EP4330552B1 - Système d'entraînement pour un compresseur à vis à plusieurs étapes - Google Patents

Système d'entraînement pour un compresseur à vis à plusieurs étapes

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Publication number
EP4330552B1
EP4330552B1 EP22725469.5A EP22725469A EP4330552B1 EP 4330552 B1 EP4330552 B1 EP 4330552B1 EP 22725469 A EP22725469 A EP 22725469A EP 4330552 B1 EP4330552 B1 EP 4330552B1
Authority
EP
European Patent Office
Prior art keywords
drive
compressor
shaft
main rotor
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.)
Active
Application number
EP22725469.5A
Other languages
German (de)
English (en)
Other versions
EP4330552A1 (fr
Inventor
Rainer OBERHAUSEN
Michael Federmann
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.)
Compair Drucklufttechnik Zweigniederlassung der Gardner Denver Deutschland GmbH
Original Assignee
Compair Drucklufttechnik Zweigniederlassung der Gardner Denver Deutschland GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Compair Drucklufttechnik Zweigniederlassung der Gardner Denver Deutschland GmbH filed Critical Compair Drucklufttechnik Zweigniederlassung der Gardner Denver Deutschland GmbH
Priority to EP25220627.1A priority Critical patent/EP4682383A3/fr
Publication of EP4330552A1 publication Critical patent/EP4330552A1/fr
Application granted granted Critical
Publication of EP4330552B1 publication Critical patent/EP4330552B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C18/14—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F04C18/16—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/001—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar working principle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/02—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids specially adapted for several pumps connected in series or in parallel
    • 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
    • F04C29/005—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
    • 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
    • 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
    • F04C2240/70—Use of multiplicity of similar components; Modular construction
    • 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
    • F04C23/02—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • 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
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/08—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by varying the rotational speed

Definitions

  • the present invention relates to improvements in the drive of a multi-stage screw compressor and in particular a two-stage screw compressor in which the main rotors of the stages are driven via a common drive shaft.
  • a 3-wheel gearbox is conventionally used, in which a drive wheel arranged on the drive shaft engages with the two drive pinions arranged on the respective screw shaft of the first and second compressor stages to drive the two compressor stages.
  • an intermediate pressure develops between the first and second stages, dependent on the final pressure, which essentially corresponds to the final pressure of the first stage.
  • This intermediate pressure arises because the first stage delivers a higher volume flow than the second stage can dissipate. Consequently, the speed of the second stage must be set to a defined ratio relative to the speed of the first stage to achieve optimal intermediate pressure.
  • the respective pressure ratios of the individual compressor stages determine the distribution of the total output within the two-stage compressor.
  • a compressor generates pressure by enclosing a certain volume of air and continuously reducing the volume of that enclosed air until a defined pressure is reached.
  • the volume ratio that is, the initial volume of the enclosed gas (when the compressor's pressure chamber is closing) to the final volume at the point of defined pressure (when the pressure chamber opens again)—is determined during the compressor's design and remains constant. Maximum efficiency is achieved when the compressor's pressure chamber opens and the pressure in the adjacent pressure chamber is the same.
  • this pressure chamber is, in the first stage, the space between the two compressor stages with the intermediate pressure described above.
  • this pressure chamber is the one connected to the Compressor connected pressure vessels or the consumer network, which has the constant final pressure.
  • the intermediate pressure corresponds to the intake pressure of the second compressor stage, where the intake pressure is the pressure present when the pressure chamber of the respective compressor stage is closed. Consequently, if the intermediate pressure deviates from the optimal setting, the optimal intake pressure is not generated during the compression process in the second stage, resulting in over- or under-compression with respect to the final pressure and thus a significant loss of efficiency in the two-stage compressor.
  • the intermediate pressure must be adjusted to the respective final pressure by adjusting the speed of the two compressor stages in order to achieve maximum efficiency.
  • the rotors of the two compressor stages are installed in a common rotor housing, so the position of the driven main rotors is fixed and the gearbox consequently has a constant center distance.
  • the gear ratio between the first and second stages can only be changed to a very small extent by modifying the tooth geometry, for example by shifting the profile of the meshing gears.
  • JP 2020 037922 A This discloses a drive system for a multi-stage screw compressor with the features of the preamble of claim 1, as well as a corresponding screw compressor.
  • Helical toothed input and output pinions and their technical effects and advantages are also known, but not disclosed in the prior art in an obvious manner with the other features of claim 1.
  • the present invention aims to avoid the aforementioned problem and to enable changes in the overall power, final pressure, or volume flow rate of a multi-stage, and in particular two-stage, compressor, especially in the case of a fixed and unchangeable distance between the main rotor axes and the drive shaft, without significant efficiency losses. Furthermore, the present invention offers numerous other advantages, which will be discussed in detail below.
  • the drive system includes a drive shaft for driving the shafts of both main rotors of the first and second compressor stages.
  • the drive of the shaft of the first main rotor is independent of the drive of the shaft of the second main rotor.
  • the drive of the shaft of the first main rotor is independent of the drive of the shaft of the second.
  • the speeds of the main rotors can be adjusted independently of each other.
  • the ratio of the rotational speeds to each other is preferably freely selectable, whereas the speed ratio of the two rotors in a conventional 3-wheel gearbox is fixed by the design.
  • an independent drive of the two shafts of the main rotors is to be understood as meaning that the two shafts are driven by a common drive shaft, but, in contrast to the 3-wheel transmission of the prior art, not via the same drive wheel on the drive shaft.
  • the drive shaft has two drive wheels mounted on it that are fixed against rotation.
  • the first of these two drive wheels engages with a first output pinion that is fixed against rotation on the shaft of the first main rotor, while the second of the two drive wheels engages with a second output pinion that is fixed against rotation on the shaft of the second main rotor.
  • the 4-wheel gearbox according to the invention makes it very easy to adjust the intermediate pressure by freely selecting the gear ratios between the two compressor stages, and it also allows for coverage of ranges that are not achievable with a simple change in the tooth geometry of a 3-wheel gearbox. This leads to significant advantages in compressor operation when the total power output changes, the final pressure varies, and the volumetric flow rates are altered, as thermodynamically induced power losses due to over- or under-compression can be avoided.
  • the intermediate pressure is no longer essentially determined by the predetermined center distance as described above for the 3-wheel transmission, the arrangement of the individual compressor stages can be freely selected.
  • the 4-wheel drive according to the invention allows for the free arrangement of all compressor stages, it also offers the possibility, unlike 3-wheel drives, of freely designing the inlets and outlets, as well as the spaces within the compressor housing. This enables the implementation of a fluid-mechanically optimal arrangement by reducing deflections and adapting the arrangement of the internal flow channels and the inlets and outlets. Consequently, in addition to the increased compactness, this results in a further significant efficiency gain.
  • the invention allows for the simple adjustment of the best possible intermediate pressure by freely choosing the translation ratios between The two compressor stages also allow for the optimization of an oil-flooded compressor operated at constant speed, since in this case the injection temperature of the oil, which also has a strong influence on the intermediate pressure and efficiency, can be chosen thermodynamically favorably just above the point of condensation.
  • a preferred embodiment of the present invention relates to an oil-injected compressor in which the drive system according to the invention is used.
  • the 4-wheel gear arrangement according to the invention also has advantageous effects on the design and service life of the bearings used in the system for the rotor shafts, as will be shown below.
  • a screw compressor typically comprises one or more pairs of main and secondary rotors that mesh together in a helical shape.
  • the screws of the two rotors each have different pitches and numbers of teeth, so that during rotation, a chamber forms between each tooth gap of the rotors. This chamber continuously shrinks, thus generating the desired pressure. Consequently, different pressures arise at different axial points of the screw pair.
  • This pressure gradient generates axial and radial forces on the rotors, which are absorbed by the bearings of the two rotors.
  • the forces caused and generated by the rotor geometry depend on the intermediate and final pressure, but not on the compressor's power output.
  • the resulting radial force is absorbed by the radial bearings, and the axial force by the axial bearings. Due to the different geometries of the main and secondary rotors, the contributions of the resulting forces differ in the radial and axial directions. The greatest axial force typically occurs in the main rotor.
  • the intermediate pressure which represents the discharge pressure of the first stage as well as the intake pressure of the second stage, also influences the bearing forces of the individual compressor stages. If the intermediate pressure is too high, the bearings of the first stage are subjected to greater stress; if it is too low, the bearings of the second stage are subjected to greater stress.
  • the intermediate pressure in conventional three-wheel drives cannot be kept constant when the total power output changes, when different discharge pressures are used, when volume flows are altered, and also when different injection temperatures occur in the case of an oil-flooded compressor.
  • the two drive wheels on the drive shaft can be positioned in contact with each other, which can lead to increased stability of the drive wheels against axially acting forces.
  • the transmission between the second drive wheel and the second output pinion can have a different or the same gear ratio as the transmission between the first drive wheel and the first output pinion, in order to ensure the higher speed of the second compressor stage that is usually necessary in operation.
  • the toothing between at least one of the drive gears and the corresponding output pinion can be inclined relative to the axial extent of the drive shaft.
  • the toothing between both drive gears and their respective output pinions is inclined relative to the axial extent of the drive shaft, with the angles formed by the toothing of each drive gear with the output pinion relative to the axial extent of the drive shaft being different.
  • the angles formed by the toothing of each drive gear with the output pinion relative to the axial extent of the drive shaft have opposite signs.
  • Helical gearing of the drive wheels and the respective output pinions can be advantageously used to control axial forces acting on the rotors and their shafts during operation, as described in detail below.
  • helical gearing on the drive gear and the driven pinion results in additional forces within the system.
  • the helical gearing generates axial forces, dependent on the helix angle, which act on the drive shaft and the driven rotor.
  • the forces generated by the gears depend on the compressor's power output and the selected gear ratio.
  • the forces resulting from the helical gearing can either load or relieve the axial rotor bearing of the driven main rotor. This may allow for the use of smaller axial bearings on the rotors, or conversely, the application of a defined force to the axial rotor bearing.
  • the gear forces acting on the rotor bearings can also be controlled or reduced by appropriately selected and matched helical gearing of the individual drive gears. If a high axial force is generated at the driven rotor of a screw compressor due to the geometry of the rotors and the resulting pressure differential, the axial force generated by the pressure differential can be counteracted or increased individually at each compressor stage using the 4-gear transmission according to the invention and corresponding helical gearing between the respective drive gear and associated output pinion.
  • This adjustment of bearing forces has the advantage that smaller bearings can be used, resulting in cost savings, and a longer bearing lifespan can be achieved.
  • the drive system described in detail above is used in a two-stage compressor, wherein in a preferred embodiment it is an oil-injected compressor in which the advantages of the invention described in detail above can be used to a particularly beneficial effect.
  • Figure 1 shows a perspective view of a compressor 1 with a compressor housing 2 in which an embodiment of the drive system according to the invention is housed.
  • the compressor shown in the figures is an oil-injected compressor, but the drive system according to the invention, as described above, can also be used in compressors that do not have oil injection.
  • the compressor has an inlet 3 and an outlet 4 through which the medium to be compressed is supplied and discharged, as indicated by the arrows.
  • the drive shaft 5, which protrudes from the housing 2, is driven rotationally in the direction indicated by arrow R by means of a motor (not shown).
  • the in Figure 1 The compressor 1 shown is in Figure 2 shown again in a frontal view.
  • the compressor shown (1) is a two-stage compressor, and the two compressor stages 10 and 20 are located in the Figures 3-5 depicted.
  • the first compressor stage 10 comprises a main rotor 11 and a secondary rotor 14, which rotate to compress the medium led into the housing 2 via the inlet 3. interlock.
  • the two rotors 11 and 14 are mounted on their respective shafts 12 and 15 in a rotationally fixed manner.
  • the second compressor stage 20 also comprises a main rotor 21 and a secondary rotor 24, which rotate and interlock to further compress the medium delivered by the first compressor stage 10.
  • the two rotors 21 and 24 of the second compressor stage 20 are also mounted to their respective shafts 22 and 25 in a rotationally fixed manner.
  • the drive shaft 5 has a first drive wheel 51 and a second drive wheel 52 for independently driving the two compressor stages 10, 20, each of which is mounted on the drive shaft 5 in a rotationally fixed manner.
  • the first drive wheel 51 has teeth on its circumferential surface that engage with corresponding teeth on a first output pinion 13, which is mounted non-rotatably on the shaft 12 of the first main rotor 11.
  • rotation of the drive shaft 5 and the first drive wheel 51 results in a corresponding rotation of the shaft 12 of the first main rotor 11.
  • the first auxiliary rotor 14 is driven by the first main rotor 11 via the helical gearing with a transmission ratio determined by the respective number of teeth on the two rotors.
  • the rotational speed of the first main rotor 11 is determined by the transmission ratio between the first drive wheel 51 and the first output pinion 13.
  • the first main rotor and the first secondary rotor can also be rotaryally connected to each other via a further gearbox that is sufficiently known to those skilled in the art, so that the two rotors rotate synchronously in an interlocking manner during operation.
  • the toothing 16 between the first drive gear 51 and the first output pinion 13 is inclined with respect to the axis 5A of the shaft 5, as will be described later in connection with the Figures 6a and 6b will be described in more detail.
  • the second drive wheel 52 also has teeth on its circumferential surface, which, however, engage with corresponding teeth on a second output pinion 23 that is rotationally fixed on the shaft 22 of the second main rotor 21, so that a rotation of the drive shaft 5 and the second drive wheel 52 results in a corresponding rotation of the shaft 22 of the first main rotor 21.
  • the second auxiliary rotor 24 is driven by the second main rotor 21 via the helical teeth with a gear ratio that is
  • the rotational speed of the second main rotor 21 is determined by the gear ratio between the second drive gear 52 and the second output pinion 23 and can be adjusted independently of the rotational speed of the first main rotor 11 by appropriately adjusting the radial size of the two elements.
  • the second main rotor and the second auxiliary rotor can be rotaryally connected to each other via a further gearbox that is sufficiently known to those skilled in the art, so that the two rotors rotate synchronously and interlock during operation.
  • the toothing 26 between the second drive gear 52 and the second output pinion 23 is also inclined with respect to the axis 5A of the shaft 5, as will be described later in connection with the Figures 6a and 6b will be described in more detail.
  • the teeth arranged and engaged on the circumferential sides of the drive wheels 51 and 52 and the output pinions 13 and 23 are arranged at an angle with respect to the axis 5A of the drive shaft.
  • the teeth arranged on the first drive wheel 51 form an angle ⁇ with the axis 5A
  • the teeth arranged on the second drive wheel 52 form an angle ⁇ with the axis 5A, as shown in Figure 6a is shown schematically.
  • angles ⁇ and ⁇ with respect to axis 5A have the same sign, so that the resulting axial forces on the drive shaft 5 are in the same direction.
  • Figure 7f shows an example of a three-stage compressor which uses a drive system according to the invention, in which an additional third drive wheel 53 is mounted non-rotatably on the drive shaft 5 and engages in a third output pinion 33 which is mounted non-rotatably on the shaft 32 of a main rotor of the third compressor stage, in order to realize a drive of a third compressor stage which is conditioned via the common drive shaft 5 but is independent of the drive of the first two compressor stages.

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

Claims (6)

  1. Système d'entraînement pour un compresseur à vis à plusieurs étages (1) comprenant un premier étage de compression (10) avec un premier rotor principal (11) monté solidairement en rotation sur un premier arbre (12),
    un second étage de compression (20) avec un second rotor principal (21) monté solidairement en rotation sur un second arbre (22),
    sachant que le système d'entraînement présente un arbre d'entraînement (5) pour entraîner les arbres (12, 22) des deux rotors principaux (11, 21) des premier et second étages de compression (10, 20),
    sachant que l'entraînement de l'arbre (12) du premier rotor principal (11) s'effectue indépendamment de l'entraînement de l'arbre (22) du second rotor principal (21) ; sachant que un entraînement indépendant des deux arbres des rotors principaux doit être compris de sorte que l'arbre d'entraînement (5) présente deux roues d'entraînement (51, 52) disposées solidairement en rotation sur l'arbre d'entraînement, dont une première roue d'entraînement (51) s'engrène avec un premier pignon de sortie (13) disposé solidairement en rotation sur l'arbre (12) du premier rotor principal (11) et dont une seconde roue d'entraînement (52) s'engrène avec un second pignon de sortie (23) disposé solidairement en rotation sur l'arbre (22) du second rotor principal (21) ;
    sachant que la transmission entre la seconde roue d'entraînement (52) et le second pignon de sortie (23) présente un rapport de transmission différent de celui de la transmission entre la première roue d'entraînement (51) et le premier pignon de sortie (13) ;
    caractérisé en ce que
    la denture (16, 26) entre les deux roues d'entraînement (51, 52) et les pignons de sortie (13, 23) respectifs est oblique par rapport à l'extension axiale (5A) de l'arbre d'entraînement (5) et sachant que les angles (α, β) formés par la denture (16, 26) de la roue d'entraînement (51, 52) respective avec le pignon de sortie (13, 23) par rapport à l'extension axiale (5A) de l'arbre d'entraînement (5) sont différents ; et
    sachant que les angles (α, β) formés par la denture (16, 26) de la roue d'entraînement (51, 52) respective avec le pignon de sortie (13, 23) par rapport à l'extension axiale (5A) de l'arbre d'entraînement (5) présentent des signes différents.
  2. Système d'entraînement selon la revendication 1,
    sachant que, grâce à l'entraînement de l'arbre (12) du premier rotor principal (11) indépendamment de l'entraînement de l'arbre (22) du second rotor principal (21), les vitesses de rotation des deux rotors principaux (11, 21) peuvent être adaptées indépendamment l'une de l'autre.
  3. Système d'entraînement selon la revendication 2,
    sachant que, grâce à l'entraînement de l'arbre (12) du premier rotor principal (11) indépendamment de l'entraînement de l'arbre (22) du second rotor principal (21), le rapport entre les vitesses de rotation des deux rotors principaux (11, 21) peut être choisi librement l'une par rapport à l'autre.
  4. Compresseur à vis (1) avec un système d'entraînement selon l'une des revendications 1 à 3.
  5. Compresseur à vis (1) selon la revendication 4,
    sachant que le compresseur à vis (1) présente précisément deux étages de compression (10, 20).
  6. Compresseur à vis (1) selon la revendication 4 ou la revendication 5,
    sachant que le compresseur à vis (1) est un compresseur à injection d'huile.
EP22725469.5A 2021-04-30 2022-04-26 Système d'entraînement pour un compresseur à vis à plusieurs étapes Active EP4330552B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP25220627.1A EP4682383A3 (fr) 2021-04-30 2022-04-26 Système d'entraînement pour compresseur à vis à plusieurs étages

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102021111297.4A DE102021111297A1 (de) 2021-04-30 2021-04-30 Antriebssystem für einen mehrstufiger Schraubenverdichter
PCT/EP2022/060967 WO2022229133A1 (fr) 2021-04-30 2022-04-26 Système d'entraînement pour compresseur à vis à plusieurs étages

Related Child Applications (2)

Application Number Title Priority Date Filing Date
EP25220627.1A Division EP4682383A3 (fr) 2021-04-30 2022-04-26 Système d'entraînement pour compresseur à vis à plusieurs étages
EP25220627.1A Division-Into EP4682383A3 (fr) 2021-04-30 2022-04-26 Système d'entraînement pour compresseur à vis à plusieurs étages

Publications (2)

Publication Number Publication Date
EP4330552A1 EP4330552A1 (fr) 2024-03-06
EP4330552B1 true EP4330552B1 (fr) 2026-01-28

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EP25220627.1A Pending EP4682383A3 (fr) 2021-04-30 2022-04-26 Système d'entraînement pour compresseur à vis à plusieurs étages
EP22725469.5A Active EP4330552B1 (fr) 2021-04-30 2022-04-26 Système d'entraînement pour un compresseur à vis à plusieurs étapes

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Country Status (4)

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US (2) US12435721B2 (fr)
EP (2) EP4682383A3 (fr)
DE (1) DE102021111297A1 (fr)
WO (1) WO2022229133A1 (fr)

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USD1102484S1 (en) * 2023-09-27 2025-11-18 Fujian Snowman Compressor Co., Ltd Centrifugal compressor
CN120120246B (zh) * 2025-04-22 2025-09-23 山东众海机械有限公司 一种节能型多级螺杆空气压缩机

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2020037922A (ja) * 2018-09-05 2020-03-12 株式会社宇野澤組鐵工所 多段ルーツ式ポンプ

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US20260104046A1 (en) 2026-04-16
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US12435721B2 (en) 2025-10-07
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