EP3080455B1 - Compressor - Google Patents

Compressor Download PDF

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Publication number
EP3080455B1
EP3080455B1 EP14821504.9A EP14821504A EP3080455B1 EP 3080455 B1 EP3080455 B1 EP 3080455B1 EP 14821504 A EP14821504 A EP 14821504A EP 3080455 B1 EP3080455 B1 EP 3080455B1
Authority
EP
European Patent Office
Prior art keywords
compressor
bearing
lubricant
drive shaft
radial
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.)
Active
Application number
EP14821504.9A
Other languages
German (de)
French (fr)
Other versions
EP3080455A1 (en
Inventor
Wolfgang SANDKÖTTER
Bernd KWIATKOWSKI
Dmytro Zaytsev
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.)
GEA Refrigeration Germany GmbH
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GEA Refrigeration Germany GmbH
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Publication of EP3080455A1 publication Critical patent/EP3080455A1/en
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Publication of EP3080455B1 publication Critical patent/EP3080455B1/en
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Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/08Rotary-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
    • F04C18/12Rotary-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
    • F04C18/14Rotary-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
    • F04C18/16Rotary-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
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/0042Driving elements, brakes, couplings, transmissions specially adapted for pumps
    • F04C29/0085Prime movers
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/02Lubrication; Lubricant separation
    • F04C29/021Control systems for the circulation of the lubricant
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00Components
    • F04C2240/40Electric motor
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00Components
    • F04C2240/50Bearings
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00Components
    • F04C2240/50Bearings
    • F04C2240/52Bearings for assemblies with supports on both sides
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00Components
    • F04C2240/60Shafts
    • F04C2240/601Shaft flexion

Definitions

  • the present invention relates to a screw compressor according to the preamble of claim 1.
  • Such screw compressors are used in many applications because their construction is robust and the efficiency that can be achieved is high.
  • An electric motor is usually provided as the drive device for the actual compression device, which has, for example, two interlocking compression screws or screw rotors.
  • the motors of the compressors described above which can be designed as semi-hermetic compact screw compressors, for example, are mostly overhung.
  • the compressor rotor, ie a first compressor screw, and the motor rotor, ie the rotor of the electric motor are arranged on a common shaft (drive shaft) which has two radial bearing points.
  • a first radial bearing point is arranged on the compressor-side end of the shaft and a second radial bearing point is located on the shaft section between the compressor rotor and the motor rotor.
  • This means that the drive shaft or the rotor of the motor is only supported on one side of the motor.
  • the disadvantage here is that with increasing compressor size and with increasing Motor speed resonances can occur, which can lead to the starting of the motor rotor on the motor stator.
  • the EP 1 348 077 A1 a compressor is specified which has a third radial bearing in the form of a roller bearing at the motor-side end of the shaft. This means that the compressor motor is supported on both sides by means of roller bearings. Due to the three bearing points, however, the position of the drive shaft is overdetermined, which can only be compensated if the section of the drive shaft located between the first radial bearing and the third radial bearing is designed to compensate for any misalignment occurring between the radial bearings. This is achieved by a flexible section of the drive shaft.
  • Another compressor, which has roller bearings at all three bearing points, is from the WO 2013/126 970 A1 known.
  • the object of the present invention is to specify a compressor which prevents a collision of the rotor and stator of the motor and at the same time can be implemented in a simple and inexpensive manner.
  • a screw compressor for compressing refrigerant which has an electric motor with a rotor and a stator, as well as a drive shaft and a compression device with (at least) one compressor screw or (at least) one screw rotor, the Compressor screw and the rotor of the electric motor are arranged on or on the drive shaft.
  • the drive shaft is rotatably mounted by means of a first, a second and a third radial bearing and the first radial bearing is arranged between the rotor of the electric motor and the compressor screw.
  • the second radial bearing is arranged on a side of the compressor screw opposite the first radial bearing
  • the third radial bearing is arranged on a side of the rotor of the electric motor opposite the first radial bearing.
  • the first radial bearing and the second radial bearing are each designed as a roller bearing
  • the third radial bearing is designed as a plain bearing.
  • the plain bearing is connected to a lubricant feed and a lubricant discharge, the lubricant feed being connected to a first volume to which a first pressure can be applied and / or the lubricant discharge to a second volume to which a second pressure can be applied Connection.
  • the design of the third bearing as a slide bearing ensures a corresponding play at the bearing point itself, so that the position overdetermination of the drive shaft, which is caused by the bearing of the same in three points, can be compensated for without additional flexural elasticity of the drive shaft or other compensatory measures , while the two roller bearings ensure that the drive shaft is precisely positioned.
  • Fig. 1 is a possible embodiment of a compressor according to the invention, more precisely a screw compressor 10 according to the invention, which is also briefly below is referred to as compressor 10 is shown.
  • the compressor 10 has a housing 12 and an electric motor 14 arranged in the housing 12.
  • the electric motor 14 has a rotor 16 and a stator 18.
  • the screw compressor 10 has a drive shaft 20 and a compression device 22 with a first and a second intermeshing compressor screw or a first and a second intermeshing screw rotor 24 and 26, the first compressor screw 24 and the rotor 16 of the electric motor 14 on or on the Drive shaft 20 are arranged.
  • the drive shaft 20 is accordingly driven in rotation by the electric motor 14 and at the same time drives the compression device 22.
  • the compressor according to the invention can have only one compressor screw 24 or else three or more than three compressor screws.
  • the drive shaft 20 is rotatably mounted in the compressor 10 by means of a first, a second and a third radial bearing 27, 28 and 30, the first radial bearing 27 being arranged between the rotor 16 of the electric motor 12 and the first compressor screw 24.
  • the second radial bearing 28 is arranged on a side of the first compressor screw 24 opposite the first radial bearing 27, and the third radial bearing 30 is arranged on a side of the rotor 16 of the electric motor 12 opposite the first radial bearing 27.
  • the first and second radial bearings 27, 28 are designed as roller bearings
  • the third radial bearing 30 is designed as a plain bearing (here as a plain bearing with fluid friction or hydrodynamic plain bearing, but in alternative embodiments also as a dry running plain bearing).
  • a hydrodynamic slide bearing is also suitable for damping shaft movements and thus also and in particular for damping vibrations.
  • the third radial bearing 30, which is also referred to below as a sliding bearing 30, is connected to a lubricant feed 32 in the form of an oil feed channel and a lubricant discharge 34 in the form of an oil return channel.
  • the lubricant feed 32 is also connected to a first volume (oil distribution space, not shown in the figures), which can be acted upon by a first pressure, in the possible embodiment described here with a compression end pressure of the compressor.
  • the lubricant discharge 34 is also connected to a second volume (not shown in the figures), which can be acted upon by a second pressure, in the possible embodiment described here, approximately a suction pressure of the compressor 10.
  • the second volume is a closed compression work space of the compressor 10, i.e. the work space of the compressor 10, where the suction process has already ended and the compression process has just started. In this working space, the pressure is almost the same as the suction pressure.
  • This construction ensures a supply of lubricant under relatively high pressure, so that the bearing can take place as well as possible and without friction, ie with a lubricant film that is as closed as possible between the plain bearing 30 and the drive shaft 20.
  • the application of a relatively low pressure to the lubricant discharge 34 ensures a reliable discharge of the lubricant which, in the embodiment described here, is formed by the oil which the compressor 10 also uses as a lubricant.
  • the slide bearing 30 is arranged in a bearing receiving bush 36 which is at least partially arranged in the housing 12.
  • the bearing receiving bush 36 is arranged parallel and concentrically to the drive shaft 20.
  • the bearing receiving bushing 36 has a first end 38 through which the drive shaft 20 extends, and a second end 40 which is opposite the first end 38.
  • the bearing receiving bush 36 is sealed at both its first and its second end 38, 40 from the environment, ie the interior of the housing 12, the seal at the first end 38 through which the drive shaft 20 extends by means of a first Cover 42, which has a drive shaft passage 44 and a radial shaft seal 46, takes place.
  • a second cover 48 is arranged for sealing, which is attached to the second end 40 using suitable sealing materials, if necessary.
  • the second end can also be designed, for example, closed, i.e. the bearing receiving bushing 36 can alternatively be designed, for example, in the form of a blind hole or a cylinder closed on one side.
  • the sliding bearing 30 is arranged in a sealed manner from the environment, which means that no lubricant can escape to the environment.
  • the compressor 10 has a lubricant collecting space 50, which is arranged within the bearing receiving bush 36 in the embodiment described here and is connected to the lubricant discharge 34, for collecting and deliberately discharging the sliding bearing lubricant.
  • the lubricant collecting space is in fluid connection with the sliding bearing 30 or is open towards the sliding bearing 30 in order to be able to receive the lubricant of the sliding bearing 30 unhindered, while it is sealed against the environment in a similar way to the sliding bearing 30.
  • the seal against the environment takes place, as also for the slide bearing 30, by the first cover 42 including the radial shaft seal 46 and the second cover 48 limited, which are arranged at the radial ends of the bearing receiving sleeve 36.
  • the lubricant chamber 50 can also be arranged outside the bearing receiving bushing 36 and with the sliding bearing 30, for example be connected via a channel.
  • the lubricant can also be collected in a targeted manner through an additional formation of a lubricant collecting space 50 which is in connection with the sliding bearing (fluid connection, fluid communication).
  • a lubricant collecting space 50 which is in connection with the sliding bearing (fluid connection, fluid communication).
  • the fact that the sliding bearing 30 and the lubricant collecting chamber 50 are arranged sealed against the environment and the targeted removal of the lubricant means that there is no bearing-related lubricant entry into the suction gas flow of the compressor 10.
  • the pressurized lubricant supply leads to the best possible lubricating effect and thus to a further reduced heat development.

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

Description

Die vorliegende Erfindung betrifft einen Schraubenverdichter gemäß dem Oberbegriff des Patentanspruchs 1.The present invention relates to a screw compressor according to the preamble of claim 1.

Derartige Schraubenverdichter finden in vielen Anwendungen Verwendung, da ihre Konstruktion robust und die erzielbare Effizienz hoch ist. Als Antriebsvorrichtung für die eigentliche Verdichtungsvorrichtung, die beispielsweise zwei ineinandergreifende Verdichterschrauben bzw. Schraubenläufer aufweist, ist meist ein Elektromotor vorgesehen.Such screw compressors are used in many applications because their construction is robust and the efficiency that can be achieved is high. An electric motor is usually provided as the drive device for the actual compression device, which has, for example, two interlocking compression screws or screw rotors.

Die Motoren der vorstehend beschriebenen Verichter, die beispielsweise als semihermetischer Kompaktschraubenverdichter ausgebildet sein können, sind dabei meistens fliegend gelagert. Bei den Verdichtern dieser Art sind der Verdichterrotor, d.h. eine erste Verdichterschraube, und der Motorrotor, d.h. der Rotor des Elektromotors, an einer gemeinsamen Welle (Antriebswelle) angeordnet, die zwei Radiallagerstellen besitzt. Dabei ist eine erste Radiallagerstelle an dem verdichterseitigen Ende der Welle angeordnet und eine zweite Radiallagerstelle befindet sich an dem Wellenabschnitt zwischen dem Verdichterrotor und dem Motorrotor. Das heißt, eine Lagerung der Antriebswelle bzw. des Rotors des Motors ist nur an einer Seite des Motors vorhanden. Nachteilig dabei ist, dass mit der steigenden Verdichterbaugröße und mit der steigenden Motordrehzahl Resonanzen auftreten können, die zum Anlaufen des Motorrotors an den Motorstator führen können.The motors of the compressors described above, which can be designed as semi-hermetic compact screw compressors, for example, are mostly overhung. In compressors of this type, the compressor rotor, ie a first compressor screw, and the motor rotor, ie the rotor of the electric motor, are arranged on a common shaft (drive shaft) which has two radial bearing points. A first radial bearing point is arranged on the compressor-side end of the shaft and a second radial bearing point is located on the shaft section between the compressor rotor and the motor rotor. This means that the drive shaft or the rotor of the motor is only supported on one side of the motor. The disadvantage here is that with increasing compressor size and with increasing Motor speed resonances can occur, which can lead to the starting of the motor rotor on the motor stator.

Um dadurch entstehende Beschädigungen zu vermeiden wird in der EP 1 348 077 A1 ein Verdichter angegeben, der eine dritte Radiallagerstelle in Form eines Wälzlagers an dem motorseitigen Ende der Welle aufweist. Damit ist der Motor des Verdichters mittels Wälzlagern beidseitig gelagert. Aufgrund der drei Lagerstellen kommt es jedoch zu einer Überbestimmung der Position der Antriebswelle, die nur dadurch ausgeglichen werden kann,dass der sich zwischen dem ersten Radiallager und dem dritten Radiallager befindende Abschnitt der Antriebswelle zwischen den Radiallagern auftretende Fluchtungsfehler ausgleichend ausgebildet ist. Dies wird durch einen biegeelastischen Abschnitt der Antriebswelle realisiert. Ein weiterer Verdichter, der an allen drei Lagerstellen Wälzlager aufweist, ist aus der WO 2013/126 970 A1 bekannt.In order to avoid the resulting damage, the EP 1 348 077 A1 a compressor is specified which has a third radial bearing in the form of a roller bearing at the motor-side end of the shaft. This means that the compressor motor is supported on both sides by means of roller bearings. Due to the three bearing points, however, the position of the drive shaft is overdetermined, which can only be compensated if the section of the drive shaft located between the first radial bearing and the third radial bearing is designed to compensate for any misalignment occurring between the radial bearings. This is achieved by a flexible section of the drive shaft. Another compressor, which has roller bearings at all three bearing points, is from the WO 2013/126 970 A1 known.

Ferner ist aus der DE 197 44 466 A1 ein Schraubenverdichter mit einem Gehäuse bekannt, in dem ein Hauptläufer und ein Nebenläufer angeordnet sind, die jeweils eine Welle und einen Schraubenrotor aufweisen, wobei der Nebenläufer axial an dem Hauptläufer abgestützt ist, und wobei nur der Hauptläufer ein rotierendes Axiallagerteil aufweist, das an einem feststehenden Axiallagerteil des Gehäuses abgestützt ist.Furthermore, from the DE 197 44 466 A1 Known a screw compressor with a housing in which a main rotor and a secondary rotor are arranged, each having a shaft and a screw rotor, the secondary rotor being axially supported on the main rotor, and only the main rotor having a rotating axial bearing part which is attached to a stationary Axial bearing part of the housing is supported.

Die vorstehend beschriebene Konstruktion erfordert einen hohen konstruktiven und fertigungstechnischen Aufwand.The construction described above requires a high level of design and manufacturing effort.

Ausgehend hiervon ist es die Aufgabe der vorliegenden Erfindung, einen Verdichter, anzugeben, der eine Kollision von Rotor und Stator des Motors verhindert und gleichzeitig auf einfache und kostengünstige Art und Weise realisierbar ist.Based on this, the object of the present invention is to specify a compressor which prevents a collision of the rotor and stator of the motor and at the same time can be implemented in a simple and inexpensive manner.

Diese Aufgabe wird durch einen Verdichter mit den Merkmalen des Patentanspruchs 1 gelöst.This object is achieved by a compressor with the features of claim 1.

Demnach wird die Aufgabe durch einen Schraubenverdichter zum Verdichten von Kältemittel gelöst, der einen Elektromotor mit einem Rotor und einem Stator, sowie eine Antriebswelle und eine Verdichtungsvorrichtung mit (wenigstens) einer Verdichterschraube bzw. (wenigstens) einem Schraubenläufer aufweist, wobei die Verdichterschraube sowie der Rotor des Elektromotors an oder auf der Antriebswelle angeordnet sind. Die Antriebswelle ist mittels eines ersten, eines zweiten und eines dritten Radiallagers drehbar gelagert und das erste Radiallager ist zwischen dem Rotor des Elektromotors und der Verdichterschraube angeordnet. Das zweite Radiallager ist auf einer dem ersten Radiallager gegenüberliegenden Seite der Verdichterschraube angeordnet, und das dritte Radiallager ist auf einer dem ersten Radiallager gegenüberliegenden Seite des Rotors des Elektromotors angeordnet. Das erste Radiallager und das zweite Radiallager ist jeweils als Wälzlager ausgebildet, und das dritte Radiallager ist als Gleitlager ausgebildet. Das Gleitlager steht mit einer Schmiermittelzuführung und einer Schmiermittelabführung in Verbindung, wobei die Schmiermittelzuführung mit einem ersten Volumen, das mit einem ersten Druck beaufschlagbar ist, in Verbindung steht und/oder die Schmiermittelabführung mit einem zweiten Volumen, das mit einem zweiten Druck beaufschlagbar ist, in Verbindung steht.Accordingly, the object is achieved by a screw compressor for compressing refrigerant, which has an electric motor with a rotor and a stator, as well as a drive shaft and a compression device with (at least) one compressor screw or (at least) one screw rotor, the Compressor screw and the rotor of the electric motor are arranged on or on the drive shaft. The drive shaft is rotatably mounted by means of a first, a second and a third radial bearing and the first radial bearing is arranged between the rotor of the electric motor and the compressor screw. The second radial bearing is arranged on a side of the compressor screw opposite the first radial bearing, and the third radial bearing is arranged on a side of the rotor of the electric motor opposite the first radial bearing. The first radial bearing and the second radial bearing are each designed as a roller bearing, and the third radial bearing is designed as a plain bearing. The plain bearing is connected to a lubricant feed and a lubricant discharge, the lubricant feed being connected to a first volume to which a first pressure can be applied and / or the lubricant discharge to a second volume to which a second pressure can be applied Connection.

Die Ausbildung des dritten Lagers als Gleitlager sorgt für ein entsprechendes Spiel an der Lagerstelle selbst, so dass die Positions-Überbestimmung der Antriebswelle, die durch die Lagerung derselben in drei Punkten bedingt ist, ohne eine zusätzliche Biegeelastizität der Antriebswelle oder anderweitige kompensierende Maßnahmen kompensiert werden kann, während die beiden Wälzlager für eine positionsgenaue Lagerung der Antriebswelle sorgen.The design of the third bearing as a slide bearing ensures a corresponding play at the bearing point itself, so that the position overdetermination of the drive shaft, which is caused by the bearing of the same in three points, can be compensated for without additional flexural elasticity of the drive shaft or other compensatory measures , while the two roller bearings ensure that the drive shaft is precisely positioned.

Weitere optionale Merkmale der Erfindung sind in den Unteransprüchen, sowie der folgenden Figurenbeschreibung angegeben. Die beschriebenen jeweiligen Merkmale können einzeln oder in beliebigen Kombinationen realisiert sein.Die Erfindung wird demnach im Folgenden mit Bezug auf die beiliegenden Zeichnungen anhand von beispielhaften Ausführungsformen beschrieben. In den Zeichnungen zeigen:

  • Fig. 1 eine Schnittansicht einer beispielhaften Ausführungsform eines erfindungsgemäßen Verdichters; und
  • Fig. 2 eine vergrößerte Darstellung eines Teilbereichs des Verdichters gemäß Fig. 1.
Further optional features of the invention are specified in the subclaims and the following description of the figures. The respective features described can be implemented individually or in any combination. The invention is therefore described below with reference to the accompanying drawings on the basis of exemplary embodiments. In the drawings show:
  • Fig. 1 a sectional view of an exemplary embodiment of a compressor according to the invention; and
  • Fig. 2 an enlarged illustration of a portion of the compressor according to FIG Fig. 1 .

In Fig. 1 ist eine mögliche Ausführungsform eines erfindungsgemäßen Verdichters, genauer eines erfindungsgemäßen Schraubenverdichters 10, der nachstehend auch kurz als Verdichter 10 bezeichnet wird, dargestellt. Der Verdichter 10 weist ein Gehäuse 12 und einen in dem Gehäuse 12 angeordneten Elektromotor 14 auf. Der Elektromotor 14 weist einen Rotor 16 und einen Stator 18 auf. Ferner weist der Schraubenverdichter 10 eine Antriebswelle 20 und eine Verdichtungsvorrichtung 22 mit einer ersten und einer zweiten ineinandergreifenden Verdichterschraube bzw. einem ersten und einem zweiten ineinandergreifenden Schraubenläufer 24 und 26 auf, wobei die erste Verdichterschraube 24 sowie der Rotor 16 des Elektromotors 14 an oder auf der Antriebswelle 20 angeordnet sind. Die Antriebswelle 20 wird demnach durch den Elektromotor 14 dreh-angetrieben und treibt gleichzeitig die Verdichtungsvorrichtung 22 an. In alternativen Ausführungsformen kann der erfindungsgemäße Verdichter nur eine Verdichterschraube 24 oder aber auch drei oder mehr als drei Verdichterschrauben aufweisen.In Fig. 1 is a possible embodiment of a compressor according to the invention, more precisely a screw compressor 10 according to the invention, which is also briefly below is referred to as compressor 10 is shown. The compressor 10 has a housing 12 and an electric motor 14 arranged in the housing 12. The electric motor 14 has a rotor 16 and a stator 18. Furthermore, the screw compressor 10 has a drive shaft 20 and a compression device 22 with a first and a second intermeshing compressor screw or a first and a second intermeshing screw rotor 24 and 26, the first compressor screw 24 and the rotor 16 of the electric motor 14 on or on the Drive shaft 20 are arranged. The drive shaft 20 is accordingly driven in rotation by the electric motor 14 and at the same time drives the compression device 22. In alternative embodiments, the compressor according to the invention can have only one compressor screw 24 or else three or more than three compressor screws.

Die Antriebswelle 20 ist mittels eines ersten, eines zweiten und eines dritten Radiallagers 27, 28 und 30 im Verdichter 10 drehbar gelagert, wobei das erste Radiallager 27 zwischen dem Rotor 16 des Elektromotors 12 und der ersten Verdichterschraube 24 angeordnet ist. Das zweite Radiallager 28 ist auf einer dem ersten Radiallager 27 gegenüberliegenden Seite der ersten Verdichterschraube 24 angeordnet, und das dritte Radiallager 30 ist auf einer dem ersten Radiallager 27 gegenüberliegenden Seite des Rotors 16 des Elektromotors 12 angeordnet. Während das erste und das zweite Radiallager 27, 28 als Wälzlager ausgebildet sind, ist das dritte Radiallager 30 als Gleitlager (hier als Gleitlager mit Flüssigkeitsreibung bzw. hydrodynamisches Gleitlager, in alternativen Ausführungsformen aber auch als trocken laufendes Gleitlager) ausgebildet. An dieser Stelle sei angemerkt, dass ein hydrodynamisches Gleitlager auch zum Dämpfen von Wellenbewegungen und damit auch und insbesondere zur Dämpfung von Schwingungen geeignet ist.The drive shaft 20 is rotatably mounted in the compressor 10 by means of a first, a second and a third radial bearing 27, 28 and 30, the first radial bearing 27 being arranged between the rotor 16 of the electric motor 12 and the first compressor screw 24. The second radial bearing 28 is arranged on a side of the first compressor screw 24 opposite the first radial bearing 27, and the third radial bearing 30 is arranged on a side of the rotor 16 of the electric motor 12 opposite the first radial bearing 27. While the first and second radial bearings 27, 28 are designed as roller bearings, the third radial bearing 30 is designed as a plain bearing (here as a plain bearing with fluid friction or hydrodynamic plain bearing, but in alternative embodiments also as a dry running plain bearing). At this point it should be noted that a hydrodynamic slide bearing is also suitable for damping shaft movements and thus also and in particular for damping vibrations.

Das dritte Radiallager 30, das nachstehend auch als Gleitlager 30 bezeichnet sei, steht mit einer Schmiermittelzuführung 32 in Form eines Ölzufuhrkanals und einer Schmiermittelabführung 34 in Form eines Ölrückführungskanals in Verbindung. Die Schmiermittelzuführung 32 steht weiterhin mit einem ersten Volumen (Ölverteilungsraum, in den Figuren nicht dargestellt), das mit einem ersten Druck, in der hier beschriebenen möglichen Ausführungsform mit einem Verdichtungsenddruck des Verdichters beaufschlagbar ist, in Verbindung. Die Schmiermittelabführung 34 steht weiterhin mit einem zweiten Volumen (in den Figuren nicht dargestellt), das mit einem zweiten Druck, in der hier beschriebenen möglichen Ausführungsform in etwa einem Saugdruck des Verdichters 10 beaufschlagbar ist, in Verbindung. In der beschriebenen Ausführungsform handelt es sich bei dem zweiten Volumen um einen geschlossenen Verdichtungsarbeitsraum des Verdichters 10, d.h. den Arbeitsraum des Verdichters 10, wo der Ansaugvorgang bereits beendet ist und der Verdichtungsvorgang gerade begonnen hat. In diesem Arbeitsraum ist der Druck dem Saugdruck nahezu gleich.The third radial bearing 30, which is also referred to below as a sliding bearing 30, is connected to a lubricant feed 32 in the form of an oil feed channel and a lubricant discharge 34 in the form of an oil return channel. The lubricant feed 32 is also connected to a first volume (oil distribution space, not shown in the figures), which can be acted upon by a first pressure, in the possible embodiment described here with a compression end pressure of the compressor. The lubricant discharge 34 is also connected to a second volume (not shown in the figures), which can be acted upon by a second pressure, in the possible embodiment described here, approximately a suction pressure of the compressor 10. In the embodiment described, the second volume is a closed compression work space of the compressor 10, i.e. the work space of the compressor 10, where the suction process has already ended and the compression process has just started. In this working space, the pressure is almost the same as the suction pressure.

Diese Konstruktion sorgt für eine Zufuhr von Schmiermittel unter relativ hohem Druck, so dass die Lagerung möglichst gut und reibungsfrei, d.h. mit einem möglichst geschlossenen Schmiermittelfilm zwischen dem Gleitlager 30 und der Antriebswelle 20, erfolgen kann. Die Beaufschlagung der Schmiermittelabführung 34 mit einem relativ niedrigen Druck sorgt für eine zuverlässige Abführung des Schmiermittels, das in der vorliegend beschriebenen Ausführungsform durch das Öl, das auch der Verdichter 10 als Schmiermittel verwendet, gebildet wird.This construction ensures a supply of lubricant under relatively high pressure, so that the bearing can take place as well as possible and without friction, ie with a lubricant film that is as closed as possible between the plain bearing 30 and the drive shaft 20. The application of a relatively low pressure to the lubricant discharge 34 ensures a reliable discharge of the lubricant which, in the embodiment described here, is formed by the oil which the compressor 10 also uses as a lubricant.

Das Gleitlager 30 ist in einer Lageraufnahmebuchse 36 angeordnet, welche wenigsten teilweise in dem Gehäuse 12 angeordnet ist. Die Lageraufnahmebuchse 36 ist parallel und konzentrisch zu der Antriebswelle 20 angeordnet. Die Lageraufnahmebuchse 36 weist ein erstes Ende 38, durch welches sich die Antriebswelle 20 hindurcherstreckt, und ein zweites Ende 40 auf, das dem ersten Ende 38 gegenüberliegt.The slide bearing 30 is arranged in a bearing receiving bush 36 which is at least partially arranged in the housing 12. The bearing receiving bush 36 is arranged parallel and concentrically to the drive shaft 20. The bearing receiving bushing 36 has a first end 38 through which the drive shaft 20 extends, and a second end 40 which is opposite the first end 38.

Die Lageraufnahmebuchse 36 ist sowohl an ihrem ersten als auch an ihrem zweite Ende38, 40 gegen die Umgebung, d.h. den Innenraum des Gehäuses 12, hin abgedichtet, wobei die Abdichtung an dem ersten Ende 38, durch welches sich die Antriebswelle 20 hindurcherstreckt, mittels eines ersten Deckels 42, welcher eine Antriebswellendurchführung 44 und eine Radialwellendichtung 46 aufweist, erfolgt. Am zweiten Ende 40 ist zur Abdichtung ein zweiter Deckel 48 angeordnet, welcher ggf. unter Verwendung geeigneter Dichtmaterialien am zweiten Ende 40 angebracht ist.The bearing receiving bush 36 is sealed at both its first and its second end 38, 40 from the environment, ie the interior of the housing 12, the seal at the first end 38 through which the drive shaft 20 extends by means of a first Cover 42, which has a drive shaft passage 44 and a radial shaft seal 46, takes place. At the second end 40, a second cover 48 is arranged for sealing, which is attached to the second end 40 using suitable sealing materials, if necessary.

Alternativ hierzu kann das zweite Ende jedoch auch beispielsweise geschlossen ausgebildet sein, d.h. die Lageraufnahmebuchse 36 kann alternativ beispielsweise in Form eines Sacklochs oder eines an einer Seite geschlossenen Zylinders ausgebildet sein. Dadurch ist das Gleitlager 30 gegen die Umgebung hin abgedichtet angeordnet, was dazu führt, dass kein Schmiermittel zu der Umgebung hin austreten kann.As an alternative to this, however, the second end can also be designed, for example, closed, i.e. the bearing receiving bushing 36 can alternatively be designed, for example, in the form of a blind hole or a cylinder closed on one side. As a result, the sliding bearing 30 is arranged in a sealed manner from the environment, which means that no lubricant can escape to the environment.

Der Verdichter 10 weist zum Sammeln und gezielten Abführen des Gleitlager-Schmiermittels einen in der vorliegend beschriebenen Ausführungsform innerhalb der Lageraufnahmebuchse 36 angeordneten Schmiermittelsammelraum 50 auf, der mit der Schmiermittelabführung 34 in Verbindung steht. Der Schmiermittelsammelraum steht mit dem Gleitlager 30 in Fluidverbindung bzw. ist gegen das Gleitlager 30 hin offen, um ungehindert Schmiermittel des Gleitlagers 30 aufnehmen zu können, während er analog zum Gleitlager 30 gegen die Umgebung hin abgedichtet ist.The compressor 10 has a lubricant collecting space 50, which is arranged within the bearing receiving bush 36 in the embodiment described here and is connected to the lubricant discharge 34, for collecting and deliberately discharging the sliding bearing lubricant. The lubricant collecting space is in fluid connection with the sliding bearing 30 or is open towards the sliding bearing 30 in order to be able to receive the lubricant of the sliding bearing 30 unhindered, while it is sealed against the environment in a similar way to the sliding bearing 30.

Die Abdichtung gegen die Umgebung erfolgt, wie auch für das Gleitlager 30, durch den ersten Deckel 42 samt Radialwellendichtung 46 und den zweiten Deckel 48. Der Schmiermittelsammelraum 50 wird demnach von einer Innenwand 52 der Lageraufnahmebuchse 36, sowie dem ersten und zweiten Deckel 42, 48 begrenzt, welche an den radialen Enden der Lageraufnahmebuchse 36 angeordnet sind. Der Schmiermittelsamelraum 50 kann in alternativen Ausführungsformen auch außerhalb der Lageraufnahmebuchse 36 angeordnet sein und mit dem Gleitlager 30 beispielsweise über einen Kanal verbunden sein.The seal against the environment takes place, as also for the slide bearing 30, by the first cover 42 including the radial shaft seal 46 and the second cover 48 limited, which are arranged at the radial ends of the bearing receiving sleeve 36. In alternative embodiments, the lubricant chamber 50 can also be arranged outside the bearing receiving bushing 36 and with the sliding bearing 30, for example be connected via a channel.

Durch die Verwendung des Gleitlagers 30 mit mit Flüssigkeitsreibung wird für eine möglichst geringe Wärmebildung im Bereich der Lagerstelle gesorgt. Durch eine zusätzliche Ausbildung eines Schmiermittelsammelraums 50, welcher mit dem Gleitlager in Verbindung (Fluidverbindung, Fluidkommunikation) steht, kann das Schmiermittel zusätzlich gezielt gesammelt werden. Dadurch dass das Gleitlager 30, sowie der Schmiermittelsammelraum 50 gegen die Umgebung hin abgedichtet angeordnet sind und durch die gezielte Abfuhr des Schmiermittels kommt es zu keinem Lager-bedingten Schmiermitteleintrag in den Sauggasstrom des Verdichters 10. Die druckbeaufschlagte Schmiermittelzuführung führt zu einer möglichst guten Schmierwirkung und somit zu einer nochmals verringerten Wärmeentwicklung.By using the plain bearing 30 with fluid friction, the lowest possible heat build-up is ensured in the area of the bearing point. The lubricant can also be collected in a targeted manner through an additional formation of a lubricant collecting space 50 which is in connection with the sliding bearing (fluid connection, fluid communication). The fact that the sliding bearing 30 and the lubricant collecting chamber 50 are arranged sealed against the environment and the targeted removal of the lubricant means that there is no bearing-related lubricant entry into the suction gas flow of the compressor 10. The pressurized lubricant supply leads to the best possible lubricating effect and thus to a further reduced heat development.

Obwohl die Erfindung anhand von Ausführungsformen mit festen Merkmalskombinationen beschrieben wird, umfasst sie jedoch auch die denkbaren weiteren vorteilhaften Kombinationen, wie sie durch die Unteransprüche angegeben sind. Sämtliche in den Anmeldungsunterlagen offenbarten Merkmale werden als erfindungswesentlich angesehen, soweit sie einzeln oder in Kombination gegenüber dem Stand der Technik neu sind.Although the invention is described on the basis of embodiments with fixed combinations of features, it also encompasses the further conceivable advantageous combinations as indicated by the subclaims. All of the features disclosed in the application documents are considered essential to the invention insofar as they are new to the state of the art, individually or in combination.

BezugszeichenlisteList of reference symbols

1010
Verdichtercompressor
1212th
Gehäusecasing
1414th
ElektromotorElectric motor
1616
Rotorrotor
1818th
Statorstator
2020th
Antriebswelledrive shaft
2222nd
VerdichtungsvorrichtungCompaction device
2424
erste Verdichterschraubefirst compressor screw
2626th
zweite Verdichterschraubesecond compressor screw
2727
erstes Radiallagerfirst radial bearing
2828
zweites Radiallagersecond radial bearing
3030th
drittes Radiallagerthird radial bearing
3232
SchmiermittelzuführungLubricant supply
3434
SchmiermittelabführungLubricant discharge
3636
LageraufnahmebuchseBearing bushing
3838
erstes Ende der Lageraufnahmebuchse 36first end of the bearing receiving sleeve 36
4040
zweites Ende der Lageraufnahmebuchse 36second end of bearing receptacle 36
4242
erster Deckelfirst lid
4444
AntriebswellendurchführungDrive shaft feed-through
4646
RadialwellendichtungRadial shaft seal
4848
zweiter Deckelsecond lid
5050
SchmiermittelsammelraumLubricant collection space
5252
Innenwand der Lageraufnahmebuchse 36Inner wall of the bearing receiving bush 36

Claims (10)

  1. A screw compressor (10) for compressing refrigerant, comprising an electric motor (14), which has a rotor (16) and a stator (18), and also a drive shaft (20) and a compressing device (22) with a compressor screw (24), wherein the compressor screw (24) and the rotor (16) of the electric motor (14) are arranged against or on the drive shaft (20), wherein the drive shaft (20) is rotatably mounted by means of a first, a second and a third radial bearing (27, 28, 30), wherein the first radial bearing (27) is arranged between the rotor (16) of the electric motor (14) and the compressor screw (24), wherein the second radial bearing (28) is arranged on a side of the compressor screw (24) opposite the first radial bearing (27), and wherein the third radial bearing (30) is arranged on a side of the rotor (16) of the electric motor (14) opposite the first radial bearing (27),
    characterized in that
    the first radial bearing and the second radial bearing are each designed as rolling bearings, and the third radial bearing (30) is designed as a plain bearing, wherein
    the plain bearing (30) communicates with a lubricant inlet (32) and with a lubricant outlet (34), wherein the lubricant inlet (32) communicates with a first volume which can be subjected to a first pressure and/or the lubricant outlet (34) communicates with a second volume which can be subjected to a second pressure.
  2. The compressor (10) as claimed in claim 1, characterized in that the first volume can be subjected to approximately a compression end pressure of the compressor (10).
  3. The compressor (10) as claimed in claim 1 or claim 2, characterized in that the second volume can be subjected to approximately a suction pressure of the compressor (10).
  4. The compressor (10) as claimed in one of the preceding claims, characterized in that the lubricant outlet communicates with a closed compression work chamber.
  5. The compressor (10) as claimed in one of the preceding claims, characterized in that the compressor (10) has a lubricant collection chamber (50) for lubricant of the plain bearing.
  6. The compressor (10) as claimed in claim 5, characterized in that the lubricant collection chamber (50) communicates with a/the lubricant outlet (32).
  7. The compressor (10) as claimed in one of claims 5 or 6, characterized in that the plain bearing (30) and the lubricant collection chamber (50) are sealed off from the environment.
  8. The compressor (10) as claimed in one of the preceding claims, characterized in that the plain bearing (30) is arranged in a bearing bushing (36) which has a first end (38), through which the drive shaft (20) extends, and a second end (40), wherein the bearing bushing (36) is sealed off from the environment both at its first end (38) and at its second end (40), wherein the seal at the first end (38), through which the drive shaft (20) extends, is embodied by means of a first cover (42), which has a drive shaft passage (44) and a radial shaft seal (46).
  9. The compressor as claimed in one of claims 5 through 8, characterized in that the lubricant collection chamber (50) is delimited by an inner wall (52) of a/the bearing bushing (36) and by a/the first and second cover (42, 44), which are arranged at radial ends of the bearing bushing (36) .
  10. The compressor as claimed in one of the preceding claims, characterized in that the plain bearing is designed as a hydrodynamic plain bearing.
EP14821504.9A 2013-12-12 2014-12-12 Compressor Active EP3080455B1 (en)

Applications Claiming Priority (2)

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DE102013020535.2A DE102013020535A1 (en) 2013-12-12 2013-12-12 compressor
PCT/EP2014/003342 WO2015086158A1 (en) 2013-12-12 2014-12-12 Compressor

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EP3080455A1 EP3080455A1 (en) 2016-10-19
EP3080455B1 true EP3080455B1 (en) 2021-09-22

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US (1) US20160327040A1 (en)
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CN (1) CN105874205A (en)
DE (1) DE102013020535A1 (en)
WO (1) WO2015086158A1 (en)

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Publication number Priority date Publication date Assignee Title
DE102015113698B4 (en) * 2015-08-19 2021-11-11 Knorr-Bremse Systeme für Schienenfahrzeuge GmbH Compressor unit with flanged electric motor
JP6835681B2 (en) * 2017-07-18 2021-02-24 日立ジョンソンコントロールズ空調株式会社 Screw fluid machine
DE102018130472A1 (en) * 2018-11-30 2020-06-04 Nidec Gpm Gmbh Screw pump

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Publication number Priority date Publication date Assignee Title
JPS4975104U (en) * 1972-10-14 1974-06-28
JPS54154811A (en) * 1978-05-26 1979-12-06 Hitachi Ltd Screw compressor
DE3106483A1 (en) * 1981-02-21 1982-09-09 Allweiler Ag, 7760 Radolfzell Pump unit without stuffing box
DE19744466C2 (en) * 1997-10-08 1999-08-19 Kt Kirsten Technologie Entwick Screw compressor
JP3668616B2 (en) * 1998-09-17 2005-07-06 株式会社日立産機システム Oil-free screw compressor
DE10101016A1 (en) * 2001-01-05 2002-07-25 Bitzer Kuehlmaschinenbau Gmbh Refrigerant compressor
BE1013944A3 (en) * 2001-03-06 2003-01-14 Atlas Copco Airpower Nv Water injected screw compressor.
DE102006028291B4 (en) * 2006-06-20 2013-10-24 Gea Grasso Gmbh Arrangement of an oil pump in the screw compressor
CN201321981Y (en) * 2008-11-28 2009-10-07 武汉凯龙技术开发有限责任公司 Large-sized semi-enclosed screw type refrigeration compressor
JP2012515303A (en) * 2009-01-12 2012-07-05 ダウ グローバル テクノロジーズ エルエルシー Improved journal bearing structure
DE102011054607A1 (en) * 2010-10-27 2012-06-21 Gebr. Becker Gmbh vacuum pump
BE1020311A3 (en) * 2012-02-28 2013-07-02 Atlas Copco Airpower Nv SCREW COMPRESSOR.

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US20160327040A1 (en) 2016-11-10
EP3080455A1 (en) 2016-10-19
WO2015086158A1 (en) 2015-06-18
DE102013020535A1 (en) 2015-06-18

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