EP1957797B1 - Helical screw compressor comprising a cooling jacket - Google Patents

Helical screw compressor comprising a cooling jacket Download PDF

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Publication number
EP1957797B1
EP1957797B1 EP06754260.5A EP06754260A EP1957797B1 EP 1957797 B1 EP1957797 B1 EP 1957797B1 EP 06754260 A EP06754260 A EP 06754260A EP 1957797 B1 EP1957797 B1 EP 1957797B1
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EP
European Patent Office
Prior art keywords
cooling
housing
rotor housing
screw compressor
wall
Prior art date
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EP06754260.5A
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German (de)
French (fr)
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EP1957797A1 (en
Inventor
Carsten Achtelik
Dieter HÜTTERMANN
Michael Besseling
Norbert Henning
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GHH Rand Schraubenkompressoren GmbH
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GHH Rand Schraubenkompressoren GmbH
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Publication of EP1957797A1 publication Critical patent/EP1957797A1/en
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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
    • F04C18/08—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
    • F04C18/082—Details specially related to intermeshing engagement type pumps
    • F04C18/084—Toothed wheels
    • 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
    • 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
    • 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
    • F04C2220/00—Application
    • F04C2220/40—Pumps with means for venting areas other than the working chamber, e.g. bearings, gear chambers, shaft seals

Definitions

  • the invention relates to a screw compressor having a rotor housing, in which two screw rotors which mesh with helical ribs and groove are rotatably mounted parallel axis, and with a surrounding the rotor housing at a distance cooling housing which forms a cooling space together with the rotor housing and at least one inlet opening and an outlet opening for a refrigerant flowing through the cooling space.
  • a screw compressor of this kind is z. B. off DE 201 10 360.5 U1 known as part of a two-stage screw compressor.
  • the invention is particularly applicable to a screw compressor which is a gaseous medium such.
  • a gaseous medium such as air, at very high pressures, in the range of 30 to 50 bar, in particular about 40 bar, compressed and which may be in particular the high pressure stage of a two- or multi-stage compressor unit.
  • the compression to very high pressures is associated with a strong heating of the gaseous medium, so that a particularly effective cooling is desirable.
  • the coolant in the cooling space flows around the outer surface of the rotor housing in the circumferential direction over almost 360 °. Furthermore, the coolant is deflected sharply when flowing into the cooling space and before the outflow respectively at the dividing wall connecting the rotor housing to the cooling jacket. It has been found that is achieved here by a very intense cooling effect, especially in the region of the acting like a cooling fin partition.
  • the in FIG. 1 shown screw compressor has a rotor housing 1 shown in section, in which two rotors 3 and 5 are mounted rotatable parallel axis.
  • the axes of rotation of the rotors 3, 5 lie in a common vertical plane, which is also the cutting plane for the representation of the rotor housing 1.
  • Each rotor has a profile section 7 and 9, which has a profile with helically extending ribs or grooves, wherein the ribs and grooves of the two profile sections 7, 9 engage in a non-contact meshing and sealing engagement.
  • At the profile sections 7, 9 close to both sides shaft journals 7a, 7b, 9a, 9b, with the peripheral surface seal assemblies 11, 12 cooperate to seal the rotor in the rotor housing 1.
  • the shaft journals 7a, 7b, 9a, 9b are also rotatably supported by bearings 13, 15 in the rotor housing 1.
  • the in FIG. 1 upper rotor 3 is the main rotor and has at its in FIG. 1 left end of an extension 7c of its shaft journal, which serves to receive a drive gear (not shown), which meshes with a corresponding gear of a drive gear (not shown) to drive the rotor 3 for rotation.
  • a drive gear not shown
  • a corresponding gear of a drive gear not shown
  • screw compressor When operating the in FIG. 1 shown screw compressor is its suction chamber 10, which at the in FIG. 1 left end of the profile sections 7 and 9 formed in the rotor housing 1 and connected to a (not shown) intake, the gas to be compressed, in particular air, supplied.
  • the supplied gas is already precompressed by one or more upstream compressor stages (not shown) to an intermediate pressure, for example to a pressure in the range of 10 to 15 bar, preferably about 12 bar.
  • This precompressed gas is through the profile sections 7, 9 of the two rotors 3, 5 in FIG. 1 conveyed to the right and thereby compressed to a final pressure, which is preferably in the range of 30 to 50 bar, in particular at about 40 bar.
  • the compressed gas leaves the rotor housing 1 at the in FIG. 1 right, pressure-side end of the profile sections 7, 9 through an outlet (not shown).
  • the rotor housing 1 is surrounded by a cooling jacket or cooling housing 21, which is formed predominantly in one piece with the rotor housing 1 and surrounds this at a distance.
  • the cooling housing 21 has large-area openings, which are closed by means of a cover plate 23 and a bottom plate 25, which are fastened by screws.
  • FIG. 2 shows schematically and simplified a cross section approximately along the line II - II of FIG. 1 ,
  • the rotor housing 1 for receiving the (not shown) screw rotors is surrounded by the cooling jacket or cooling housing 21, the side walls 21a, 21b are preferably formed integrally with the rotor housing 1 and which closed at the top and bottom by the top wall 23 and bottom plate 25 is.
  • the cooling housing 21 forms, together with the rotor housing 1, a cooling space 27 which surrounds the rotor housing 1 essentially completely annularly and which is interrupted only at one point by a partition wall 29 connecting the rotor housing 1 to the side wall 21b of the cooling housing 21.
  • the partition wall 29 extends horizontally approximately at half the height between the center axis M1 M2 of the vertically superposed screw rotors.
  • the cooling housing 21 has an inlet opening 31 and an outlet opening 33 for cooling fluid, for. As cooling water or oil on.
  • the inlet opening 31 opens into a vertically upwardly extending inlet channel 35, the upper outlet opening 35 'facing the underside of the partition wall 29 at a distance.
  • Upstream of the outlet opening 33 is a vertical outflow channel 37, the lower inlet opening 37 'of the top of the partition 29 faces with a small distance.
  • the black arrows in FIG. 2 indicate the flow path of the coolant supplied to the inlet port 31. This is perpendicular by the inflow passage 35 directed upward against the underside of the partition wall 29, deflected at this sharply and then flows down and in Fig. 2 in a clockwise direction around the entire circumference of the rotor housing 1 until it impinges on the upper side of the partition wall 29, is deflected sharply upward by the latter and is withdrawn through the outflow channel 37 and the outlet opening 33.
  • a vent opening 41 formed with a small cross-section. Through this vent opening 41 can escape when filling the cooling chamber 27 with coolant air, as in FIG. 2 indicated by the upper dotted arrows, so that the cooling space 27 up to the height of the vent opening 41, ie up to the in FIG. 2 can be filled by the line 43 indicated liquid level, and the volume of the liquid is trapped above the liquid level 43 residual air is very low.
  • a percolation opening 47 of very small cross-section In the inflow channel 35 separating from the cooling chamber 27 wall 45 is formed at the level of the lower boundary of the inlet opening 31, a percolation opening 47 of very small cross-section.
  • cooling liquid can drain through the seepage opening 47 and the inlet opening 31 (as indicated by the lower dotted arrows in FIG FIG. 2 indicated), until the coolant level in the cooling chamber 27 has reached the height of the seepage opening 47, ie, has dropped to the level indicated by the line 49.
  • the remaining amount of cooling liquid remaining upon emptying of the cooling space 27 below the line 49 is therefore very small.
  • FIG. 3 shows further details of the screw compressor referring to the in FIG. 1 shown seal assemblies 11 for sealing the pressure-side shaft journals 7b, 9b of the rotors 3, 5 in the rotor housing 1 relate.
  • the seal assembly 11 consists of a number of lined ring seals 11a, 11b. In the illustrated embodiment, eight ring seals 11a, 11b are arranged one behind the other. In the ring seals 11 a, 11 b may preferably be lip seals, as in itself z. B. off EP 0 993 553 known.
  • the seal assembly 11 is surrounded by a first annular relief space 51 for trapping leakage gas passing through the seals 11a.
  • the relief space 51 may advantageously lie between the first number of five seal rings 11a seen from the rotor profile 7 and the last three, ie outer ring seals 11b.
  • the relief space 51 is connected by a formed in the rotor housing 1 parallel to the rotor axis connecting channel 53 with the suction chamber 10 of the screw compressor.
  • the annular relief chamber 51 is therefore acted upon by the suction pressure prevailing in the suction chamber 10 of the screw compressor.
  • the intake chamber 10 supplied air through the upstream compressor stages already at a pressure of z. B. between 10 and 15 bar, in particular about 12 bar, be compressed, and this is then also the pressure prevailing in the discharge chamber 51.
  • the high end pressure generated by the rotors, z. B. 40 bar, via the seal assembly 11 a, 11 b fall to zero.
  • a second annular discharge chamber 55 is provided, which is connected in a conventional manner with the atmosphere.
  • the task of this second discharge chamber 55 is to keep the oil system serving for lubrication of the bearings 15 and the constant velocity gear 17, 19 pressure-free and to minimize the access of leakage gas through the sealing arrangement 11 to the oil-lubricated regions.
  • the discharge chamber 51 communicates with the suction chamber 10 connecting passage 53 in the rotor housing 1 preferably in the immediate vicinity of the rotor housing 1 to the cooling housing 21 connecting partition 29. Thanks to the intensive cooling of acting like a cooling fin partition 29 by the deflected at her Coolant is also the connecting channel 53, and thus exposed to it in the suction chamber 10 leakage gas, a particularly intense cooling.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Electromagnetic Pumps, Or The Like (AREA)
  • Supercharger (AREA)

Abstract

A multi-staged screw compressor system includes a gearbox, a drive gear located in the gearbox, and a first, second and third screw compressor that are fastened to the gearbox and coupled to the drive gear such that the first, second, and third screw compressors are all driven in common by the drive gear. During operation the first screw compressor compresses a flow of gaseous fluid from an inlet pressure to a first intermediate pressure, the second screw compressor compresses the flow of fluid from the first intermediate pressure to a second intermediate pressure, and the third screw compressor compresses the flow of fluid from the second intermediate pressure to a final pressure. The final pressure is at least thirty times the inlet pressure.

Description

Die Erfindung betrifft einen Schraubenkompressor mit einem Rotorgehäuse, in dem zwei Schraubenrotoren, die mit schraubenförmigen Rippen und Nut miteinander kämmen, parallelachsig drehbar gelagert sind, und mit einem das Rotorgehäuse mit Abstand umgebenden Kühlgehäuse, das zusammen mit dem Rotorgehäuse einen Kühlraum bildet und mindestens eine Einlassöffnung und eine Auslassöffnung für ein den Kühlraum durchfließendes Kühlmittel aufweist.The invention relates to a screw compressor having a rotor housing, in which two screw rotors which mesh with helical ribs and groove are rotatably mounted parallel axis, and with a surrounding the rotor housing at a distance cooling housing which forms a cooling space together with the rotor housing and at least one inlet opening and an outlet opening for a refrigerant flowing through the cooling space.

Ein Schraubenkompressor dieser Art ist z. B. aus DE 201 10 360.5 U1 als Teil eines zweistufigen Schraubenkompressors bekannt.A screw compressor of this kind is z. B. off DE 201 10 360.5 U1 known as part of a two-stage screw compressor.

Die Erfindung ist mit besonderem Vorteil bei einem Schraubenkompressor anwendbar, der ein gasförmiges Medium, wie z. B. Luft, auf sehr hohe Drücke, im Bereich von 30 bis 50 bar insbesondere ca. 40 bar, verdichtet und bei dem es sich insbesondere um die Hochdruckstufe eines zwei- oder mehrstufigen Verdichteraggregats handeln kann. Die Verdichtung auf sehr hohe Drücke ist mit einer starken Erhitzung des gasförmigen Mediums verbunden, so dass eine besonders wirksame Kühlung wünschenswert ist.The invention is particularly applicable to a screw compressor which is a gaseous medium such. As air, at very high pressures, in the range of 30 to 50 bar, in particular about 40 bar, compressed and which may be in particular the high pressure stage of a two- or multi-stage compressor unit. The compression to very high pressures is associated with a strong heating of the gaseous medium, so that a particularly effective cooling is desirable.

Es ist deshalb eine Aufgabe der Erfindung, einen Schraubenkompressor der angegebenen Art mit besonders wirksamer Kühlung zu schaffen. Eine weitere Aufgabe besteht darin, den Schraubenkompressor so zu gestalten, dass die Entleerung und Befüllung des Kühlraums mit Kühlmittel besonders einfach ist.It is therefore an object of the invention to provide a screw compressor of the type specified with particularly effective cooling. Another object is to make the screw compressor so that the emptying and filling of the cooling chamber with coolant is particularly easy.

Der zur Lösung der Aufgabe erfindungsgemäß vorgeschlagene Schraubenkompressor ist im Anspruch 1 angegeben. Die abhängigen Ansprüche beziehen sich auf weitere vorteilhafte Merkmale des Schraubenkompressors.The proposed solution to the problem according to the invention screw compressor is given in claim 1. The dependent claims relate to further advantageous features of the screw compressor.

Durch die Erfindung wird erreicht, dass das Kühlmittel in dem Kühlraum die Außenfläche des Rotorgehäuses in Umfangsrichtung über nahezu 360° umströmt. Ferner wird das Kühlmittel beim Einströmen in den Kühlraum und vor dem Ausströmen jeweils an der das Rotorgehäuse mit dem Kühlmantel verbindenden Trennwand scharf umgelenkt. Es wurde gefunden, dass hier durch eine sehr intensive Kühlwirkung, insbesondere auch im Bereich der nach Art einer Kühlrippe wirkenden Trennwand, erzielt wird.By the invention it is achieved that the coolant in the cooling space flows around the outer surface of the rotor housing in the circumferential direction over almost 360 °. Furthermore, the coolant is deflected sharply when flowing into the cooling space and before the outflow respectively at the dividing wall connecting the rotor housing to the cooling jacket. It has been found that is achieved here by a very intense cooling effect, especially in the region of the acting like a cooling fin partition.

Eine Ausführungsform der Erfindung wird anhand der Zeichnungen näher erläutert. Es zeigt

Figur 1
eine perspektivische, teilweise geschnittene Ansicht des Schraubenkompressors gemäß einer Ausführungsform der Erfindung;
Figur 2
einen Querschnitt des Schraubenkompressors von Figur 1 ungefähr längs der Schnittlinie II - II von Figur 1,
Figur 3
einen Schnitt im Wesentlichen entlang der Linie III - III von Figur 2.
An embodiment of the invention will be explained in more detail with reference to the drawings. It shows
FIG. 1
a perspective, partially sectioned view of the screw compressor according to an embodiment of the invention;
FIG. 2
a cross section of the screw compressor of FIG. 1 approximately along the section line II - II of FIG. 1 .
FIG. 3
a section substantially along the line III - III of FIG. 2 ,

Der in Figur 1 gezeigte Schraubenkompressor hat ein im Schnitt dargestelltes Rotorgehäuse 1, in welchem zwei Rotoren 3 und 5 parallelachsig drehbar gelagert sind. Die Drehachsen der Rotoren 3, 5 liegen in einer gemeinsamen vertikalen Ebene, die auch die Schnittebene für die Darstellung des Rotorgehäuses 1 ist. Jeder Rotor hat einen Profilabschnitt 7 bzw. 9, der ein Profil mit schraubenförmig verlaufenden Rippen bzw. Nuten aufweist, wobei die Rippen und Nuten der beiden Profilabschnitte 7, 9 berührungsfrei kämmend und abdichtend ineinander greifen. An die Profilabschnitte 7, 9 schließen sich beiderseits Wellenzapfen 7a, 7b, 9a, 9b an, mit deren Umfangsfläche Dichtungsanordnungen 11, 12 zusammenwirken, um den Rotor im Rotorgehäuse 1 abzudichten. Die Wellenzapfen 7a, 7b, 9a, 9b sind ferner durch Lager 13, 15 in dem Rotorgehäuse 1 drehbar gelagert.The in FIG. 1 shown screw compressor has a rotor housing 1 shown in section, in which two rotors 3 and 5 are mounted rotatable parallel axis. The axes of rotation of the rotors 3, 5 lie in a common vertical plane, which is also the cutting plane for the representation of the rotor housing 1. Each rotor has a profile section 7 and 9, which has a profile with helically extending ribs or grooves, wherein the ribs and grooves of the two profile sections 7, 9 engage in a non-contact meshing and sealing engagement. At the profile sections 7, 9 close to both sides shaft journals 7a, 7b, 9a, 9b, with the peripheral surface seal assemblies 11, 12 cooperate to seal the rotor in the rotor housing 1. The shaft journals 7a, 7b, 9a, 9b are also rotatably supported by bearings 13, 15 in the rotor housing 1.

Der in Figur 1 obere Rotor 3 ist der Hauptläufer und weist an seinem in Figur 1 linken Ende eine Verlängerung 7c seines Wellenzapfens auf, die zur Aufnahme eines Antriebszahnrades (nicht dargestellt) bestimmt ist, das mit einem entsprechenden Zahnrad eines Antriebsgetriebes (nicht dargestellt) kämmt, um den Rotor 3 zur Drehung anzutreiben. An dem in Figur 1 rechten Ende weisen die beiden Rotoren 3, 5 zwei miteinander kämmende Zahnräder 17, 19 auf, die ein Synchronisiergetriebe bilden, das die Drehung von dem oberen Rotor 3 auf den unteren Rotor 5, der der Nebenläufer ist, im gewünschten Drehzahlverhältnis überträgt.The in FIG. 1 upper rotor 3 is the main rotor and has at its in FIG. 1 left end of an extension 7c of its shaft journal, which serves to receive a drive gear (not shown), which meshes with a corresponding gear of a drive gear (not shown) to drive the rotor 3 for rotation. At the in FIG. 1 right end, the two rotors 3, 5, two intermeshing gears 17, 19, which form a synchronizing, which transmits the rotation of the upper rotor 3 to the lower rotor 5, which is the Nebenläufer in the desired speed ratio.

Bei Betrieb des in Figur 1 gezeigten Schraubenkompressors wird seinem Ansaugraum 10, der an dem in Figur 1 linken Ende der Profilabschnitte 7 bzw. 9 in dem Rotorgehäuse 1 ausgebildet und mit einem (nicht dargestellten) Ansaugstutzen verbunden ist, das zu verdichtende Gas, insbesondere Luft, zugeführt. Vorzugsweise ist das zugeführte Gas bereits von einer oder mehreren vorgeschalteten Kompressorstufen (nicht dargestellt) auf einen Zwischendruck vorverdichtet, beispielsweise auf einen Druck im Bereich von 10 bis 15 bar, vorzugsweise ca. 12 bar. Dieses vorverdichtete Gas wird durch die Profilabschnitte 7, 9 der beiden Rotoren 3, 5 in Figur 1 nach rechts gefördert und dabei auf einen Enddruck verdichtet, der vorzugsweise im Bereich von 30 bis 50 bar, insbesondere bei ca. 40 bar, liegt. Das verdichtete Gas verlässt das Rotorgehäuse 1 an dem in Figur 1 rechten, druckseitigen Ende der Profilabschnitte 7, 9 durch einen (nicht dargestellten) Auslass.When operating the in FIG. 1 shown screw compressor is its suction chamber 10, which at the in FIG. 1 left end of the profile sections 7 and 9 formed in the rotor housing 1 and connected to a (not shown) intake, the gas to be compressed, in particular air, supplied. Preferably, the supplied gas is already precompressed by one or more upstream compressor stages (not shown) to an intermediate pressure, for example to a pressure in the range of 10 to 15 bar, preferably about 12 bar. This precompressed gas is through the profile sections 7, 9 of the two rotors 3, 5 in FIG. 1 conveyed to the right and thereby compressed to a final pressure, which is preferably in the range of 30 to 50 bar, in particular at about 40 bar. The compressed gas leaves the rotor housing 1 at the in FIG. 1 right, pressure-side end of the profile sections 7, 9 through an outlet (not shown).

Das Rotorgehäuse 1 ist von einem Kühlmantel oder Kühlgehäuse 21 umgeben, das überwiegend einstückig mit dem Rotorgehäuse 1 ausgebildet ist und dieses mit Abstand umgibt. Oben und unten hat das Kühlgehäuse 21 großflächige Öffnungen, die mittels einer Deckelplatte 23 bzw. einer Bodenplatte 25, die durch Schrauben befestigt sind, verschlossen sind. Zwischen dem Rotorgehäuse 1 und dem Kühlgehäuse 21, 23, 25 befindet sich ein das Rotorgehäuse 1 ringförmig umgebender Kühlraum 27.The rotor housing 1 is surrounded by a cooling jacket or cooling housing 21, which is formed predominantly in one piece with the rotor housing 1 and surrounds this at a distance. Above and below, the cooling housing 21 has large-area openings, which are closed by means of a cover plate 23 and a bottom plate 25, which are fastened by screws. Between the rotor housing 1 and the cooling housing 21, 23, 25 is a rotor housing 1 annularly surrounding cooling space 27th

Figur 2 zeigt schematisch und vereinfacht einen Querschnitt etwa entlang der Linie II - II von Figur 1. Das Rotorgehäuse 1 für die Aufnahme der (nicht dargestellten) Schraubenrotoren ist von dem Kühlmantel oder Kühlgehäuse 21 umgeben, dessen Seitenwände 21a, 21b vorzugsweise einstückig mit dem Rotorgehäuse 1 ausgebildet sind und welches oben und unten durch die Deckelwand 23 bzw. Bodenplatte 25 verschlossen ist. Das Kühlgehäuse 21 bildet mit dem Rotorgehäuse 1 einen das Rotorgehäuse 1 im Wesentlichen vollständig ringförmig umgebenden Kühlraum 27, der nur an einer Stelle durch eine das Rotorgehäuse 1 mit der Seitenwand 21b des Kühlgehäuses 21 verbindende Trennwand 29 unterbrochen ist. Die Trennwand 29 verläuft horizontal etwa in halber Höhe zwischen den Achsmittelpunkten M1 M2 der lotrecht übereinander angeordneten Schraubenrotoren. FIG. 2 shows schematically and simplified a cross section approximately along the line II - II of FIG. 1 , The rotor housing 1 for receiving the (not shown) screw rotors is surrounded by the cooling jacket or cooling housing 21, the side walls 21a, 21b are preferably formed integrally with the rotor housing 1 and which closed at the top and bottom by the top wall 23 and bottom plate 25 is. The cooling housing 21 forms, together with the rotor housing 1, a cooling space 27 which surrounds the rotor housing 1 essentially completely annularly and which is interrupted only at one point by a partition wall 29 connecting the rotor housing 1 to the side wall 21b of the cooling housing 21. The partition wall 29 extends horizontally approximately at half the height between the center axis M1 M2 of the vertically superposed screw rotors.

Das Kühlgehäuse 21 weist eine Einlassöffnung 31 und eine Auslassöffnung 33 für Kühlflüssigkeit, z. B. Kühlwasser oder Öl, auf. Die Einlassöffnung 31 mündet in einem lotrecht nach oben verlaufenden Einlaufkanal 35, dessen obere Austrittsöffnung 35' der Unterseite der Trennwand 29 mit einem Abstand gegenübersteht. Der Auslassöffnung 33 vorgelagert befindet sich ein lotrechter Ausströmkanal 37, dessen untere Einlauföffnung 37' der Oberseite der Trennwand 29 mit geringem Abstand gegenübersteht.The cooling housing 21 has an inlet opening 31 and an outlet opening 33 for cooling fluid, for. As cooling water or oil on. The inlet opening 31 opens into a vertically upwardly extending inlet channel 35, the upper outlet opening 35 'facing the underside of the partition wall 29 at a distance. Upstream of the outlet opening 33 is a vertical outflow channel 37, the lower inlet opening 37 'of the top of the partition 29 faces with a small distance.

Die schwarzen Pfeile in Figur 2 kennzeichnen den Strömungsweg des der Einlassöffnung 31 zugeführten Kühlmittels. Dieses wird durch den Einströmkanal 35 senkrecht nach
oben gegen die Unterseite der Trennwand 29 gerichtet, an dieser scharf umgelenkt und fließt dann nach unten und in Fig. 2 im Uhrzeigersinn um den gesamten Umfang des Rotorgehäuses 1 herum, bis es auf die Oberseite der Trennwand 29 auftrifft, von dieser scharf nach oben umgelenkt und durch den Ausströmkanal 37 und die Auslassöffnung 33 abgezogen wird.The black arrows in FIG. 2 indicate the flow path of the coolant supplied to the inlet port 31. This is perpendicular by the inflow passage 35
directed upward against the underside of the partition wall 29, deflected at this sharply and then flows down and in Fig. 2 in a clockwise direction around the entire circumference of the rotor housing 1 until it impinges on the upper side of the partition wall 29, is deflected sharply upward by the latter and is withdrawn through the outflow channel 37 and the outlet opening 33.

In der den Ausströmkanal 37 vom Kühlraum 1 abtrennenden Wandung 39 ist in einer Höhe, die etwa der oberen Begrenzung der Auslassöffnung 33 entspricht, eine Entlüftungsöffnung 41 mit kleinem Querschnitt ausgebildet. Durch diese Entlüftungsöffnung 41 kann beim Befüllen des Kühlraums 27 mit Kühlmittel Luft entweichen, wie in Figur 2 durch die oberen gepunkteten Pfeile angedeutet, so dass der Kühlraum 27 bis zur Höhe der Entlüftungsöffnung 41, d. h. bis zu dem in Figur 2 durch die Linie 43 angegebenen Flüssigkeitsstand, befüllt werden kann und das Volumen der oberhalb des Flüssigkeitsspiegels 43 eingeschlossenen Restluft sehr gering ist.In the discharge channel 37 from the cooling chamber 1 separating wall 39 is at a height which corresponds approximately to the upper boundary of the outlet opening 33, a vent opening 41 formed with a small cross-section. Through this vent opening 41 can escape when filling the cooling chamber 27 with coolant air, as in FIG. 2 indicated by the upper dotted arrows, so that the cooling space 27 up to the height of the vent opening 41, ie up to the in FIG. 2 can be filled by the line 43 indicated liquid level, and the volume of the liquid is trapped above the liquid level 43 residual air is very low.

In der den Einströmkanal 35 vom Kühlraum 27 abtrennenden Wandung 45 ist in Höhe der unteren Begrenzung der Einlassöffnung 31 eine Sickeröffnung 47 sehr kleinen Querschnitts ausgebildet. Beim Entleeren der Kühlflüssigkeit aus dem Kühlraum 27 kann durch die Sickeröffnung 47 und die Einlassöffnung 31 Kühlflüssigkeit ablaufen (wie durch die unteren gepunkteten Pfeile in Figur 2 angedeutet), bis der Kühlflüssigkeitsspiegel im Kühlraum 27 die Höhe der Sickeröffnung 47 erreicht hat, d. h. bis auf das durch die Linie 49 angegebene Niveau abgesunken ist. Die beim Entleeren des Kühlraumes 27 unterhalb der Linie 49 verbleibende Restmenge an Kühlflüssigkeit ist deshalb sehr gering.In the inflow channel 35 separating from the cooling chamber 27 wall 45 is formed at the level of the lower boundary of the inlet opening 31, a percolation opening 47 of very small cross-section. When emptying the cooling liquid from the cooling space 27, cooling liquid can drain through the seepage opening 47 and the inlet opening 31 (as indicated by the lower dotted arrows in FIG FIG. 2 indicated), until the coolant level in the cooling chamber 27 has reached the height of the seepage opening 47, ie, has dropped to the level indicated by the line 49. The remaining amount of cooling liquid remaining upon emptying of the cooling space 27 below the line 49 is therefore very small.

Figur 3 zeigt weitere Details des Schraubenkompressors die sich auf die in Figur 1 gezeigten Dichtungsanordnungen 11 zum Abdichten der druckseitigen Wellenzapfen 7b, 9b der Rotoren 3, 5 im Rotorgehäuse 1 beziehen. Wie dargestellt, besteht die Dichtungsanordnung 11 aus einer Anzahl aneinander gereihter Ringdichtungen 11a, 11b. Bei der dargestellten Ausführungsform sind acht Ringdichtungen 11a, 11b hintereinander angeordnet. Bei den Ringdichtungen 11a, 11b kann es sich vorzugsweise um Lippendichtringe handeln, wie an sich z. B. aus EP 0 993 553 bekannt. An einer geeigneten Stelle, die zwischen einer ersten Anzahl von Ringdichtungen 11a und einer zweiten Anzahl von Ringdichtungen 11b liegt, ist die Dichtungsanordnung 11 von einem ersten ringförmigen Entlastungsraum 51 zum Auffangen von durch die Dichtungen 11a hindurchtretendem Leckgas umgeben. Bei der Ausführungsform von Figur 3 mit acht Ringdichtungen kann der Entlastungsraum 51 vorteilhafterweise zwischen der vom Rotorprofil 7 aus gesehen ersten Anzahl von fünf Dichtungsringen 11a und den drei letzten, d. h. äußeren Ringdichtungen 11b liegen. FIG. 3 shows further details of the screw compressor referring to the in FIG. 1 shown seal assemblies 11 for sealing the pressure-side shaft journals 7b, 9b of the rotors 3, 5 in the rotor housing 1 relate. As shown, the seal assembly 11 consists of a number of lined ring seals 11a, 11b. In the illustrated embodiment, eight ring seals 11a, 11b are arranged one behind the other. In the ring seals 11 a, 11 b may preferably be lip seals, as in itself z. B. off EP 0 993 553 known. At a suitable location located between a first number of ring seals 11a and a second number of ring seals 11b, the seal assembly 11 is surrounded by a first annular relief space 51 for trapping leakage gas passing through the seals 11a. In the embodiment of FIG. 3 With eight ring seals, the relief space 51 may advantageously lie between the first number of five seal rings 11a seen from the rotor profile 7 and the last three, ie outer ring seals 11b.

Der Entlastungsraum 51 ist durch einen im Rotorgehäuse 1 parallel zur Rotorachse ausgebildeten Verbindungskanal 53 mit dem Ansaugraum 10 des Schraubenkompressors verbunden. Der ringförmige Entlastungsraum 51 ist daher mit dem im Ansaugraum 10 herrschenden Ansaugdruck des Schraubenkompressors beaufschlagt. Bei der bevorzugten Verwendung des Schraubenkompressors als Hochdruckstufe eines mehrstufigen Kompressoraggregats kann die dem Ansaugraum 10 zugeführte Luft durch die vorgeschalteten Kompressorstufen bereits auf einen Druck von z. B. zwischen 10 und 15 bar, insbesondere ca. 12 bar, verdichtet sein, und dies ist dann auch der im Entlastungsraum 51 herrschende Druck. In Betrieb des Kompressors muss der von den Rotoren erzeugte hohe Enddruck, z. B. 40 bar, über die Dichtungsanordnung 11a, 11b auf Null abfallen. Es hat sich gezeigt, dass dieser Druckabfall nicht linear ist, sondern sich überwiegend auf die äußeren, vom Profilabschnitt 7, 9 entfernteren Ringdichtungen 11b konzentriert und diese daher sehr stark mechanisch belastet. Durch den ersten Entlastungsraum 51, der mit dem Einlassdruck des Kompressors beaufschlagt ist, wird an einer definierten Stelle der Dichtungsanordung ein definierter Zwischendruck vorgegeben und dadurch der Druckabfall über die gesamte Dichtungsanordnung 11a, 11b vergleichmäßigt, wodurch die Dichtungen 11b mechanisch entlastet werden.The relief space 51 is connected by a formed in the rotor housing 1 parallel to the rotor axis connecting channel 53 with the suction chamber 10 of the screw compressor. The annular relief chamber 51 is therefore acted upon by the suction pressure prevailing in the suction chamber 10 of the screw compressor. In the preferred use of the screw compressor as a high-pressure stage of a multi-stage compressor unit, the intake chamber 10 supplied air through the upstream compressor stages already at a pressure of z. B. between 10 and 15 bar, in particular about 12 bar, be compressed, and this is then also the pressure prevailing in the discharge chamber 51. In operation of the compressor, the high end pressure generated by the rotors, z. B. 40 bar, via the seal assembly 11 a, 11 b fall to zero. It has been found that this pressure drop is not linear, but concentrates predominantly on the outer ring seals 11b, which are more remote from the profile section 7, 9, and therefore load them very heavily mechanically. By the first discharge chamber 51, which is acted upon by the inlet pressure of the compressor, a defined intermediate pressure is specified at a defined location of the seal assembly and thereby the pressure drop over the entire seal assembly 11a, 11b made uniform, whereby the seals 11b are mechanically relieved.

An dem rotorfernen Ende der Dichtungsanordnung 11 ist ein zweiter ringförmiger Entlastungsraum 55 vorgesehen, der in an sich bekannter Weise mit der Atmosphäre verbunden ist. Aufgabe dieses zweiten Entlastungsraums 55 ist es, das zur Schmierung der Lager 15 und des Gleichlaufgetriebes 17, 19 dienende Ölsystem druckfrei zu halten und den Zutritt von Leckgas durch die Dichtungsanordung 11 hindurch zu den ölgeschmierten Bereichen möglichst klein zu halten.At the rotor remote end of the seal assembly 11, a second annular discharge chamber 55 is provided, which is connected in a conventional manner with the atmosphere. The task of this second discharge chamber 55 is to keep the oil system serving for lubrication of the bearings 15 and the constant velocity gear 17, 19 pressure-free and to minimize the access of leakage gas through the sealing arrangement 11 to the oil-lubricated regions.

Wie in Figur 2 dargestellt, verläuft der den Entlastungsraum 51 mit dem Ansaugraum 10 verbindende Verbindungskanal 53 im Rotorgehäuse 1 vorzugsweise in unmittelbarer Nähe der das Rotorgehäuse 1 mit dem Kühlgehäuse 21 verbindenden Trennwand 29. Dank der intensiven Kühlung der nach Art einer Kühlrippe wirkenden Trennwand 29 durch das an ihr umgelenkte Kühlmittel wird auch der Verbindungskanal 53, und damit das in ihm zum Ansaugraum 10 strömende Leckgas, einer besonders intensiven Kühlung ausgesetzt.As in FIG. 2 shown, the discharge chamber 51 communicates with the suction chamber 10 connecting passage 53 in the rotor housing 1 preferably in the immediate vicinity of the rotor housing 1 to the cooling housing 21 connecting partition 29. Thanks to the intensive cooling of acting like a cooling fin partition 29 by the deflected at her Coolant is also the connecting channel 53, and thus exposed to it in the suction chamber 10 leakage gas, a particularly intense cooling.

Claims (5)

  1. Screw compressor having a rotor housing (1), in which two screw rotors (3, 5) are mounted rotatably, a cooling housing (21) which surrounds the rotor housing at a spacing and, together with the rotor housing (1), forms a cooling space (27) and has at least one inlet opening (31) and one outlet opening (33) for a liquid coolant which flows through the cooling space, characterized in that the cooling space (27) surrounds the rotor housing (1) annularly substantially over its entire circumference and is interrupted only at one location by way of a separating wall (29) which connects the rotor housing (1) to the cooling housing (21), and in that an inflow duct (35) is connected to the inlet opening (31), out of which inflow duct (35) the coolant flows into the cooling space (27) with an inflow direction which is directed substantially perpendicularly against a side face of the separating wall (29), and in that an outflow duct (37) is positioned upstream of the outlet opening (33), which outflow duct (37) has an inflow opening (37) which lies substantially perpendicularly opposite the other side face of the separating wall (29), in such a way that the coolant which is fed in first of all strikes one side of the separating wall (29) and is deflected at the latter, then flows around the rotor housing over approximately 360° of its circumference, and is then deflected again on the other side of the separating wall (29) and is drawn off through the outflow duct.
  2. Screw compressor according to Claim 1, characterized in that the separating wall (29) runs horizontally, the coolant which flows in is directed substantially vertically upwards against the underside of the separating wall (29) by way of the inflow duct (35), and, after flowing around the rotor housing (1), is again deflected vertically upwards into the outflow duct on the upper side of the separating wall (29).
  3. Screw compressor according to Claims 1 and 2, characterized in that a weep hole (47) of small cross section is arranged in the wall of the inflow duct (35) at a small spacing from the lower wall (25) of the cooling housing (21).
  4. Screw rotor according to one of Claims 1 to 3, characterized in that a vent hole (41) of small cross section is provided in the wall of the outflow duct (3, 7) at a small spacing from the upper wall (23) of the cooling housing.
  5. Screw rotor according to one of Claims 1 to 4, characterized in that a connecting duct (53) is configured in the wall of the rotor housing (1) in the vicinity of the separating wall (29) which connects the latter to the cooling housing (21), which connecting duct (53) a relief space (51) which connects a seal arrangement (11) which seals the pressure-side shaft journals (7b, 9b) of the screw rotors (3, 5) in the rotor housing to the intake space (10) of the screw compressor.
EP06754260.5A 2005-12-08 2006-06-09 Helical screw compressor comprising a cooling jacket Active EP1957797B1 (en)

Applications Claiming Priority (2)

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DE102005058698 2005-12-08
PCT/EP2006/005557 WO2007065485A1 (en) 2005-12-08 2006-06-09 Helical screw compressor comprising a cooling jacket

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EP1957797A1 EP1957797A1 (en) 2008-08-20
EP1957797B1 true EP1957797B1 (en) 2016-09-28

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EP06762002A Active EP1957798B1 (en) 2005-12-08 2006-06-09 Helical screw compressor
EP06754260.5A Active EP1957797B1 (en) 2005-12-08 2006-06-09 Helical screw compressor comprising a cooling jacket
EP06754261.3A Active EP1979618B1 (en) 2005-12-08 2006-06-09 Multi-step helical screw compressor unit
EP06754262A Withdrawn EP1957799A1 (en) 2005-12-08 2006-06-09 Helical screw compressor

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EP06754261.3A Active EP1979618B1 (en) 2005-12-08 2006-06-09 Multi-step helical screw compressor unit
EP06754262A Withdrawn EP1957799A1 (en) 2005-12-08 2006-06-09 Helical screw compressor

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US (4) US20080286129A1 (en)
EP (4) EP1957798B1 (en)
CN (2) CN101321955A (en)
AT (1) ATE498071T1 (en)
DE (1) DE502006008894D1 (en)
ES (1) ES2359015T3 (en)
HK (1) HK1127111A1 (en)
WO (4) WO2007065485A1 (en)

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Also Published As

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EP1957799A1 (en) 2008-08-20
DE502006008894D1 (en) 2011-03-24
HK1127111A1 (en) 2009-09-18
EP1957797A1 (en) 2008-08-20
WO2007065486A1 (en) 2007-06-14
US20080286138A1 (en) 2008-11-20
CN101321954A (en) 2008-12-10
US20130011285A1 (en) 2013-01-10
EP1979618A1 (en) 2008-10-15
CN101321955A (en) 2008-12-10
ATE498071T1 (en) 2011-02-15
WO2007065484A1 (en) 2007-06-14
ES2359015T3 (en) 2011-05-17
US9091268B2 (en) 2015-07-28
EP1979618B1 (en) 2016-04-27
EP1957798A1 (en) 2008-08-20
EP1957798B1 (en) 2011-02-09
WO2007065487A1 (en) 2007-06-14
CN101321954B (en) 2012-06-13
WO2007065485A1 (en) 2007-06-14
US7690901B2 (en) 2010-04-06
US7713039B2 (en) 2010-05-11
US20080286129A1 (en) 2008-11-20
US20090004036A1 (en) 2009-01-01

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