EP1957797A1 - Helical screw compressor comprising a cooling jacket - Google Patents

Helical screw compressor comprising a cooling jacket

Info

Publication number
EP1957797A1
EP1957797A1 EP06754260A EP06754260A EP1957797A1 EP 1957797 A1 EP1957797 A1 EP 1957797A1 EP 06754260 A EP06754260 A EP 06754260A EP 06754260 A EP06754260 A EP 06754260A EP 1957797 A1 EP1957797 A1 EP 1957797A1
Authority
EP
European Patent Office
Prior art keywords
cooling
housing
rotor housing
partition
rotor
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP06754260A
Other languages
German (de)
French (fr)
Other versions
EP1957797B1 (en
Inventor
Carsten Achtelik
Dieter HÜTTERMANN
Michael Besseling
Norbert Henning
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.)
GHH Rand Schraubenkompressoren GmbH
Original Assignee
GHH Rand Schraubenkompressoren GmbH
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by GHH Rand Schraubenkompressoren GmbH filed Critical GHH Rand Schraubenkompressoren GmbH
Publication of EP1957797A1 publication Critical patent/EP1957797A1/en
Application granted granted Critical
Publication of EP1957797B1 publication Critical patent/EP1957797B1/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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
    • 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 with a rotor housing in which two screw rotors, which mesh with one another with helical ribs and groove, are rotatably supported in parallel axes, and with a cooling housing which surrounds the rotor housing at a distance and which forms a cooling space together with the rotor housing and at least one inlet opening and has an outlet opening for a coolant flowing through the cooling space.
  • a screw compressor of this type is e.g. B. from DE 201 10 360.5 Ul known as part of a two-stage screw compressor.
  • the invention is particularly applicable to a screw compressor that uses a gaseous medium such.
  • a gaseous medium such.
  • B. air compressed to very high pressures, in the range of 30 to 50 bar, in particular approximately 40 bar, and which can in particular be the high-pressure stage of a two-stage or multi-stage compressor unit.
  • the compression to very high pressures is associated with a strong heating of the gaseous medium, so that particularly effective cooling is desirable.
  • the screw compressor proposed according to the invention to achieve the object is specified in claim 1.
  • the dependent claims relate to further advantageous features of the screw compressor. It is achieved by the invention 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 sharply deflected when it flows into the cooling space and before it flows out at the partition wall connecting the rotor housing to the cooling jacket. It was found that a very intensive cooling effect is achieved here, in particular also in the area of the partition wall, which acts like a cooling fin.
  • FIG. 1 shows a perspective, partially sectioned view of the screw compressor according to an embodiment of the invention
  • FIG. 2 shows a cross section of the screw compressor from FIG. 1 approximately along the section line II-II from FIG. 1,
  • FIG. 3 shows a section substantially along the line III-III of FIG. 2.
  • the screw compressor shown in FIG. 1 has a rotor housing 1, shown in section, in which two rotors 3 and 5 are rotatably mounted in parallel axes.
  • the axes of rotation of the rotors 3, 5 lie in a common vertical plane, which is also the sectional plane for the representation of the rotor housing 1.
  • Each rotor has a profile section 7 or 9, which has a profile with helically extending ribs or grooves, the ribs and grooves of the two profile sections 7, 9 meshing and sealingly in a contact-free manner.
  • Shaft journals 7a, 7b, 9a, 9b adjoin the profile sections 7, 9 on both sides, with their peripheral surface cooperating with sealing arrangements 11, 12 in order to seal the rotor in the rotor housing 1.
  • the shaft journals 7a, 7b, 9a, 9b are also rotatably supported in the rotor housing 1 by bearings 13, 15.
  • the upper rotor 3 in FIG. 1 is the main rotor and has an extension 7c of its shaft journal at its left end in FIG.
  • Drive gear (not shown) is determined, which meshes with a corresponding gear of a drive gear (not shown) to drive the rotor 3 for rotation.
  • the two rotors 3, 5 have two meshing gears 17, 19 which form a synchronizing gear which rotates from the upper rotor 3 to the lower rotor 5, which is the secondary rotor, in the desired speed ratio transmits.
  • the screw compressor shown in FIG. 1 When the screw compressor shown in FIG. 1 is operating, its suction chamber 10, which is formed in the rotor housing 1 at the left end of the profile sections 7 and 9 in FIG. 1 and is connected to a suction nozzle (not shown), the gas to be compressed, in particular air , fed.
  • the gas supplied is preferably already pre-compressed by one or more upstream compressor stages (not shown) to an intermediate pressure, for example to a pressure in the range from 10 to 15 bar, preferably approximately 12 bar.
  • This precompressed gas is conveyed to the right by the profile sections 7, 9 of the two rotors 3, 5 in FIG. 1 and is compressed to a final pressure which is preferably in the range from 30 to 50 bar, in particular around 40 bar.
  • the compressed gas leaves the rotor housing 1 at the right end of the profile sections 7, 9 in FIG. 1 through an outlet (not shown).
  • the rotor housing 1 is surrounded by a cooling jacket or cooling housing 21, which is predominantly formed in one piece with the rotor housing 1 and surrounds it at a distance.
  • the cooling housing 21 has large openings at the top and bottom, which are closed by means of a cover plate 23 and a base plate 25 which are fastened by screws. Between the rotor housing 1 and the cooling housing 21, 23, 25 there is a cooling space 27 which surrounds the rotor housing 1 in a ring.
  • FIG. 2 shows schematically and simplified a cross section approximately along the line II - II of Figure 1.
  • the rotor housing 1 for receiving the screw rotors (not shown) is surrounded by the cooling jacket or cooling housing 21, the side walls 21a, 21b of which are preferably in one piece with the rotor housing 1 and which is closed at the top and bottom by the cover wall 23 or base plate 25.
  • the cooling housing 21 forms with the rotor housing 1 a cooling space 27 which surrounds the rotor housing 1 in a substantially completely annular manner 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 29 runs horizontally approximately halfway between the axis centers Ml, M2 of the screw rotors arranged vertically one above the other.
  • the cooling housing 21 has an inlet opening 31 and an outlet opening 33 for cooling liquid, for. B. cooling water or oil.
  • the inlet opening 31 opens into an inlet channel 35 which runs vertically upwards, the upper outlet opening 35 'of which is at a distance from the underside of the partition wall 29.
  • the black arrows in FIG. 2 indicate the flow path of the coolant supplied to the inlet opening 31. This is perpendicular through the inflow channel 35
  • a ventilation opening 41 with a small cross section is formed at a height which corresponds approximately to the upper limit of the outlet opening 33. Air can escape through this ventilation opening 41 when the cooling space 27 is filled with coolant, as indicated by the upper dotted arrows in FIG. 2, so that the cooling space 27 up to the height of the ventilation opening 41, ie up to that indicated by line 43 in FIG. 2 Liquid level, can be filled and the volume of the residual air trapped above the liquid level 43 is very small.
  • a seepage opening 47 of very small cross-section is formed in the wall 45 separating the inflow channel 35 from the cooling space 27 at the lower limit of the inlet opening 31.
  • cooling liquid When the cooling liquid is emptied 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. 2) until the cooling liquid level in the cooling space 27 has reached the height of the seepage opening 47, ie to has dropped to the level indicated by line 49.
  • the residual amount of cooling liquid remaining below line 49 when the cooling chamber 27 is emptied is therefore very small.
  • FIG. 3 shows further details of the invention which relate to the sealing arrangements 11 shown in FIG. 1 for sealing the pressure-side shaft journals 7b, 9b of the rotors 3, 5 in the rotor housing 1.
  • the sealing arrangement 11 consists of a number of ring seals I Ia, I Ib arranged in a row. In the illustrated embodiment, eight ring seals I Ia, I Ib are arranged one behind the other. The ring seals I Ia, 1 Ib can preferably be lip seals, as such. B. is known from EP 0 993 553.
  • the seal arrangement 11 is surrounded by a first annular relief chamber 51 for collecting leakage gas passing through the seals 11a.
  • the relief space 51 can advantageously be between the first number of five sealing rings 11a seen from the rotor profile 7 and the last three, i. H. outer ring seals are 1 Ib.
  • the relief chamber 51 is connected to the suction chamber 10 of the screw compressor by a connecting channel 53 formed in the rotor housing 1 parallel to the rotor axis.
  • the annular relief chamber 51 is therefore subjected to the suction pressure of the screw compressor prevailing in the suction chamber 10.
  • the air supplied to the suction chamber 10 can already be brought up to a pressure of, for example, upstream by the compressor stages. B. between 10 and 15 bar, in particular about 12 bar, and this is also the pressure prevailing in the relief chamber 51.
  • the high final pressure generated by the rotors e.g. B.
  • the first relief chamber 51 which is charged with the inlet pressure of the compressor, predefines a defined intermediate pressure at a defined point in the seal arrangement, thereby equalizing the pressure drop across the entire seal arrangement I Ia, I Ib, whereby the seals I Ib are mechanically relieved.
  • a second annular relief space 55 is provided, which is connected to the atmosphere in a manner known per se.
  • the purpose of this second relief chamber 55 is to keep the oil system used for lubricating the bearings 15 and the synchronous gear 17, 19 free of pressure and to keep the leakage gas through the seal arrangement 11 to the oil-lubricated areas as small as possible.
  • the connecting channel 53 connecting the relief chamber 51 to the suction chamber 10 in the rotor housing 1 preferably runs in the immediate vicinity of the partition wall 29 connecting the rotor housing 1 to the cooling housing 21, thanks to the intensive cooling of the partition wall 29, which acts like a cooling fin the coolant deflected at it, the connecting channel 53, and thus the leakage gas flowing in it to the suction space 10, is subjected to particularly intensive cooling.

Landscapes

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

Abstract

The invention relates to the rotor housing (1) of a helical screw compressor which is surrounded by a cooling housing (21, 23, 25) which forms a cooling chamber (27) which surrounds the rotor housing (1) in an annular-shaped manner, said cooling chamber being intercepted on a point by a separating wall (29) which connects the rotor housing (1) to the cooling housing (21). The coolant, which is guided to an inlet (31), is oriented counter to the lower side of the separating wall (29) through a perpendicular inlet channel (35) which flows in an upward direction, is deviated there and flows about the rotor housing (1) until the upper side of the separating wall (29), where it is deviated again and is discharged to the outlet opening (33) through a perpendicular outlet channel (37) which extends in an upward manner. A weephole (47) is provided in a wall of an inlet channel (35) and a ventilation opening (41) is provided in the wall of the outlet channel (37), such that only a small amount of residual air remains in the cooling chamber (27) when it is filled with a cooling liquid and only a small amount of residual fluid remains when emptied.

Description

Schraubenkompressor mit Kühlmantel  Screw compressor with cooling jacket
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 with a rotor housing in which two screw rotors, which mesh with one another with helical ribs and groove, are rotatably supported in parallel axes, and with a cooling housing which surrounds the rotor housing at a distance and which forms a cooling space together with the rotor housing and at least one inlet opening and has an outlet opening for a coolant flowing through the cooling space.
Ein Schraubenkompressor dieser Art ist z. B. aus DE 201 10 360.5 Ul als Teil eines zweistufigen Schraubenkompressors bekannt. A screw compressor of this type is e.g. B. from DE 201 10 360.5 Ul 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 that uses a gaseous medium such. B. air, compressed to very high pressures, in the range of 30 to 50 bar, in particular approximately 40 bar, and which can in particular be the high-pressure stage of a two-stage or multi-stage compressor unit. The compression to very high pressures is associated with a strong heating of the gaseous medium, so that 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 task is to design the screw compressor so that emptying and filling the cooling space with coolant is particularly simple.
Der zur Lösung der Aufgabe erfindungsgemäß vorgeschlagene Schraubenkompressor ist im Anspruch 1 angegeben. Die abhängigen Ansprüche beziehen sich auf weitere vorteilhafte Merkmale des Schraubenkompressors. 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. The screw compressor proposed according to the invention to achieve the object is specified in claim 1. The dependent claims relate to further advantageous features of the screw compressor. It is achieved by the invention 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 sharply deflected when it flows into the cooling space and before it flows out at the partition wall connecting the rotor housing to the cooling jacket. It was found that a very intensive cooling effect is achieved here, in particular also in the area of the partition wall, which acts like a cooling fin.
Eine Ausführungsform der Erfindung wird anhand der Zeichnungen näher erläutert. Es zeigt An embodiment of the invention is explained in more detail with reference to the drawings. It shows
Figur 1 eine perspektivische, teilweise geschnittene Ansicht des Schraubenkom- pressors gemäß einer Ausführungsform der Erfindung; 1 shows a perspective, partially sectioned view of the screw compressor according to an embodiment of the invention;
Figur 2 einen Querschnitt des Schraubenkompressors von Figur 1 ungefähr längs der Schnittlinie II - II von Figur 1 , FIG. 2 shows a cross section of the screw compressor from FIG. 1 approximately along the section line II-II from FIG. 1,
Figur 3 einen Schnitt im Wesentlichen entlang der Linie III - III von Figur 2. FIG. 3 shows 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 screw compressor shown in FIG. 1 has a rotor housing 1, shown in section, in which two rotors 3 and 5 are rotatably mounted in parallel axes. The axes of rotation of the rotors 3, 5 lie in a common vertical plane, which is also the sectional plane for the representation of the rotor housing 1. Each rotor has a profile section 7 or 9, which has a profile with helically extending ribs or grooves, the ribs and grooves of the two profile sections 7, 9 meshing and sealingly in a contact-free manner. Shaft journals 7a, 7b, 9a, 9b adjoin the profile sections 7, 9 on both sides, with their peripheral surface cooperating with sealing arrangements 11, 12 in order to seal the rotor in the rotor housing 1. The shaft journals 7a, 7b, 9a, 9b are also rotatably supported in the rotor housing 1 by bearings 13, 15.
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 An- triebszahnrades (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 upper rotor 3 in FIG. 1 is the main rotor and has an extension 7c of its shaft journal at its left end in FIG. Drive gear (not shown) is determined, which meshes with a corresponding gear of a drive gear (not shown) to drive the rotor 3 for rotation. At the right end in FIG. 1, the two rotors 3, 5 have two meshing gears 17, 19 which form a synchronizing gear which rotates from the upper rotor 3 to the lower rotor 5, which is the secondary rotor, in the desired speed ratio transmits.
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 the screw compressor shown in FIG. 1 is operating, its suction chamber 10, which is formed in the rotor housing 1 at the left end of the profile sections 7 and 9 in FIG. 1 and is connected to a suction nozzle (not shown), the gas to be compressed, in particular air , fed. The gas supplied is preferably already pre-compressed by one or more upstream compressor stages (not shown) to an intermediate pressure, for example to a pressure in the range from 10 to 15 bar, preferably approximately 12 bar. This precompressed gas is conveyed to the right by the profile sections 7, 9 of the two rotors 3, 5 in FIG. 1 and is compressed to a final pressure which is preferably in the range from 30 to 50 bar, in particular around 40 bar. The compressed gas leaves the rotor housing 1 at the right end of the profile sections 7, 9 in FIG. 1 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 predominantly formed in one piece with the rotor housing 1 and surrounds it at a distance. The cooling housing 21 has large openings at the top and bottom, which are closed by means of a cover plate 23 and a base plate 25 which are fastened by screws. Between the rotor housing 1 and the cooling housing 21, 23, 25 there is a cooling space 27 which surrounds the rotor housing 1 in a ring.
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 verschlos- sen 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 Ml, M2 der lotrecht übereinander angeordneten Schraubenrotoren. Figure 2 shows schematically and simplified a cross section approximately along the line II - II of Figure 1. The rotor housing 1 for receiving the screw rotors (not shown) is surrounded by the cooling jacket or cooling housing 21, the side walls 21a, 21b of which are preferably in one piece with the rotor housing 1 and which is closed at the top and bottom by the cover wall 23 or base plate 25. is. The cooling housing 21 forms with the rotor housing 1 a cooling space 27 which surrounds the rotor housing 1 in a substantially completely annular manner 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 29 runs horizontally approximately halfway between the axis centers Ml, M2 of the screw rotors arranged vertically one above the other.
Das Kühlgehäuse 21 weist eine Einlassöffhung 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 liquid, for. B. cooling water or oil. The inlet opening 31 opens into an inlet channel 35 which runs vertically upwards, the upper outlet opening 35 'of which is at a distance from the underside of the partition wall 29. In front of the outlet opening 33 there is a vertical outflow channel 37, the lower inlet opening 37 'of which faces the upper side of the partition wall 29 at a short distance.
Die schwarzen Pfeile in Figur 2 kennzeichnen den Strömungsweg des der Einlassöffnung 31 zugeführten Kühlmittels. Dieses wird durch den Einströmkanal 35 senkrecht nach The black arrows in FIG. 2 indicate the flow path of the coolant supplied to the inlet opening 31. This is perpendicular through the inflow channel 35
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. directed upwards against the underside of the partition 29, deflected sharply at this and then flows downward and clockwise in FIG. 2 around the entire circumference of the rotor housing 1 until it hits the top of the partition 29, deflected sharply upward therefrom 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, befullt werden kann und das Volumen der oberhalb des Flüssigkeitsspiegels 43 eingeschlossenen Restluft sehr gering ist. 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 Kühlflüssig- keitsspiegel 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 wall 39 separating the outflow channel 37 from the cooling space 1, a ventilation opening 41 with a small cross section is formed at a height which corresponds approximately to the upper limit of the outlet opening 33. Air can escape through this ventilation opening 41 when the cooling space 27 is filled with coolant, as indicated by the upper dotted arrows in FIG. 2, so that the cooling space 27 up to the height of the ventilation opening 41, ie up to that indicated by line 43 in FIG. 2 Liquid level, can be filled and the volume of the residual air trapped above the liquid level 43 is very small. A seepage opening 47 of very small cross-section is formed in the wall 45 separating the inflow channel 35 from the cooling space 27 at the lower limit of the inlet opening 31. When the cooling liquid is emptied 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. 2) until the cooling liquid level in the cooling space 27 has reached the height of the seepage opening 47, ie to has dropped to the level indicated by line 49. The residual amount of cooling liquid remaining below line 49 when the cooling chamber 27 is emptied is therefore very small.
Figur 3 zeigt weitere Details der Erfindung, 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 I Ia, I Ib. Bei der dargestellten Ausführungsform sind acht Ringdichtungen I Ia, I Ib hintereinander angeordnet. Bei den Ringdichtungen I Ia, 1 Ib 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 I Ia und einer zweiten Anzahl von Ringdichtungen 1 Ib liegt, ist die Dichtungsanordnung 11 von einem ersten ringförmigen Entlastungsraum 51 zum Auffangen von durch die Dichtungen I Ia 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 I Ia und den drei letzten, d. h. äußeren Ringdichtungen 1 Ib liegen. FIG. 3 shows further details of the invention which relate to the sealing arrangements 11 shown in FIG. 1 for sealing the pressure-side shaft journals 7b, 9b of the rotors 3, 5 in the rotor housing 1. As shown, the sealing arrangement 11 consists of a number of ring seals I Ia, I Ib arranged in a row. In the illustrated embodiment, eight ring seals I Ia, I Ib are arranged one behind the other. The ring seals I Ia, 1 Ib can preferably be lip seals, as such. B. is known from EP 0 993 553. At a suitable point, which lies between a first number of ring seals 11a and a second number of ring seals 11b, the seal arrangement 11 is surrounded by a first annular relief chamber 51 for collecting leakage gas passing through the seals 11a. In the embodiment of FIG. 3 with eight ring seals, the relief space 51 can advantageously be between the first number of five sealing rings 11a seen from the rotor profile 7 and the last three, i. H. outer ring seals are 1 Ib.
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 I Ia, I Ib 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 I Ib 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 I Ia, I Ib vergleichmäßigt, wodurch die Dichtungen I Ib mechanisch entlastet werden. The relief chamber 51 is connected to the suction chamber 10 of the screw compressor by a connecting channel 53 formed in the rotor housing 1 parallel to the rotor axis. The annular relief chamber 51 is therefore subjected to the suction pressure of the screw compressor prevailing in the suction chamber 10. In the preferred use of the screw compressor as a high-pressure stage of a multi-stage compressor unit, the air supplied to the suction chamber 10 can already be brought up to a pressure of, for example, upstream by the compressor stages. B. between 10 and 15 bar, in particular about 12 bar, and this is also the pressure prevailing in the relief chamber 51. In operation of the compressor, the high final pressure generated by the rotors, e.g. B. 40 bar, drop to zero via the sealing arrangement I Ia, I Ib. It has been shown that this pressure drop is not linear, but mainly concentrates on the outer ring seals 11b, which are more distant from the profile section 7, 9, and is therefore subject to very high mechanical loads. The first relief chamber 51, which is charged with the inlet pressure of the compressor, predefines a defined intermediate pressure at a defined point in the seal arrangement, thereby equalizing the pressure drop across the entire seal arrangement I Ia, I Ib, whereby the seals I Ib 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 ölgeschmier- ten Bereichen möglichst klein zu halten. At the end of the sealing arrangement 11 remote from the rotor, a second annular relief space 55 is provided, which is connected to the atmosphere in a manner known per se. The purpose of this second relief chamber 55 is to keep the oil system used for lubricating the bearings 15 and the synchronous gear 17, 19 free of pressure and to keep the leakage gas through the seal arrangement 11 to the oil-lubricated areas as small as possible.
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 shown in FIG. 2, the connecting channel 53 connecting the relief chamber 51 to the suction chamber 10 in the rotor housing 1 preferably runs in the immediate vicinity of the partition wall 29 connecting the rotor housing 1 to the cooling housing 21, thanks to the intensive cooling of the partition wall 29, which acts like a cooling fin the coolant deflected at it, the connecting channel 53, and thus the leakage gas flowing in it to the suction space 10, is subjected to particularly intensive cooling.

Claims

Ansprüche Expectations
1. Schraubenkompressor mit einem Rotorgehäuse (1), in dem zwei Schraubenrotoren (3, 5) drehbar gelagert sind, einem das Rotorgehäuse mit Abstand umgebenden Kühlgehäuse (21), das zusammen mit dem Rotorgehäuse (1) einen Kühlraum (27) bildet und mindestens eine Einlassöffhung (31) und eine Auslassöffhung (33) für ein den Kühlraum durchströmendes flüssiges Kühlmittel aufweist, 1. Screw compressor with a rotor housing (1) in which two screw rotors (3, 5) are rotatably mounted, a cooling housing (21) surrounding the rotor housing at a distance, which together with the rotor housing (1) forms a cooling space (27) and at least has an inlet opening (31) and an outlet opening (33) for a liquid coolant flowing through the cooling space,
dadurch gekennzeichnet, dass der Kühlraum (27) das Rotorgehäuse (1) ringförmig im Wesentlichen über seinen gesamten Umfang umgibt und nur an einer Stelle durch eine das Rotorgehäuse (1) mit dem Kühlgehäuse (21) verbindende Trennwand (29) unterbrochen ist,  characterized in that the cooling space (27) surrounds the rotor housing (1) in a ring substantially over its entire circumference and is interrupted only at one point by a partition (29) connecting the rotor housing (1) to the cooling housing (21),
und dass an die Einlassöffhung (31) ein Einströmkanal (35) angeschlossen ist, aus dem das Kühlmittel mit im Wesentlichen senkrecht gegen eine Seitenfläche der Trennwand (29) gerichteter Einströmrichtung in den Kühlraum (27) einströmt, und dass der Auslassöffhung (33) ein Ausströmkanal (37) vorgelagert ist, der eine der anderen Seitenfläche der Trennwand (29) im Wesentlichen senkrecht gegenüberstehende Einströmöffnung (37') aufweist, derart, dass das zugeführte Kühlmittel zunächst auf die eine Seite der Trennwand (29) auftrifft und an dieser umgelenkt wird, dann das Rotorgehäuse auf annähernd 360° seines Umfangs umströmt und dann an der anderen Seite der Trennwand (29) erneut umgelenkt und durch den Ausströmkanal abgezogen wird.  and that an inlet channel (35) is connected to the inlet opening (31), from which the coolant flows into the cooling space (27) with an inflow direction directed essentially perpendicularly against a side surface of the partition (29), and that the outlet opening (33) enters Outflow channel (37) is arranged upstream, which has an inflow opening (37 ') which is essentially perpendicular to the other side surface of the partition (29), such that the coolant supplied first hits one side of the partition (29) and is deflected thereon , then flows around the rotor housing to approximately 360 ° of its circumference and then deflected again on the other side of the partition (29) and is withdrawn through the outflow channel.
2. Schraubenkompressor nach Anspruch 1, dadurch gekennzeichnet, dass die Trennwand (29) horizontal verläuft, das einströmende Kühlmittel durch den Einströmkanal (35) im Wesentlichen vertikal nach oben gegen die Unterseite der Trennwand (29) gerichtet wird und nach Umströmen des Rotorgehäuses (1) an der Oberseite der Trennwand (29) erneut vertikal nach oben in den Ausströmkanal umgelenkt wird. 2. Screw compressor according to claim 1, characterized in that the partition (29) runs horizontally, the inflowing coolant through the inflow channel (35) is directed substantially vertically upwards against the underside of the partition (29) and after flowing around the rotor housing (1 ) at the top of the partition (29) is redirected vertically upwards into the outflow channel.
3. Schraubenkompressor nach Anspruch 1 und 2, dadurch gekennzeichnet, dass in der Wandung des Einströmkanals (35) in geringem Abstand von der unteren Wandung (25) des Kühlgehäuses (21) eine Sickeröffhung (47) geringen Querschnitts angeordnet ist. 3. Screw compressor according to claim 1 and 2, characterized in that in the wall of the inflow channel (35) at a short distance from the lower wall (25) of the cooling housing (21) a seepage opening (47) is arranged with a small cross-section.
4. Schraubenrotor nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, dass in der Wandung des Ausströmkanals (3, 7) in geringem Abstand von der oberen Wandung (23) des Kühlgehäuses eine Entlüftungsöffnung (41) geringen Querschnitts vorgesehen ist. 4. Screw rotor according to one of claims 1 to 3, characterized in that in the wall of the outflow channel (3, 7) at a short distance from the upper wall (23) of the cooling housing, a vent opening (41) is provided with a small cross-section.
5. Schraubenrotor nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, dass in der Wandung des Rotorgehäuses 1 in der Nähe der dieses mit dem Kühlgehäuse (21) verbindenden Trennwand (29) ein Verbindungskanal (53) ausgebildet ist, der einen Entlastungsraum (51), der eine die druckseitigen Wellenzapfen (7b, 9b) der Schraubenrotoren (3, 5) in dem Rotorgehäuse abdichtende Dichtungsanordnung (11) mit dem Ansaugraum (10) des Schraubenkompressors verbindet. 5. Screw rotor according to one of claims 1 to 4, characterized in that a connecting channel (53) is formed in the wall of the rotor housing 1 in the vicinity of the partition wall (29) connecting it to the cooling housing (21), which has a relief space (51 ), which connects a sealing arrangement (11) which seals the pressure-side shaft journals (7b, 9b) of the screw rotors (3, 5) in the rotor housing to the suction space (10) of the screw compressor.
EP06754260.5A 2005-12-08 2006-06-09 Helical screw compressor comprising a cooling jacket Active EP1957797B1 (en)

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EP06754260.5A Active EP1957797B1 (en) 2005-12-08 2006-06-09 Helical screw compressor comprising a cooling jacket
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WO2007065485A1 (en) 2007-06-14
EP1979618A1 (en) 2008-10-15
ES2359015T3 (en) 2011-05-17
CN101321954B (en) 2012-06-13
US20080286138A1 (en) 2008-11-20
US7713039B2 (en) 2010-05-11
EP1957797B1 (en) 2016-09-28
WO2007065486A1 (en) 2007-06-14
CN101321954A (en) 2008-12-10
EP1979618B1 (en) 2016-04-27
DE502006008894D1 (en) 2011-03-24
CN101321955A (en) 2008-12-10
US7690901B2 (en) 2010-04-06
WO2007065487A1 (en) 2007-06-14
US9091268B2 (en) 2015-07-28
HK1127111A1 (en) 2009-09-18
US20090004036A1 (en) 2009-01-01
EP1957798A1 (en) 2008-08-20
ATE498071T1 (en) 2011-02-15
EP1957798B1 (en) 2011-02-09
US20080286129A1 (en) 2008-11-20
EP1957799A1 (en) 2008-08-20
WO2007065484A1 (en) 2007-06-14
US20130011285A1 (en) 2013-01-10

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