EP1399677B1 - Two-stage helical screw compressor - Google Patents
Two-stage helical screw compressor Download PDFInfo
- Publication number
- EP1399677B1 EP1399677B1 EP02747418A EP02747418A EP1399677B1 EP 1399677 B1 EP1399677 B1 EP 1399677B1 EP 02747418 A EP02747418 A EP 02747418A EP 02747418 A EP02747418 A EP 02747418A EP 1399677 B1 EP1399677 B1 EP 1399677B1
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- EP
- European Patent Office
- Prior art keywords
- coolant
- housing
- rotor
- compressor
- stage
- 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
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Classifications
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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
- F04C18/12—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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
- F04C23/001—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
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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
- 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
Definitions
- the invention relates to a two-stage screw compressor according to the preamble of claim 1.
- a screw compressor is known inter alia from DE 299 22 878 U1. The disclosure of this document is fully incorporated by reference.
- each of the two parallel projecting from the gear housing compressor stages is surrounded by its own cooling housing, which is connected by its own connections to the coolant circuit and coolant sump. Due to the space requirement of said cooling housing of the two compressor stages, the construction of the known screw compressor is not particularly compact.
- a ringenlcompressor with two compressor stages is known, the compressor housing are arranged parallel to each other and surrounded by a common inner housing.
- the inner housing is concentrically surrounded by an outer housing, and the annular space between the inner and outer housing is divided into chambers, which are flowed through by a coolant, in order to cool arranged in the chambers tube bundles through which flows the compressed gas.
- a first coolant stream cools the compressed gas of the first compressor stage
- a second coolant stream cools the compressed gas of the second compressor stage.
- the coolant has essentially no direct cooling effect on the rotor housing of the two compressor stages.
- the object of the invention is to provide a two-stage screw compressor of the specified type with a particularly compact design, in which further simplifies the production and the utilization of the cooling effect of the coolant circuit is improved.
- the rotor housings of both compressor stages are arranged in a common cooling housing which surrounds them at a distance and are preferably produced integrally with the cooling housing.
- the cooling housing has only a coolant inlet and a coolant outlet and is designed such that a flow path is imposed on the coolant, which successively flows around and cools both rotor housings of the compressor stages.
- the illustrated in Fig. 1 to 5 two-stage screw compressor has a housing 1, which is provided with feet 3 for attachment to a substrate.
- the upper part 5 of the housing 1 has substantially the shape of a disk-shaped stator with two vertical end walls.
- a cooling housing 7 is freely cantilever mounted on the left in Fig. 2 end wall.
- the cooling housing 7 surrounds two compressor stages arranged in its interior, each consisting of a rotor housing and two screw rotors arranged therein, as will be explained with reference to FIG. 8. From the lower part of the housing 1 protrudes below the cooling housing 7 and at a distance from this an oil reservoir 9 out, which may also have feet 3 for support on the base.
- a drive unit 13 On the side facing away from the cooling housing 7 of the upper housing portion 5, a drive unit 13 is provided with a preferably speed-controlled motor, which drives the screw rotors of the compressor stages via a housing housed in the housing section 5 gear.
- the drive motor 13 may further drive an oil pump, which is arranged in a housing portion 14 between the drive unit 13 and the branching gear in the housing portion 5.
- the illustrated screw compressor is preferably a dry running screw compressor, i. the actual compressor chamber with the screw rotors therein is kept oil-free.
- the held by the oil pump in circulation oil is used on the one hand for lubrication of the transmission and the bearings of the screw rotors and on the other hand as a coolant for external cooling of the rotor housing of the two compressor stages.
- FIGS. 6 and 7 The part of the screw compressor, to which the invention mainly refers, namely the cooling housing 7 with the compressor stages arranged therein, is shown in FIGS. 6 and 7 in perspective from two different viewing directions and in FIG. 8 in section.
- a first compressor stage 15 (low-pressure stage) is located inside the cooling housing 7 with two intermeshing screw rotors 17, 19 which are mounted in a rotor housing 21 with a cross-sectionally 8-shaped, and axially parallel thereto a second compressor stage 23 (high-pressure stage) 23 with a pair of screw rotors 25, 27 which are mounted on an 8-shaped rotor housing 29.
- the cooling housing 7 is box-shaped with a substantially rectangular cross-section, so that it has two to the rotors 17, 19, 25, 27 parallel side walls 31, 35, a top 37 and a bottom 39.
- the cooling housing 7 openings which are closed by screwed plates 41, 43, 47.
- the cooling housing 7 merges into a large-area flange 49, which serves for fastening the cooling housing 7 to the transmission housing 5 and has an outer contour adapted thereto.
- the cooling housing 7 is closed at the end by a bearing cap 51, which is fastened with screws on the cooling housing 7.
- On the underside of the bearing cap 51 is an oil drain port 53, which is connected via a Rüclclauftechnisch 55 (Fig. 1-5) with the oil reservoir 9.
- the inlet opening 57 for sucking the gas to be compressed in the compression space in the rotor housing 21 of the first compressor stage 15.
- the outlet 59 for the compressed in the first stage gas is in the right in Fig. 7 (in Fig. 8 left) side wall 31.
- the inlet port 61 for the second compressor stage 23 is in the left in Fig. 6 (right in Fig. 8) side wall 35.
- the outlet port 59 of the low-pressure stage is connected to the inlet port 61 of the high pressure stage usually via an intercooler (not in the drawings ) shown.
- the intake opening 57 of the low-pressure stage upstream filter and / or muffler and the outlet 63 of the high-pressure stage downstream muffler, cooler and / or filters are of any known in the art construction.
- each of the four sides 31, 35, 37, 39 of the cooling housing 7 each one of the four ports of the two compressor stages (inlet and outlet ports 57, 59 of the low pressure stage 15, inlet and outlet ports 61, 63 of the high-pressure stage 23), resulting in a compact design with good utilization of existing on the four sides of the housing 7 place.
- the rotor housings 21, 29 of the two compressor stages 15, 23 are arranged at a sufficient distance from the walls of the cooling housing 7.
- the cooling housing 7 at the bottom 39 an inlet opening 65 for the cooling medium and in the upper region of the side wall 35 an outlet opening 67 for the cooling medium.
- the coolant supplied at the opening 65 flows through the cooling housing 7 to the outlet opening 67 on an S-shaped flow path, which is indicated by the dot-dash line 69.
- This flow path is forced by baffles 71, 73, which extend at appropriate locations through the gap between the rotor housings 21, 29 and the cooling housing 7.
- the flow path 69 first flows around the rotor housing 21 of the low-pressure stage 15 and then the rotor housing 29 of the high-pressure stage 23, in each case over a "wrap angle" of more than 180 °, preferably almost 360 °.
- the rotor housings 21, 29 of the compressor stages, the baffles 71, 73 and the cooling housing 7 are made as a one-piece housing block, as indicated by the uniform hatching in FIG.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
Abstract
Description
Die Erfindung betrifft einen zweistufigen Schraubenkompressor gemäß dem Oberbegriff des Anspruchs 1. Ein solcher Schraubenkompressor ist unter anderem aus DE 299 22 878 U1 bekannt. Auf die Offenbarung dieser Druckschrift wird in vollem Umfang Bezug genommen.The invention relates to a two-stage screw compressor according to the preamble of
Bei diesem bekannten zweistufigen Schraubenkompressor ist jede der beiden parallel zueinander vom Getriebegehäuse auskragenden Verdichterstufen von einem eigenen Kühlgehäuse umgeben, welches durch eigene Anschlüsse mit dem Kühlmittelkreislauf bzw. Kühlmittelsumpf verbunden ist. Aufgrund des Platzbedarfs der genannten Kühlgehäuse der beiden Verdichterstufen ist die Bauweise des bekannten Schraubenkompressors nicht besonders kompakt.In this known two-stage screw compressor each of the two parallel projecting from the gear housing compressor stages is surrounded by its own cooling housing, which is connected by its own connections to the coolant circuit and coolant sump. Due to the space requirement of said cooling housing of the two compressor stages, the construction of the known screw compressor is not particularly compact.
Das gleiche Problem besteht bei einem in US-A-5,785,149 beschriebenen zweistufigen Schraubenkompressor, dessen beide Verdichterstufen schematisch mit getrennten Gehäusen dargestellt sind, die durch eine Verbindungsleitung verbunden sind und vom Kühlmittel nacheinander durchströmt werden.The same problem exists in a two-stage screw compressor described in US-A-5,785,149, the two compressor stages are shown schematically with separate housings, which are connected by a connecting line and flows through the coolant in succession.
Aus US-A-4,174,196 ist ein Schraubenlcompressor mit zwei Verdichterstufen bekannt, deren Verdichtergehäuse parallel zueinander angeordnet und von einem gemeinsamen Innengehäuse umgeben sind. Das Innengehäuse ist konzentrisch von einem Außengehäuse umgeben, und der Ringraum zwischen Innen- und Außengehäuse ist in Kammern unterteilt, die von einem Kühlmittel durchströmt werden, um in den Kammern angeordnete Rohrbündel, durch die das verdichtete Gas strömt, zu kühlen. Ein erster Kühlmittelstrom kühlt das verdichtete Gas der ersten Verdichterstufe, ein zweiter Kühlmittelstrom das verdichtete Gas der zweiten Verdichterstufe. Das Kühlmittel hat im wesentlichen keine direkte Kühlwirkung auf die Rotorgehäuse der beiden Verdichterstufen.From US-A-4,174,196 a Schraubenlcompressor with two compressor stages is known, the compressor housing are arranged parallel to each other and surrounded by a common inner housing. The inner housing is concentrically surrounded by an outer housing, and the annular space between the inner and outer housing is divided into chambers, which are flowed through by a coolant, in order to cool arranged in the chambers tube bundles through which flows the compressed gas. A first coolant stream cools the compressed gas of the first compressor stage, a second coolant stream cools the compressed gas of the second compressor stage. The coolant has essentially no direct cooling effect on the rotor housing of the two compressor stages.
Aufgabe der Erfindung ist es, einen zweistufigen Schraubenkompressor der angegebenen Art mit besonders kompakter Bauweise zur Verfügung zu stellen, bei dem ferner die Herstellung vereinfacht und die Ausnutzung der Kühlwirkung des Kühlmittelkreislaufs verbessert wird.The object of the invention is to provide a two-stage screw compressor of the specified type with a particularly compact design, in which further simplifies the production and the utilization of the cooling effect of the coolant circuit is improved.
Die erfindungsgemäße Lösung der Aufgabe ist im Anspruch 1 angegeben. Die abhängigen Ansprüche beziehen sich auf weitere vorteilhafte Merkmale der Erfindung.The achievement of the object according to the invention is specified in
Erfindungsgemäß sind die Rotorgehäuse beider Verdichterstufen in einem gemeinsamen, sie mit Abstand umgebenden Kühlgehäuse angeordnet und vorzugsweise einstükkig mit dem Kühlgehäuse hergestellt. Das Kühlgehäuse weist nur einen Kühlmitteleinlaß und einen Kühlmittelauslaß auf und ist so ausgebildet, daß dem Kühlmittel ein Strömungsweg aufgezwungen wird, der nacheinander beide Rotorgehäuse der Verdichterstufen umspült und kühlt. Hierdurch wird eine besonders kompakte Bauweise sowie gleichzeitig eine Vereinfachung der Herstellung des Schraubenverdichters und eine verbesserte Ausnutzung des Kühlmittels erzielt.According to the invention, the rotor housings of both compressor stages are arranged in a common cooling housing which surrounds them at a distance and are preferably produced integrally with the cooling housing. The cooling housing has only a coolant inlet and a coolant outlet and is designed such that a flow path is imposed on the coolant, which successively flows around and cools both rotor housings of the compressor stages. As a result, a particularly compact design and at the same time a simplification of the production of the screw compressor and improved utilization of the coolant is achieved.
Eine weitere Möglichkeit zur besonders kompakten Ausbildung des Schraubenkompressors ergibt sich, wenn an jeder der vier Seiten des kastenförmigen Kühlgehäuses je einer der vier Anschlüsse der beiden Verdichterstufen (Ein- und Auslaß der Niederdruckstufe, Ein- und Auslaß der Hochdruckstufe) angeordnet ist. Es kann dann der auf jeder der Seitenflächen des Kühlgehäuses vorhandene Platz optimal für den jeweiligen dort angeordneten Anschluß genutzt werden, ohne durch einen weiteren Anschluß auf derselben Seite behindert zu sein.Another possibility for particularly compact design of the screw compressor results when each of the four sides of the box-shaped cooling housing one of the four ports of the two compressor stages (inlet and outlet of the low pressure stage, inlet and outlet of the high-pressure stage) is arranged. It can then be used optimally for the respective terminal arranged there on each of the side surfaces of the cooling housing without being hindered by another connection on the same side.
Eine Ausführungsform der Erfindung wird anhand der Zeichnungen näher erläutert. Es zeigt:
- Fig. 1
- eine perspektivische Ansicht eines Schraubenkompressors gemäß einer Ausführungsform der Erfindung,
- Fig. 2
- eine Seitenansicht eines Schraubenkompressors gemäß einer Ausführungsform der Erfindung in der Blickrichtung des Pfeiles A in Fig. 3,
- Fig. 3
- eine Stirnansicht des Schraubenkompressors in der Blickrichtung des Pfeiles B von Fig. 2,
- Fig. 4
- eine Seitenansicht in der Blickrichtung des Pfeiles C in Fig. 3,
- Fig. 5
- eine Draufsicht auf den Schraubenkompressor gemäß Fig. 2,
- Fig. 6
- eine perspektivische Darstellung des Kühlgehäuses des Schraubenkonipressors mit Blickrichtung von oben links,
- Fig. 7
- eine perspektivische Darstellung des Kühlgehäuses gemäß Fig. 6, jedoch in der Blickrichtung von unten rechts,
- Fig. 8
- einen achssenkrechten Querschnitt durch das Kühl-gehäuse und die Verdichterstufen gemäß der Schnittlinie und der Blickrichtung der Pfeile D-D von Fig. 4.
- Fig. 1
- a perspective view of a screw compressor according to an embodiment of the invention,
- Fig. 2
- a side view of a screw compressor according to an embodiment of the invention in the direction of arrow A in Fig. 3,
- Fig. 3
- an end view of the screw compressor in the viewing direction of the arrow B of Fig. 2,
- Fig. 4
- a side view in the direction of arrow C in Fig. 3,
- Fig. 5
- a plan view of the screw compressor of FIG. 2,
- Fig. 6
- a perspective view of the cooling housing of Schraubenkonipressors viewed from top left,
- Fig. 7
- a perspective view of the cooling housing of FIG. 6, but in the direction of the bottom right,
- Fig. 8
- an axially perpendicular cross section through the cooling housing and the compressor stages according to the section line and the viewing direction of the arrows DD of Fig. 4th
Der in Fig. 1 bis 5 dargestellte zweistufige Schraubenkompressor hat ein Gehäuse 1, das mit Füßen 3 zur Befestigung an einer Unterlage versehen ist. Der obere Teil 5 des Gehäuses 1 hat im wesentlichen die Form eines scheibenförmigen Ständers mit zwei vertikalen Stimwänden. An der in Fig. 2 linken Stirnwand ist frei auskragend ein Kühlgehäuse 7 angebracht. Das Kühlgehäuse 7 umgibt zwei in seinem Innern angeordnete Verdichterstufen, jede bestehend aus einem Rotorgehäuse und zwei darin angeordneten, miteinander kämmenden Schraubenrotoren, wie anhand von Fig. 8 noch erläutert wird. Vom unteren Teil des Gehäuses 1 ragt unterhalb des Kühlgehäuses 7 und mit Abstand zu diesem ein Ölvorratsbehälter 9 heraus, der ebenfalls Füße 3 zum Abstützen auf der Unterlage aufweisen kann. Auf der dem Kühlgehäuse 7 abgewandten Seite des oberen Gehäusebereichs 5 ist eine Antriebseinheit 13 vorgesehen mit einem vorzugsweise drehzahlgeregeltem Motor, der über ein im Gehäuseabschnitt 5 untergebrachtes Getriebe die Schraubenrotoren der Verdichterstufen antreibt. Der Antriebsmotor 13 kann ferner eine Ölpumpe antreiben, die in einem Gehäusebereich 14 zwischen der Antriebseinheit 13 und dem Verzweigungsgetriebe im Gehäusebereich 5 angeordnet ist.The illustrated in Fig. 1 to 5 two-stage screw compressor has a
Bei dem dargestellten Schraubenkompressor handelt es sich vorzugsweise um einen trockenlaufenden Schraubenkompressor, d.h. der eigentliche Verdichterraum mit den darin befindlichen Schraubenrotoren wird ölfrei gehalten. Das von der Ölpumpe in Zirkulation gehaltene Öl dient einerseits zur Schmierung des Getriebes und der Wälzlager der Schraubenrotoren und andererseits als Kühlmittel zur äußeren Kühlung der Rotorgehäuse der beiden Verdichterstufen.The illustrated screw compressor is preferably a dry running screw compressor, i. the actual compressor chamber with the screw rotors therein is kept oil-free. The held by the oil pump in circulation oil is used on the one hand for lubrication of the transmission and the bearings of the screw rotors and on the other hand as a coolant for external cooling of the rotor housing of the two compressor stages.
Bezüglich der Einzelheiten des Antriebs mit dem drehzahlgeregelten Antriebsmotor, des Verzweigungsgetriebes und der Integration der Ölpumpe in das Gehäuse wird im vollen Umfang auf die bereits genannte DE 299 22 878 U1 verwiesen. Das gilt auch für weitere, in dieser Schrift offenbarte vorteilhafte Merkmale, die auch bei dem Schraubenkompressor gemäß der vorliegenden Erfindung angewendet werden können, wie die innenliegend integrierte Ölpumpe, die keine Abdichtung erforderlich macht, die direkte Ankopplung des Motors an den Antriebszapfen des Getriebes, ohne die bisher übliche, platzbeanspruchende Kupplung, sowie die Auslegung des vom Motor angetriebenen Getriebes derart, daß innerhalb eines vorgegebenen Drehzahlbereiches des Motors, z.B. zwischen 2500 und 5500 U/Min ein optimierter Wirkungsgrad erreicht wird.With regard to the details of the drive with the variable speed drive motor, the branching gear and the integration of the oil pump in the housing is referred to the full extent to the already mentioned DE 299 22 878 U1. This also applies to other, disclosed in this document advantageous features that can be applied to the screw compressor according to the present invention, as the internally integrated oil pump, which does not require sealing, the direct coupling of the motor to the drive pin of the transmission, without the previously customary, space-consuming clutch, and the interpretation of the engine-driven transmission such that within a given speed range of the engine, eg between 2500 and 5500 rpm an optimized efficiency is achieved.
Der Teil des Schraubenkompressors, auf den sich die Erfindung hauptsächlich bezieht, nämlich das Kühlgehäuse 7 mit den darin angeordneten Verdichterstufen, ist in Fig. 6 und 7 perspektivisch aus zwei verschiedenen Blickrichtungen und in Fig. 8 im Schnitt dargestellt.The part of the screw compressor, to which the invention mainly refers, namely the cooling
Gemäß Fig. 8 befindet sich im Inneren des Kühlgehäuses 7 eine erste Verdichterstufe 15 (Niederdruclcstufe) mit zwei ineinandergreifenden Schraubenrotoren 17, 19, die in einem im Querschnitt 8-förmigen Rotorgehäuse 21 gelagert sind, und achsparallel dazu eine zweite Verdichterstufe 23 (Hochdruckstufe) 23 mit einem Paar Schraubenrotoren 25, 27, die einem 8-förmigen Rotorgehäuse 29 gelagert sind.According to FIG. 8, a first compressor stage 15 (low-pressure stage) is located inside the cooling
Das Kühlgehäuse 7 ist kastenförmig mit einem im wesentlichen rechteckigen Querschnitt, so daß es zwei zu den Rotoren 17, 19, 25, 27 parallele Seitenwände 31, 35, eine Oberseite 37 und eine Unterseite 39 aufweist.The cooling
An der Oberseite und Unterseite weist das Kühlgehäuse 7 Öffnungen auf, die durch aufgeschraubte Platten 41, 43, 47 verschlossen sind.At the top and bottom, the cooling
An einem seiner Enden geht das Kühlgehäuse 7 in einen großflächigen Flansch 49 über, der zur Befestigung des Kühlgehäuses 7 an dem Getriebegehäuse 5 dient und eine daran angepaßte Außenkontur aufweist. Am anderen Ende ist das Kühlgehäuse 7 stirnseitig durch einen Lagerdeckel 51 abgeschlossen, der mit Schrauben am Kühlgehäuse 7 befestigt ist. An der Unterseite des Lagerdeckels 51 befindet sich ein Ölablaufstutzen 53, der über eine Rüclclaufleitung 55 (Fig. 1-5) mit dem Ölvorratsbehälter 9 verbunden ist.At one of its ends, the cooling
An der Oberseite des Kühlgehäuses 7 befindet sich die Einlaßöffnung 57 zum Ansaugen des zu verdichtenden Gases in dem Verdichtungsraum im Rotorgehäuse 21 der ersten Verdichterstufe 15. Der Auslaß 59 für das in der ersten Stufe verdichtete Gas befindet sich in der in Fig. 7 rechten (in Fig. 8 linken) Seitenwand 31. An der Unterseite 39 des Kühlgehäuses 7 befindet sich die Einlaßöffnung 61 für die zweite Verdichterstufe 23 (Hochdruckstufe). Die Auslaßöffnung 63 der zweiten Verdichterstufe 23 befindet sich in der in Fig. 6 linken (in Fig. 8 rechten) Seitenwand 35. Die Auslaßöffnung 59 der Niederdruckstufe ist mit der Einlaßöffnung 61 der Hochdruckstufe in der Regel über einen Zwischenkühler verbunden (in den Zeichnungen nicht dargestellt). Ebenfalls nicht dargestellt sind die der Ansaug-öffnung 57 der Niederdruckstufe vorgeschalteten Filter und/oder Schalldämpfer sowie die dem Auslaß 63 der Hochdruckstufe nachgeschalteten Schalldämpfer, Kühler und/oder Filter. Diese Einrichtungen können von beliebiger, dem Fachmann bekannter Bauweise sein.At the top of the cooling
Bei der beschriebenen Ausführungsform ist an jeder der vier Seiten 31, 35, 37, 39 des Kühlgehäuses 7 je einer der insgesamt vier Anschlüsse der beiden Verdichterstufen (Ein- und Austrittsstutzen 57, 59 der Niederdruckstufe 15, Ein- und Austrittsstutzen 61, 63 der Hochdruckstufe 23) angeordnet, wodurch sich eine kompakte Bauweise mit guter Ausnutzung des an den vier Seiten des Gehäuses 7 vorhandenen Platzes ergibt.In the described embodiment, each of the four
Wie in Fig. 8 erkennbar, sind die Rotorgehäuse 21, 29 der beiden Verdichterstufen 15, 23 mit ausreichendem Abstand von den Wänden des Kühlgehäuses 7 angeordnet. In dem dadurch gebildeten Zwischenraum zirkuliert ein Kühlmedium zur gemeinsamen Kühlung der beiden Verdichterstufen 23, 15. Zu diesem Zweck weist das Kühlgehäuse 7 an der Unterseite 39 eine Einlaßöffnung 65 für das Kühlmedium und im oberen Bereich der Seitenwand 35 eine Auslaßöffnung 67 für das Kühlmedium auf. Das bei der Öffnung 65 zugeführte Kühlmittel strömt durch das Kühlgehäuse 7 zur Austrittsöffnung 67 auf einem S-förmigen Strömungsweg, der durch die strichpunktierte Linie 69 angedeutet ist. Dieser Strömungsweg wird durch Leitwände 71, 73 erzwungen, die sich an geeigneten Stellen durch den Zwischenraum zwischen den Rotorgehäusen 21, 29 und dem Kühlgehäuse 7 erstrecken. Der Strömungsweg 69 umströmt zuerst das Rotorgehäuse 21 der Niederdruclcstufe 15 und dann das Rotorgehäuse 29 der Hochdruckstufe 23, und zwar jeweils über einen "Umschlingungswinkel" von mehr als 180°, vorzugsweise nahezu 360°.As can be seen in FIG. 8, the
Vorzugsweise sind die Rotorgehäuse 21, 29 der Verdichterstufen, die Leitwände 71, 73 und das Kühlgehäuse 7 als ein einstückiger Gehäuseblock hergestellt, wie durch die einheitliche Schraffur in Fig. 8 angedeutet.Preferably, the
Claims (7)
- A two-stage screw compressor with two compressor stages (15, 23) that are parallel with respect to one another, each consisting of a pair of screw rotors (17, 19; 25, 27) that mesh together and are located in a rotor housing (21, 29), wherein each of the two rotor housings is surrounded by a coolant housing and is cooled by coolant that flows inside of the coolant housing, characterized in that both rotor housings (21, 29) are enclosed at a distance by a common coolant housing (7) and that the coolant housing (7) has one coolant inlet (65) and one coolant outlet (67) designed such that the coolant that flows from the inlet to the outlet passes around and cools both rotor housings (21, 29).
- A screw compressor according to claim 1, characterized in that the coolant first passes around and cools essentially one rotor housing (21) and then the other rotor housing (29) along its flow path from the inlet (65) to the outlet (67).
- A screw compressor according to claim 2, characterized in that the coolant first flows around the rotor housing (21) of the first compressor stage (15) (low-pressure stage) and then the rotor housing (29) of the second compressor stage (23) (high-pressure stage).
- A screw compressor according to one of claims 1 through 3, characterized in that the flow path (69) of the coolant proceeds in an S shape first around one compressor stage (23) and then around the other compressor stage (15).
- A screw compressor according to one of claims 1 through 4, characterized in that the intermediate space between the coolant housing (7) and the rotor housings (21, 29) is partitioned by means of guide walls (71, 73) that force the cooling medium to take the prescribed flow path (69).
- A screw compressor according to one of claims 1 through 5, characterized in that the rotor housings (21, 29) are designed as an integral block in one piece with at least a section of the coolant housing (7).
- A screw compressor according to one of claims 1 through 6, characterized in that the coolant housing (7) is designed essentially box-shaped with four sides (33, 35, 37, 39) that are parallel to the rotor axes of the compressor stages, and that the four connections (57, 59, 61, 63) of the compressor stages (15, 13) (inlet and outlet of the low pressure stage, inlet and outlet of the high pressure stage) are arranged one connection on each side of the coolant housing (7).
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE20110360U | 2001-06-22 | ||
| DE20110360U DE20110360U1 (en) | 2001-06-22 | 2001-06-22 | Two-stage screw compressor |
| PCT/EP2002/006853 WO2003001064A1 (en) | 2001-06-22 | 2002-06-20 | Two-stage helical screw compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| EP1399677A1 EP1399677A1 (en) | 2004-03-24 |
| EP1399677B1 true EP1399677B1 (en) | 2006-08-16 |
Family
ID=7958420
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| EP02747418A Expired - Lifetime EP1399677B1 (en) | 2001-06-22 | 2002-06-20 | Two-stage helical screw compressor |
Country Status (8)
| Country | Link |
|---|---|
| US (1) | US6991440B2 (en) |
| EP (1) | EP1399677B1 (en) |
| JP (1) | JP2004530836A (en) |
| CN (1) | CN1273744C (en) |
| AT (1) | ATE336659T1 (en) |
| DE (2) | DE20110360U1 (en) |
| ES (1) | ES2271293T3 (en) |
| WO (1) | WO2003001064A1 (en) |
Families Citing this family (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP4673136B2 (en) * | 2005-06-09 | 2011-04-20 | 株式会社日立産機システム | Screw compressor |
| EP1957797B1 (en) | 2005-12-08 | 2016-09-28 | GHH-RAND Schraubenkompressoren GmbH | Helical screw compressor comprising a cooling jacket |
| DE202007004292U1 (en) | 2007-03-23 | 2008-07-31 | Ghh-Rand Schraubenkompressoren Gmbh | Seal for shaft seals |
| CN101498304B (en) * | 2009-03-11 | 2011-06-15 | 宁波鲍斯能源装备股份有限公司 | Coal bed gas double screw rod compressor unit |
| US10047766B2 (en) | 2014-05-14 | 2018-08-14 | Ingersoll-Rand Company | Air compressor system |
| JP6573543B2 (en) * | 2015-12-17 | 2019-09-11 | 株式会社神戸製鋼所 | Screw compressor |
| JP6472373B2 (en) * | 2015-12-22 | 2019-02-20 | 株式会社神戸製鋼所 | Screw compressor |
| JP6744977B2 (en) | 2017-02-17 | 2020-08-19 | 三菱重工コンプレッサ株式会社 | Compressor module |
| CN110005610B (en) * | 2018-01-04 | 2022-07-26 | 复盛实业(上海)有限公司 | Interstage bleed air compressor |
| EP3816446A1 (en) * | 2019-10-31 | 2021-05-05 | Illinois Tool Works Inc. | Cooling circuit of a vehicule |
| CN115751772B (en) * | 2022-11-15 | 2023-09-15 | 大同云清科技有限公司 | Screw two-stage compressed air source heat pump |
Family Cites Families (15)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3129877A (en) * | 1956-05-17 | 1964-04-21 | Svenska Rotor Maskiner Ab | Rotary piston, positive displacement compressor |
| GB966752A (en) * | 1959-09-08 | 1964-08-12 | Svenska Rotor Maskiner Ab | Improvements in and relating to screw rotor compressors or vacuum pumps |
| US3910731A (en) * | 1970-07-09 | 1975-10-07 | Svenska Rotor Maskiner Ab | Screw rotor machine with multiple working spaces interconnected via communication channel in common end plate |
| US4174196A (en) * | 1976-07-28 | 1979-11-13 | Hitachi, Ltd. | Screw fluid machine |
| US4452575A (en) * | 1981-03-13 | 1984-06-05 | Svenska Rotormaskiner Ab | Method and device for intermediate cooling in an oil-injected multi-stage screw compressor |
| JPS61169688A (en) * | 1985-01-23 | 1986-07-31 | Hitachi Ltd | Screw fluid machinery |
| JPS6245992A (en) * | 1985-08-23 | 1987-02-27 | Anretsuto:Kk | Cooling device for vaccum-oriented multi-stage type roots blower |
| JP2588595B2 (en) * | 1988-09-30 | 1997-03-05 | 株式会社宇野澤組鐵工所 | Multi-stage rotary vacuum pump |
| FR2647853A1 (en) * | 1989-06-05 | 1990-12-07 | Cit Alcatel | DRY PRIMARY PUMP WITH TWO FLOORS |
| JP2572566Y2 (en) * | 1991-07-05 | 1998-05-25 | 株式会社 神戸製鋼所 | Air-cooled oil-free screw compressor |
| BE1009590A3 (en) * | 1995-09-12 | 1997-05-06 | Atlas Copco Airpower Nv | Screw kompressor. |
| SE512217C2 (en) * | 1998-06-17 | 2000-02-14 | Svenska Rotor Maskiner Ab | Two stage compressor and method for cooling the same |
| DE29922878U1 (en) * | 1999-12-28 | 2001-05-10 | GHH-RAND Schraubenkompressoren GmbH, 46145 Oberhausen | Two-stage dry-running screw compressor |
| JP2002155879A (en) * | 2000-11-22 | 2002-05-31 | Hitachi Ltd | Oil-free screw compressor |
| JP4493202B2 (en) * | 2000-12-01 | 2010-06-30 | 北越工業株式会社 | Oil-cooled screw two-stage compressor |
-
2001
- 2001-06-22 DE DE20110360U patent/DE20110360U1/en not_active Expired - Lifetime
-
2002
- 2002-06-20 DE DE50207867T patent/DE50207867D1/en not_active Expired - Lifetime
- 2002-06-20 WO PCT/EP2002/006853 patent/WO2003001064A1/en active IP Right Grant
- 2002-06-20 AT AT02747418T patent/ATE336659T1/en not_active IP Right Cessation
- 2002-06-20 CN CNB028021770A patent/CN1273744C/en not_active Expired - Lifetime
- 2002-06-20 EP EP02747418A patent/EP1399677B1/en not_active Expired - Lifetime
- 2002-06-20 ES ES02747418T patent/ES2271293T3/en not_active Expired - Lifetime
- 2002-06-20 JP JP2003507427A patent/JP2004530836A/en active Pending
-
2003
- 2003-09-30 US US10/675,315 patent/US6991440B2/en not_active Expired - Lifetime
Also Published As
| Publication number | Publication date |
|---|---|
| ATE336659T1 (en) | 2006-09-15 |
| WO2003001064A1 (en) | 2003-01-03 |
| EP1399677A1 (en) | 2004-03-24 |
| US6991440B2 (en) | 2006-01-31 |
| DE20110360U1 (en) | 2002-10-31 |
| JP2004530836A (en) | 2004-10-07 |
| DE50207867D1 (en) | 2006-09-28 |
| CN1463331A (en) | 2003-12-24 |
| ES2271293T3 (en) | 2007-04-16 |
| CN1273744C (en) | 2006-09-06 |
| US20040062668A1 (en) | 2004-04-01 |
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