction-side segment (17).
  4. Pump according to Claim 1, 2 or 3, characterised in that the cavity (31) extends through almost the entire rotor (5).
  5. Pump according to Claim 1, 2 or 3, characterised in that the rotor (5) consists of two segments (17, 18), in that the pressure-side segment (18) is of hollow design and in that the hollow interior space of the rotor segment (18) together with the segment (17) which is fitted as a termination on the suction side form the cavity (31) which is open on the bearing side.
  6. Pump according to Claim 4 or 5, characterised in that the shaft (6) is of hollow design and is connected outside the cavity (31) to the rotor (5) or to the pressure-side segment (18) thereof.
  7. Pump according to Claim 6, characterised in that the hollow shaft (6) and the rotor (5) or the pressure-side segment (18) thereof are of integral design.
  8. Pump according to Claim 6 or 7, characterised in that a fixed cooling pipe (33) passing through the hollow shaft (6) discharges within the cavity (31).
  9. Pump according to Claim 8, characterised in that the cooling pipe (33) serves for the supply of coolant to the cavity (31) and in that the annular space between the hollow shaft (6) and the cooling pipe (33) serves for the discharge of coolant.
  10. Pump according to Claim 9, characterised in that a constriction (39) is provided in the region of the bearing-side end of the annular space between the hollow shaft (6) and the cooling pipe (33).
  11. Pump according to Claim 8, 9 or 10, characterised in that the cooling pipe (33) consists of a material that is a poor conductor of heat.
  12. Pump according to one of Claims 1 to 5, characterised in that the shaft (6) passes through the cavity (31) and in that a cooling bushing (51) supported on the housing (4) projects into the annular space between the shaft (6) and the rotor (5) or the rotor segment (18).
  13. Pump according to Claim 11, characterised in that the cooling bushing (51) is provided with channels (52) through which a coolant flows.
  14. Pump according to Claim 12 or 13, characterised in that the cooling bushing (51) is provided with an external thread (54) having a pumping action directed in the direction of a compression chamber.
  15. Pump according to Claim 12, 13 or 14, characterised in that the cooling bushing (51) is provided with an internal thread (56) having a pumping action directed in the direction of the bearing (7).
  16. Pump according to one of the preceding claims, characterised in that channels (41) through which a coolant flows are provided in the wall of the housing (4) of the pump (1), specifically in the region of the rotor (5).
  17. Pump according to Claim 16, characterised in that channels (42) through which the coolant flows are also provided in the bearing-side region of the housing (4).
  18. Pump according to one of the preceding claims, characterised in that a coolant pump (36) is present, the inlet of which is connected via a system of pipes (38) to a coolant sump (37) located in the pump housing (4) and the outlet of which is connected to the cooling pipe (33) or to the channels (52) in the cooling bushing (51) or to the channels (41) and/- or (42) in the housing (4).
  19. Pump according to Claim 18, characterised in that sump (37) the system of pipes (38) is designed in such a way that the inlet of the coolant pump (36) is connected to the sump (37) both in the horizontal position and in the vertical position of the pump (1).
  20. Pump according to one of the preceding claims, characterised in that the coolant flowing through the pump (1) is identical with the lubricant for the bearings (7, 8).
  21. Pump according to one of the preceding claims, characterised in that a housing bore (26) is provided which connects the helical compression chambers in the region in which their cross-section decreases - be it by gradation and/or by changing the thread profile - to the outlet (27) and within which a check valve is located which opens in the event of excess pressure.
EP98937514A 1997-10-10 1998-06-19 Cooled screw vacuum pump Expired - Lifetime EP1021653B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19745616 1997-10-10
DE19745616A DE19745616A1 (en) 1997-10-10 1997-10-10 Cooling system for helical vacuum pump
PCT/EP1998/003756 WO1999019630A1 (en) 1997-10-10 1998-06-19 Cooled screw vacuum pump

Publications (2)

Publication Number Publication Date
EP1021653A1 EP1021653A1 (en) 2000-07-26
EP1021653B1 true EP1021653B1 (en) 2002-08-07

Family

ID=7845648

Family Applications (1)

Application Number Title Priority Date Filing Date
EP98937514A Expired - Lifetime EP1021653B1 (en) 1997-10-10 1998-06-19 Cooled screw vacuum pump

Country Status (7)

Country Link
US (1) US6544020B1 (en)
EP (1) EP1021653B1 (en)
JP (1) JP4225686B2 (en)
KR (1) KR100517788B1 (en)
DE (2) DE19745616A1 (en)
TW (1) TW430722B (en)
WO (1) WO1999019630A1 (en)

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DE59805126D1 (en) 2002-09-12
US6544020B1 (en) 2003-04-08
EP1021653A1 (en) 2000-07-26
TW430722B (en) 2001-04-21
DE19745616A1 (en) 1999-04-15
JP2001520352A (en) 2001-10-30
KR100517788B1 (en) 2005-09-30
WO1999019630A1 (en) 1999-04-22
JP4225686B2 (en) 2009-02-18

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