EP3158198B1 - Machine à anneau liquide - Google Patents

Machine à anneau liquide Download PDF

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Publication number
EP3158198B1
EP3158198B1 EP15729826.6A EP15729826A EP3158198B1 EP 3158198 B1 EP3158198 B1 EP 3158198B1 EP 15729826 A EP15729826 A EP 15729826A EP 3158198 B1 EP3158198 B1 EP 3158198B1
Authority
EP
European Patent Office
Prior art keywords
compression stage
impeller
compression
pressure
compressor according
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
EP15729826.6A
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German (de)
English (en)
Other versions
EP3158198A1 (fr
Inventor
Heiner KÖSTERS
Inke WRAGE
Jörg WICKBOLD
Stefan LÄHN
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.)
Sterling Industry Consult GmbH
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Sterling Industry Consult GmbH
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Publication of EP3158198A1 publication Critical patent/EP3158198A1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C19/00—Rotary-piston pumps with fluid ring or the like, specially adapted for elastic fluids
    • F04C19/005—Details concerning the admission or discharge
    • F04C19/007—Port members in the form of side plates
    • 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
    • F04C27/00—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids
    • F04C27/001—Radial sealings for working fluid
    • 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
    • F04C29/0021—Systems for the equilibration of forces acting on the pump
    • F04C29/0035—Equalization of pressure pulses
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/20—Rotors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/30—Casings or housings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/60—Shafts
    • F04C2240/605—Shaft sleeves or details thereof
    • 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
    • F04C29/0042—Driving elements, brakes, couplings, transmissions specially adapted for pumps
    • F04C29/0078—Fixing rotors on shafts, e.g. by clamping together hub and shaft

Definitions

  • the invention relates to a liquid ring compression machine with a first compression stage, which has a first impeller mounted eccentrically in a housing, and a second compression stage, which has a second impeller mounted eccentrically in a housing. Both compression levels are single-acting. A sealing gap separates the first compression stage from the second compression stage.
  • liquid ring compression machines In liquid ring compression machines, a liquid ring is kept in motion by the impeller, so that the chambers between the blades of the impeller are closed by the liquid ring. Since the impeller is mounted eccentrically in the housing, the liquid ring penetrates the chamber to different extents depending on the angular position of the impeller and thus acts as a piston that changes the volume of the chamber. In the angular range in which the volume of the chamber is small, the gas to be compressed enters the chamber. With the rotation of the impeller, the volume of the chamber decreases and the compressed gas emerges again at the end of the compression process in a different angular position of the impeller.
  • liquid ring compression machines with two compression stages are known, for example from the DE 89 06 100 U1 or from the DE 890 256 C .
  • the invention is based on the object of presenting a liquid ring compression machine with improved efficiency. Starting from the prior art mentioned, the object is achieved with the features of claim 1. Advantageous embodiments are specified in the subclaims.
  • the sealing gap is arranged between a suction section of the first compression stage and a suction section of the second compression stage.
  • sealing gap As a sealing gap, the transition area between two becomes relative components of the compaction machine moving towards one another.
  • the sealing gap is designed so that the transition of a medium is severely hindered through the sealing gap.
  • suction section refers to a peripheral section of the compacting machine.
  • a chamber of the impeller passes through the suction section, the volume of the chamber enclosed between the blades and the liquid ring increases.
  • the gas to be compressed is supplied to the chamber.
  • a single-acting compression stage only one compression process occurs during a complete rotation (360 °) of a chamber of the impeller.
  • the chamber therefore only runs through a suction section and a pressure section.
  • the compression process regularly extends over a circumferential angle of more than 180 °.
  • first a first suction section and a first pressure section and then a second suction section and a second pressure section are passed through during a complete revolution.
  • the individual compression process extends over less than 180 °.
  • the pressure difference that is present across the sealing gap is minimized.
  • the pressure difference is only as great as the pressure difference between the suction section and the pressure section of the first compression stage. Due to the low pressure difference, the leakage loss through the sealing gap is kept low, which has a positive effect on the efficiency of the compression machine.
  • both compression stages exert a force in the same direction on the shaft.
  • the invention thus stands in contrast to the usual procedure according to which machines are designed in such a way that the internal forces cancel each other out as far as possible.
  • the suction sections of the two compression stages would be arranged offset by 180 ° so that the forces are opposed to one another.
  • the invention has recognized, however, that it is possible to absorb the forces that occur by means of structural measures and that the additional effort that this entails is low compared to the advantage that results in terms of efficiency. If the two compression stages were rotated by 180 ° in relation to each other, essentially the complete pressure difference of two compression stages would be present across the sealing gap between the suction section of the first compression stage and the pressure section of the second compression stage. The reduction in efficiency would be considerable.
  • the two compression stages are preferably driven by a common shaft so that the blades of the two compression stages move at the same angular speed.
  • the compaction machine can comprise a first control disk, which is assigned to the first compression stage, and a second control disk, which is assigned to the second compression stage.
  • the control disks have suction slots through which the gas to be compressed enters the chambers of the impeller.
  • the control disks also have pressure slots through which through the compressed gas emerges again from the chambers of the impeller.
  • the suction slots are arranged in the suction section of the compaction machine, the pressure slots are arranged in the pressure section of the compaction machine.
  • the two compression stages are preferably arranged between the first control disk and the second control disk.
  • the impeller of the first compression stage can be provided at the end opposite the first control disc with a wall which closes the chambers in the axial direction and which rotates with the impeller.
  • the impeller of the second compression stage can be provided with a wall which closes off the chambers in the axial direction.
  • the wall preferably extends in the radial direction at least as far as the outer end of the wings.
  • the impeller of the first compression stage and the impeller of the second compression stage can be separated from one another, so that each of the two impellers has such a wall.
  • the impellers of the two compression stages are elements of a one-piece component.
  • the one-piece component can be provided with a central partition which at the same time closes off the chambers of both compression stages.
  • the chambers of the first compression stage can be arranged offset in the circumferential direction relative to the chambers of the second compression stage. Both compression stages can have the same number of chambers.
  • the sealing gap can be between a peripheral surface of the wall and an adjacent end surface of the housing be trained.
  • the radial distance between the peripheral surface of the wall and the end surface of the housing is preferably less than 1 mm, preferably less than 0.5 mm, at room temperature.
  • a sealing element made of a flexible material can be arranged which is flush with both surfaces.
  • the impeller of the first compression stage can have the same diameter as the impeller of the second compression stage.
  • the invention thus differs from conventional compression machines in which two compression stages connected in series are regularly equipped with two different diameters according to the different pressure levels and compression capacities.
  • the first compression stage is overdimensioned in comparison, which makes it possible to keep the outlet pressure constant even with a reduced intake pressure.
  • the impeller of the first compression stage and the impeller of the second compression stage rotate within an interior of the housing.
  • the eccentric arrangement relates to this interior space.
  • the diameter of the interior space can be just as large in the first compression stage as in the second compression stage.
  • the interior can have a uniform contour over the first compression stage and the second compression stage. For each angular position it then applies that the distance from the wall of the interior to the center of the shaft in the first compression stage is the same as in the second compression stage.
  • the housing of the compression machine can have a channel which extends from the output side of the first compression stage to the input side of the second compression stage. In the axial direction, the channel preferably extends from the first control disk over the impellers of the two compression stages to the second control disk.
  • the channel can further comprise a section which extends over a circumferential section of at least 90 °, preferably at least 120 °, of the compacting machine.
  • the compression machine can be designed such that an input opening of the compression machine is connected to the input side of the first compression stage.
  • the inlet opening can be formed on a connecting piece which is provided with a flange for connecting a pipe.
  • An outlet opening of the compression machine can be connected to the outlet side of the second compression stage, which outlet can also be formed on such a connector.
  • the outlet side of the second compression stage is followed by a third compression stage.
  • the third compression stage preferably also comprises an impeller arranged in a housing.
  • the impeller of the third compression stage can be driven with the same shaft as the impeller of the first compression stage and the impeller of the second compression stage.
  • the third compression stage can be designed double-acting, which means that each chamber during one complete cycle goes through two compression processes.
  • the third compression stage therefore preferably comprises two suction sections and two pressure sections which are each offset by 180 ° to one another.
  • a channel can be formed which extends from the pressure slot of the second compression stage to the suction slots of the first compression stage.
  • the impeller of the third compression stage can be enclosed between two control discs.
  • the suction slots can be formed in one of the control disks and the pressure slots in the other control disk.
  • the output opening of the compaction machine can connect to the output side of the third compression stage.
  • the pressure difference between the first compression stage and the second compression stage creates a considerable force in the axial direction.
  • the compression machine can be equipped with sufficiently stable main bearings to absorb these axial forces.
  • the impeller of the third compression stage comprises a relief piston which closes off a pressure compensation chamber in the axial direction.
  • the hub of the impeller can be designed as a relief piston.
  • the pressure can be lower than on the outlet side of the third compression stage, preferably lower than on the inlet side of the third compression stage.
  • the pressure compensation chamber can be connected to the inlet side of the first compression stage via a duct. The axial pressure on the shaft is considerably reduced by this measure.
  • the compaction machine according to the invention preferably comprises a continuous shaft which extends over all compaction stages.
  • the shaft can be supported by a first main bearing and a second main bearing.
  • the two main bearings can be arranged in such a way that they enclose all compression stages between them.
  • the shaft can be free of other bearings between the two main bearings.
  • One of the main bearings can be designed as a tapered roller bearing, the main bearing preferably having two tapered roller bearings which are oriented in opposite directions. Such a main bearing is well designed to absorb axial forces.
  • the main bearing on the output side of the compaction machine is preferably designed as such a tapered roller bearing.
  • a main bearing can be used on the input side of the compaction machine, which has a lower capacity for axial forces.
  • the shaft is preferably held by the main bearings in such a way that it is free of play in the axial direction.
  • the end of the shaft on the pressure side is preferably arranged within the housing. The suction-side end of the shaft can protrude from the housing so that a drive motor can be connected there.
  • the impellers Since the impellers are operated with a very small distance from the control discs, the impellers should have an exactly defined position on the shaft.
  • spacer sleeves are provided which are arranged between the shaft and the impellers and which define the radial position of the impellers.
  • the spacer sleeves can be made of a different material than the shaft.
  • the shaft can consist of simple steel and the spacer sleeve of stainless steel.
  • the spacer sleeves are preferably designed so that they fit the shaft, that is, they are free of play in the radial direction and can be moved in the axial direction relative to the shaft. Within the impellers, the spacer sleeves are also free of play in the radial direction and displaceable in the axial direction.
  • Each impeller component can be enclosed between two spacer sleeves.
  • the impeller components can have a shoulder for each spacer sleeve on which the spacer sleeve rests in the axial direction and which defines an exact axial position for the spacer sleeve. In this way, the impellers and the spacer sleeves can form a fixed unit in relation to forces in the axial direction, in which each element has a defined position.
  • the position of this unit relative to the shaft can be defined, for example, by two shaft nuts between which the unit is clamped.
  • the unit preferably comprises two outer spacer sleeves and a central spacer sleeve, the two impellers each being arranged between an outer spacer sleeve and the central spacer sleeve.
  • the spacer sleeves can be designed as shaft protection sleeves which, through suitable seals, prevent contact between the conveyed medium and the shaft.
  • one of the spacer sleeves can be provided with a weakening, so that the stresses lead to a deformation of the spacer sleeve in the area of the Lead to weakening.
  • the other spacer sleeves then do not deform, so that the impellers continue to be held in the defined position.
  • the weakening can be designed, for example, as one or more grooves that extend over the circumference of the spacer sleeve.
  • all spacer sleeves that are arranged between an impeller and the input side of the compression machine are free of any weakening.
  • a spacer sleeve which is arranged between the impeller and a pressure-side end of the shaft is preferably weakened.
  • the sealing gap between the first compression stage and the second compression stage is used specifically for the supply of the operating fluid which forms the liquid ring.
  • the second compression stage is provided with a feed for operating fluid. Part of the operating fluid passes through the sealing gap into the first compression stage in order to form the fluid ring there.
  • the first compression stage can (apart from the sealing gap) be free of a supply line for operating fluid.
  • the amount of operating fluid passing through the sealing gap regulates itself, since the pressure in the first compression stage drops if the amount of operating fluid is too small. In this embodiment, it is not necessary to keep the sealing gap as small as possible, but the sealing gap can be adjusted according to the desired flow of operating fluid become.
  • the increase in efficiency according to the invention results from the fact that the operating fluid is supplied at a higher pressure instead of being conveyed from the first compression stage to the second compression stage.
  • the operating fluid with the required pressure is regularly available through fluid separators arranged on the pressure side of the compression machine.
  • the third compression stage can also be provided with a feed for operating fluid.
  • the compression machine according to the invention can be designed as a liquid ring compressor which is designed to discharge the gas on the outlet side at a pressure well above atmospheric pressure.
  • the outlet pressure is preferably higher than 8 bar, for example between 10 bar and 15 bar.
  • the pressure on the outlet side of the first compression stage can be, for example, between 2 bar and 3 bar and the pressure on the outlet side of the second compression stage can be between 4 bar and 6 bar.
  • the compressor according to the invention has a high pumping speed, which is why it can also be operated with a slight throttling without the pressure on the outlet side dropping significantly.
  • the pressure on the inlet side can be between 200 mbar and 500 mbar without the pressure on the outlet side falling below 10 bar.
  • the invention also relates to a method in which the compressor according to the invention is used in these pressure ranges.
  • the compression machine according to the invention can also be designed as a liquid ring vacuum pump which is designed to discharge the gas at approximately atmospheric pressure.
  • the compacting machine according to the invention can be intended for use in large industrial plants, such as refineries, where high volume flows are to be processed.
  • the compression machine can for example be designed for a drive power between 500 kW and 2 MW.
  • the compression machine can also be designed to suck in a volume flow between 800 m 3 / h and 3000 m 3 / h at atmospheric pressure.
  • the diameter of the shaft can, for example, be between 15 cm and 30 cm.
  • the compression of the gas in the compression machine according to the invention takes place essentially isothermally, since the gas is in intensive contact with the liquid ring during compression.
  • the temperature of the exiting gas can be adjusted via the temperature of the liquid ring.
  • the isothermal efficiency is defined as the quotient of the thermodynamic power additionally contained in the gas flow on the output side and the drive power on the shaft of the compression machine, if the temperature of the gas flow on the output side corresponds to the temperature on the input side.
  • this isothermal efficiency is between 30% and 50%, preferably between 35% and 50%.
  • the isothermal efficiency of previous liquid ring compression machines is in the order of 25% to 30%.
  • the liquid ring compressor shown comprises a housing 14 which stands on the floor via four legs 15 and in which a shaft 16 is rotatably mounted.
  • the shaft 16 extends the entire length of the compressor.
  • the three compression stages 17, 18, 19 of the compressor are driven jointly by the shaft 16.
  • a shaft journal 20 protruding from the housing 14 is used to connect a drive motor (not shown).
  • the drive motor can for example have a power of 1 MW.
  • the opposite end of the shaft 16 is disposed within the housing 14.
  • the compressor comprises an inlet opening 21 which extends through a nozzle which is provided with a flange. The gas is sucked into the compressor through the inlet opening 21.
  • the compressor also includes a correspondingly designed outlet opening 22 through which the compressed gas is released again. The compression takes place through the three compression stages 17, 18, 19 through which the gas passes one after the other.
  • FIG. 4 A one-piece component is attached to the shaft 16, on which an impeller 23 of the first compression stage 17 and an impeller 24 of the second compression stage 18 are formed.
  • the two impellers 23, 24 are separated from one another by a central wall 26.
  • an impeller 25 of the third compression stage 19 is connected to the shaft 16.
  • the impellers 23, 24, 25 rotate in the housing 14 together with the shaft 16.
  • the sectional view in Fig. 3 shows that the impellers 23, 24 are mounted eccentrically in the housing 14.
  • the distance between the shaft 16 and the upper end of the interior space surrounding the impellers 23, 24 is smaller than the distance between the shaft 16 and the lower end of the interior space.
  • the interior has a uniform contour, so that the distance between the shaft 16 and the wall of the interior is the same in every angular position for the first compression stage 17 and the second compression stage 18.
  • the chambers of the first impeller 23 thus have their smallest volume in the same angular position as the chambers of the second impeller 24. The same applies to the largest volume and the intermediate positions.
  • the angular section in which the volume of the chambers increases is called the suction section.
  • the angular segment in which the volume of the chambers is reduced is called the pressure segment.
  • the area below the shaft 16 belongs to the suction section 271, 272 and the area above the shaft to the pressure section 281, 282 of a complete revolution, the impellers 23, 24 pass through exactly one suction section 271, 272 and exactly one pressure section 281, 282.
  • the first compression stage 17 and the second compression stage 18 are therefore single-acting.
  • the compression process extends over more than 180 °.
  • the chambers of the impellers 23, 24 are each delimited by a control disk 29, 30.
  • the control disks 29, 30 each have a suction slot in the suction section 271, 272 and a pressure slot in the pressure section 281, 282.
  • the suction slot of the control disk 29 is connected to the inlet opening 21 of the compressor. The gas sucked in through the inlet opening 21 enters the chambers of the impeller 23 through this suction slot. With the rotation of the impeller 23, the volume of the chamber decreases and the compressed gas emerges again from the chambers of the impeller 23 through the pressure slot of the control disk 29. The compression process of the first compression stage 17 is thus completed. If the gas was sucked in at an atmospheric pressure of 1 bar, the pressure at the outlet of the first compression stage can for example be between 2 bar and 3 bar.
  • the compressed gas is conducted from the pressure slot of the control disk 29 to the suction slot of the control disk 30 through a channel 31 formed in the housing 14.
  • the gas enters the chambers of the impeller 24 through the suction slot. As the impeller 24 rotates, the gas is compressed further.
  • the gas exits the second compression stage 18 again through the pressure slot of the control disk 30 at a pressure between, for example, 4 bar and 6 bar.
  • the third impeller 25, which forms the third compression stage 19, is enclosed between a third control disk 32 and a fourth control disk 33.
  • the control disk 32 comprises two suction slots offset by 180 ° to one another.
  • the control disk 33 comprises two pressure slots offset from one another by 180 °.
  • the interior of the housing surrounding the third impeller 25 is designed in such a way that it forms two suction sections and two pressure sections.
  • the impeller 25 runs through two suction sections and two pressure sections during a complete revolution and thus performs two compression processes. Each compression process extends over less than 180 °, the third compression stage is double-acting.
  • the suction slots in the control disk 32 are positioned so that they provide access to the suction sections.
  • the printing slots in the control disk 33 are positioned so that they offer access to the printing sections.
  • the gas is directed to the suction slots in the control disk 32 so that it can enter the chambers of the impeller 25.
  • the gas exits the third compression stage through the pressure slots of the control disk 33 at a pressure between, for example, 10 bar and 15 bar. From there, the gas is led out of the compressor through the outlet opening 22.
  • a leakage flow can develop between the chambers of the second impeller 24 and the chambers of the first impeller 23.
  • the leakage flow passes through a sealing gap 28 between the partition 26 of the impellers 23, 24 and the surrounding housing.
  • the radial distance between the partition wall 26 and the housing is kept as small as possible and a sealing ring is also arranged in the sealing gap 28.
  • the leakage flow cannot be completely avoided with these measures.
  • the suction sections 271, 272 and the pressure sections 281, 282 of the first compression stage 17 and the second compression stage 18 are each arranged in the same angular position contributes to reducing the leakage flow.
  • the pressure difference between the first compression stage 17 and the second compression stage 18 is thus approximately the same in all angular positions and is of the order of only 2 bar to 3 bar. This small pressure difference also counteracts the creation of a strong leakage flow.
  • the angular position of the suction sections 271, 272 and the pressure sections 281, 282, which coincide in the first two compression stages 17, 18, also means that large forces act on the shaft 16 in the radial direction. These forces are absorbed in that the shaft 16 is made very solid.
  • the shaft can for example consist of steel and have a diameter of 20 cm. This dimensioning has proven to be sufficient to prevent the shaft 16 from bending excessively under the forces exerted by the impellers 23, 24.
  • the main bearing 35 is designed as a tapered roller bearing which, in addition to the radial forces, can also absorb large axial forces.
  • the second main bearing 34 primarily absorbs radial forces.
  • the shaft 16 is no longer supported between the two main bearings 34, 35.
  • vanes of the impellers 23, 24, 25 move as close as possible to the control disks 29, 30, 32, 33. This in turn presupposes that the impellers 23, 24, 25 are held in a specific position on the shaft 16 with high precision. In the case of the compressor according to the invention, this takes place in that spacer sleeves 36, 37, 38 are arranged between the impellers and the shaft 16 and define an exact position in the radial direction.
  • the spacer sleeves 36, 37, 38 also define exact positions in the axial direction in that they bear against suitable projections of the impellers 23, 24, 25 in the axial direction. With two shaft nuts 39, 40, the unit of spacer sleeves 36, 37, 38 and impellers 23, 24, 25 is clamped against one another in the axial direction, so that all elements have an exactly defined position.
  • the spacer sleeves 36, 37, 38 are made of stainless steel and thus of a different material than the shaft 16. If the compressor heats up, stresses can occur due to the different coefficients of thermal expansion.
  • the spacer sleeve 38 is between the third impeller 25 and the pressure-side Main bearing 35 is arranged, provided with internal grooves 41, which in the enlarged view of the Fig. 6 are shown.
  • the grooves 41 form a weakening of the spacer sleeve 38, so that deformation takes place in this area due to thermal expansion. This targeted deformation ensures that the axial position of the impellers 23, 24, 25 shifts only very slightly when the compressor is heated.
  • the hub 42 of the impeller 25 is designed as a pressure relief piston in order to reduce the axial pressure on the shaft 16.
  • the hub 42 In the direction of the pressure side, the hub 42 is adjoined by a cylindrical cavity 43 which is sealed off from the hub 42 by a sealing gap 44.
  • the cavity 43 is connected via a line 45 to the suction side of the compressor, on which there is essentially atmospheric pressure. As the atmospheric pressure is passed to the outlet side of the third compression stage 19, the axial pressure is reduced and the shaft 16 is relieved.
  • the second compression stage 18 and the third compression stage 19 are each connected to a feed line (not shown) for operating fluid, which is fed by a fluid separator arranged on the pressure side of the compressor.
  • the first compression stage 17 has no direct supply for operating fluid. Rather, the first compression stage is supplied with operating fluid through the sealing gap 28. The diameter of the sealing gap is selected so that the desired flow of operating fluid is achieved.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Claims (14)

  1. Machine de compression à anneau liquide, comprenant un premier étage de compression (17) à simple effet, qui possède un premier rotor (23) monté excentrique dans un carter (14), et comprenant un deuxième étage de compression (18) à simple effet, qui possède un deuxième rotor (24) monté excentrique dans un carter, le premier étage de compression (17) et le deuxième étage de compression (18) étant séparés l'un de l'autre par un interstice d'étanchéité (28), caractérisée en ce que l'interstice d'étanchéité (28) est disposé entre une portion d'aspiration (271) du premier étage de compression (17) et une portion d'aspiration (272) du deuxième étage de compression (18).
  2. Machine de compression à anneau liquide selon la revendication 1, caractérisée en ce que le premier étage de compression (17) possède un premier plateau de distribution (29), en ce que le deuxième étage de compression (18) possède un deuxième plateau de distribution (30), le premier rotor (23) et le deuxième rotor (24) étant disposés entre le premier plateau de distribution (29) et le deuxième plateau de distribution (30) .
  3. Machine de compression à anneau liquide selon la revendication 1 ou 2, caractérisée en ce qu'une paroi (26) qui tourne avec les rotors (23, 24) est formée entre les chambres du premier rotor (23) et les chambres du deuxième rotor (24).
  4. Machine de compression à anneau liquide selon la revendication 3, caractérisée en ce que l'interstice d'étanchéité (28) est disposé entre une surface périphérique de la paroi (26) et une surface de terminaison du carter (14).
  5. Machine de compression à anneau liquide selon l'une des revendications 1 à 4, caractérisée en ce que le carter (14) possède un canal (31) qui s'étend d'un côté de sortie du premier étage de compression (17) jusqu'à un côté d'entrée du deuxième étage de compression (18).
  6. Machine de compression à anneau liquide selon l'une des revendications 1 à 5, caractérisée en ce qu'un troisième étage de compression (19) se raccorde à un côté de sortie du deuxième étage de compression (18), un rotor (25) du troisième étage de compression (19) étant entraîné par le même arbre (16) que le premier rotor (23) et le deuxième rotor (24).
  7. Machine de compression à anneau liquide selon la revendication 6, caractérisée en ce que le troisième étage de compression (19) est conçu à double effet.
  8. Machine de compression à anneau liquide selon la revendication 6 ou 7, caractérisée en ce que le rotor (25) du troisième étage de compression (19) est disposé entre un premier plateau de distribution (32) et un deuxième plateau de distribution (33) et en ce que des fentes de refoulement sont formées dans le premier plateau de distribution (32) et dans le deuxième plateau de distribution (33).
  9. Machine de compression à anneau liquide selon l'une des revendications 6 à 8, caractérisée en ce que le rotor (25) du troisième étage de compression (19) possède un piston de détente (42), qui ferme un espace d'équilibrage de pression (43) dans la direction axiale, la pression dans l'espace d'équilibrage de pression (43) étant inférieure à celle du côté de la sortie du troisième étage de compression (19).
  10. Machine de compression à anneau liquide selon l'une des revendications 1 à 9, caractérisée en ce que chaque élément structural de rotor (23, 24, 25) est enfermé entre deux douilles d'espacement (36, 37, 38) dans la direction axiale.
  11. Machine de compression à anneau liquide selon la revendication 10, caractérisée en ce que l'une des douilles d'espacement (38) est pourvue d'un affaiblissement (41).
  12. Machine de compression à anneau liquide selon l'une des revendications 1 à 11, caractérisée en ce que le deuxième étage de compression (18) est équipé d'une arrivée pour du liquide de service et en ce que le premier étage de compression (17) est dépourvu d'une conduite d'arrivée pour du liquide de service.
  13. Machine de compression à anneau liquide selon l'une des revendications 1 à 12, caractérisée en ce que le troisième étage de compression (19) est équipé d'une arrivée pour du liquide de service.
  14. Machine de compression à anneau liquide selon l'une des revendications 1 à 13, caractérisée en ce qu'elle est conçue pour une puissance d'entraînement entre 500 kW et 2 MW.
EP15729826.6A 2014-06-18 2015-06-16 Machine à anneau liquide Active EP3158198B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
EP14173028 2014-06-18
PCT/EP2015/063481 WO2015193318A1 (fr) 2014-06-18 2015-06-16 Compresseur à anneau liquide

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EP3158198A1 EP3158198A1 (fr) 2017-04-26
EP3158198B1 true EP3158198B1 (fr) 2020-09-09

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EP15729826.6A Active EP3158198B1 (fr) 2014-06-18 2015-06-16 Machine à anneau liquide

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US (1) US10590932B2 (fr)
EP (1) EP3158198B1 (fr)
CN (1) CN106536936B (fr)
WO (1) WO2015193318A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2571969B (en) * 2018-03-14 2020-10-07 Edwards Tech Vacuum Engineering Qingdao Co Ltd A liquid ring pump manifold with an integrated spray nozzle
GB2571970B (en) * 2018-03-14 2020-09-16 Edwards Tech Vacuum Engineering (Qingdao) Co Ltd A liquid ring pump manifold with integrated non-return valve
CN109026737A (zh) * 2018-08-02 2018-12-18 广州市能动机电设备有限公司 一种离心式水泵

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE890256C (de) 1943-05-07 1953-09-17 Siemens Ag Fluessigkeitsring-Verdichter
DE923571C (de) 1951-10-14 1955-02-17 Amag Hilpert Pegnitzhuette Ag Einrichtung zum Verdichten von Gasen und Daempfen
FR1113561A (fr) 1954-04-06 1956-03-30 Siemens Ag Pompe à anneau liquide pour refoulement de gaz
DE1004334B (de) 1956-03-28 1957-03-14 Siemens Ag Fluessigkeitsringpumpe
FI46204C (fi) 1962-11-27 1973-01-10 Nash Engineering Co Suurtyhjönesterengas.
US4323334A (en) * 1980-01-25 1982-04-06 The Nash Engineering Company Two stage liquid ring pump
DE8906100U1 (fr) 1989-05-17 1989-06-29 Siemens Ag, 1000 Berlin Und 8000 Muenchen, De
FI103604B (fi) * 1996-08-05 1999-07-30 Rotatek Finland Oy Nesterengaskone ja menetelmä fluidin siirtämiseksi
DE19847681C1 (de) * 1998-10-15 2000-06-15 Siemens Ag Flüssigkeitsringpumpe
DE102005043434A1 (de) * 2005-09-13 2007-03-15 Gardner Denver Elmo Technology Gmbh Einrichtung zur Leistungsanpassung einer Flüssigkeitsringpumpe
CN101251125B (zh) * 2008-04-03 2010-10-27 湖北同方高科泵业有限公司 一种耐腐蚀水环真空泵
KR101583577B1 (ko) * 2009-02-05 2016-01-08 가드너 덴버 내쉬 엘엘씨 라이너를 포함한 액체 링 펌프

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

Also Published As

Publication number Publication date
EP3158198A1 (fr) 2017-04-26
US20170130718A1 (en) 2017-05-11
US10590932B2 (en) 2020-03-17
CN106536936A (zh) 2017-03-22
CN106536936B (zh) 2019-07-16
WO2015193318A1 (fr) 2015-12-23

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