EP3737863A1 - Compresseur - Google Patents

Compresseur

Info

Publication number
EP3737863A1
EP3737863A1 EP19700332.0A EP19700332A EP3737863A1 EP 3737863 A1 EP3737863 A1 EP 3737863A1 EP 19700332 A EP19700332 A EP 19700332A EP 3737863 A1 EP3737863 A1 EP 3737863A1
Authority
EP
European Patent Office
Prior art keywords
dry
compressor according
compressing
rotor
pressure
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.)
Withdrawn
Application number
EP19700332.0A
Other languages
German (de)
English (en)
Inventor
Thomas Dreifert
Kai NADLER
Bernhard Kliem
Roland Müller
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.)
Leybold GmbH
Original Assignee
Leybold 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 Leybold GmbH filed Critical Leybold GmbH
Publication of EP3737863A1 publication Critical patent/EP3737863A1/fr
Withdrawn legal-status Critical Current

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
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/04—Heating; Cooling; Heat insulation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2220/00—Application
    • F04C2220/10—Vacuum
    • F04C2220/12—Dry running
    • 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
    • F04C2240/50—Bearings
    • F04C2240/51—Bearings for cantilever assemblies
    • 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
    • F04C25/00—Adaptations of pumps for special use of pumps for elastic fluids
    • F04C25/02—Adaptations of pumps for special use of pumps for elastic fluids for producing high vacuum
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2210/00—Working fluid
    • F05B2210/10—Kind or type
    • F05B2210/14—Refrigerants with particular properties, e.g. HFC-134a

Definitions

  • the invention relates to a compressor, in particular a screw compressor.
  • screw compressors For the compression of gases, in particular for the supply of compressed air, today primarily oil-injected screw compressors are used. With these, a compression of lbar (absolute) to 8.5 bar to 14 bar (absolute) can usually be carried out in a compressor stage.
  • the subsidized intake volume flows are in the range of 30 to 5000 m 3 / h.
  • Such screw compressors have two counter-rotating screw rotors.
  • the screw rotors each have at least one screw-line-shaped depression, so that a displacement element is formed.
  • the injection of oil into the pump chamber, in which the two screw rotors are arranged, serves to seal the gap between the rotors and the housing or the inner wall of the pump chamber.
  • dry-compressing screw compressors To produce oil-free compressed air, it is known to use dry-compressing screw compressors.
  • the two screw rotors are arranged without contact and synchronized with each other via an oil-lubricated gearbox.
  • dry compressing screw compressors have the disadvantage that with a compressor stage only a compression to 4 to 5 bar (absolute) is possible. This is due in particular to the fact that high gaps occur through the gaps between the rotors and the housing.
  • pressures of 9 bar (absolute) two-stage screw compressors must be used.
  • an intermediate cooling of the compressed air is also necessary, resulting in complex systems with many components and a large installation space.
  • spindle compressors are known. These have a plurality of closed working chambers connected in series over a plurality of turns or wraps of a displacer. Theoretically, high compression pressures should also be achieved in one stage can be replaced so that spindle compressors multi-stage screw compressors or rotary tooth compressors could be replaced. However, spindle compressors have not been on the market so far, so that practical proof that high compression pressures can be achieved in one stage has not yet taken place. Spindle compressors are described, for example, in DE 10 2010 064 388, WO 2011/101064, DE 10 2012 202 712 and DE 10 2011 004 960.
  • the object of the invention is to provide a dry compressing compressor, with the one-stage high pressures of more than 5bar (absolute) can be achieved in particular.
  • the dry compressing compressor according to the invention has a suction chamber formed by a housing.
  • Two intermeshing screw rotors are arranged in the pump chamber. These are rotated in opposite directions to convey the gas.
  • each screw rotor has at least one displacement element which has a helical recess for forming the turns.
  • only one displacement element can be provided per screw rotor, which may optionally be formed integrally with a rotor shaft.
  • the housing has a compressor inlet, to which preferably atmospheric pressure is applied. A pressure of more than 2 bar (absolute) is preferably applied to a compressor outlet, wherein it is particularly preferred for the compressor outlet to have a pressure of more than 5 bar (absolute).
  • the at least one displacement element per screw rotor is designed to be catchy and has an asymmetrical profile.
  • asymmetric profile designed such that no or at most a small blow hole is formed. Since there is no through-blowing hole, a short-circuit is only provided between two adjacent chambers in the case of an asymmetrical profile which is preferably designed according to the invention.
  • the so-called Quimby profile is provided as the asymmetrical profile.
  • Asymmetrical profiles have two different profile flanks. Although these are expensive to manufacture due to the required two separate steps, this can be achieved by a very dense working chamber.
  • the number of turns of the at least one displacement element or, in the case of a plurality of displacement elements, the sum of the turns of the displacement elements of a screw rotor is greater than the ratio of the pressure prevailing at the compressor outlet to the pressure prevailing at the compressor inlet. The number of turns n thus results
  • the built-in volume ratio of the dry compressing screw compressor between the theoretical delivery volume at the inlet stage (Vein) and the theoretical delivery volume at the outlet stage (V out ) to the pressure ratios at the inlet (Pein) and at the outlet (P out ) is adjusted.
  • n has a value of k-0.3 to k + 0.3 and preferably a value between k-0.1 and k + 0.1 k is the isotropic exponent of the gas mixture to be delivered.
  • the displacement elements have at least one region or section in which the chamber volume decreases from a volume Vein to an intermediate volume VVK.
  • the reduction of the delivery volume of the stages (working chambers) from the large inlet volume (Vein) to the smaller outlet volume (V out ) is divided into two areas.
  • the working chamber closed off towards the suction side is reduced within a small rotation angle range to a specific volume (volume of the pre-compression VVK). It is preferred that
  • the precompression raises the temperature of the gas by the compression work to a moderate value of 150 ° C - 200 ° C.
  • the working chamber volume decreases considerably less strongly as a function of the angle of rotation than in the first region. The angle of rotation and thus the number of stages is considerably higher in the second range than in the first range.
  • the compression of the gas taking place here is selected such that the resulting heat of compaction can be well dissipated via the side walls of the housing so that the temperature of the gas does not increase or increases only slightly.
  • the maximum temperature change is preferably less than 50 ° C., and more preferably less than 30 ° C.
  • a particular advantage of the selected distribution of the volume reduction is that a largely homogeneous temperature distribution is achieved in the component. As a result, thermal peak loads and the associated strong component strains can be prevented.
  • the precompression takes place in the described first range within 1.5 to 3 rotor revolutions (turns).
  • the inventively high number of turns in the second region can be achieved here in a preferred embodiment by a single displacement element per rotor. However, it is also possible to provide a corresponding number of turns in this pressure-side region, for example by two displacement elements.
  • a high number of windings in accordance with the invention in this region in which, according to the invention, preferably only a relatively small compression of the medium to be conveyed takes place per turn, it is possible to dispense with rotor internal cooling. This is due in particular to the fact that, due to the relatively low compression in this area, the temperature increase of the displacement element caused by the compression is lower. Furthermore, due to the high density of the pumped medium through the medium itself, good heat dissipation from the displacement element into the compressor housing takes place in this area.
  • the screw rotors and the at least one provided displacement element are designed such that at least 6, in particular at least 8 and particularly preferably at least 10 windings are provided between an area in which 5% -20% of the outlet pressure prevails and the pressure-side rotor end are.
  • the pressure-side rotor end is in this case the area of the compressor outlet.
  • the inventively high number of turns in this area can be provided here in a preferred embodiment in the case of a single pressure-side displacement element provided for each rotor. However, it is also possible to provide a corresponding number of turns in this pressure-side region, for example on two displacement elements.
  • the preferably at least 6, in particular at least 8 and particularly preferably at least 10 turns are provided in a pressure-side displacement element.
  • the pressure-side displacement element has an average working pressure of more than 2 bar (absolute) on at least 6, in particular at least 8 and particularly preferably at least 10 turns.
  • the aim is in particular a shallow pressure gradient within the compressor. Therefore, the pressure should rise slowly over many turns of, in particular, 6 to 10 turns.
  • a cold gap with a Height of 0.03 mm - 0.2 mm and in particular 0.05 mm - 0.1 mm.
  • Such a relatively large gap height can be due to the inventive, described above Embodiment of the particular 6, preferably 8 and more preferably 10 last turns are provided.
  • a comparison with the diameter relatively long screw rotor is selected.
  • the at least one displacement element per screw rotor or in the case of a plurality of displacement elements per screw rotor together have a ratio of length L to diameter D, for which the following applies: and particularly
  • the usable area for heat dissipation is increased. Due to the resulting good heat exchange, the gas temperatures of the compressed gas are relatively low.
  • the provision of many chambers also has the advantage that the pressure differences between adjacent chambers are small and thereby a high density can be achieved.
  • the compression process becomes thermodynamically particularly effective and the gas temperatures remain relatively low. It is particularly preferred here for the internal volume ratio to be adapted to the ratio of outlet pressure to inlet pressure such that neither over-compression nor compression due to re-aeration occurs.
  • the inner volume ratio can be achieved by varying the pitch of the turns.
  • a change in the pitch of the turns in particular such that these from the compressor inlet to Compressor outlet decreases or becomes steeper.
  • the change in slope can be continuous and / or in stages.
  • a change in the head and foot diameters of the profile can also take place in steps or continuously. Again, a continuous change of the head and foot diameter is preferred, so that the rotor is conical, in particular in combination with a continuous change in the pitch.
  • the pressure ratio between the outlet pressure and the inlet pressure is at least 5.
  • the outlet pressure is at least 2 bar (absolute), in particular at least 5 bar.
  • the dry-compressing compressor at the compressor inlet and / or at the compressor outlet in each case preferably within the compressor housing to a gas collecting space.
  • the dry compressing screw compressor is a two-shaft compressor. These are preferably mounted on both sides, so that narrow gaps can be realized both between the displacement elements and between the displacement elements and the inner wall of the suction chamber.
  • a synchronization of the two rotor shafts by a preferably arranged outside of the pump chamber synchronization gear.
  • the bearing lubrication can be done with grease and / or oil.
  • the gearbox lubrication can take place via grease and / or oil. This is possible insofar as both the bearings and the synchronization gear are preferably arranged outside the pump chamber and thus is further avoided that the gas to be delivered is contaminated with oil.
  • the housing is made of aluminum or an aluminum alloy.
  • the coefficient of thermal expansion (coefficient of expansion) of the material of the screw rotors is less than the expansion coefficient of the material of the housing. It is particularly preferred that the coefficient of expansion of the screw rotors is smaller than 12 * 10 6 1 / K. This can be achieved by rotors made of iron or steel materials.
  • the two screw rotors arranged in the pump chamber have at least one displacement element which has a helical recess.
  • the helical recesses form several turns.
  • the at least one displacement element is made of a steel or an iron alloy. It is thus particularly preferred that the screw rotors, including the displacement elements, are made of a steel or iron alloy.
  • the housing is likewise produced from a steel or iron alloy or from aluminum or an aluminum alloy.
  • Each displacement element preferably has at least one helical recess which has the same contour over its entire length.
  • the contours are preferably different for each displacement element.
  • the single displacement element thus preferably has a constant pitch and a constant contour. This simplifies the production considerably, so that the production costs can be greatly reduced.
  • the contour of the suction-side displacement element is preferably asymmetrical.
  • the flanks can be designed such that the leakage surfaces, the so-called blow-off more preferably completely disappear or at least have a small cross-section.
  • a particularly suitable asymmetric profile is the so-called "Quimby-ProfM". Although such a profile is relatively difficult to produce, it has the advantage that there is no continuous blow hole. A short circuit exists only between two adjacent chambers. Since this is an asymmetrical profile with different profile flanks, at least two working steps are required for the production because the two flanks must be produced in different work steps due to their asymmetry.
  • the pressure-side displacement element in particular the last displacement element in the pumping direction, is preferably provided with a symmetrical contour.
  • the symmetrical contour has the particular advantage that the production is easier.
  • both flanks with a symmetrical contour can be produced by a rotating end mill or by a rotating side milling cutter in one work step.
  • Such symmetrical profiles have blow holes, they are continuous, ie not only provided between two adjacent chambers. The size of the blow hole decreases as the slope decreases.
  • such symmetrical profiles can be provided in particular in the case of the pressure-side displacement element, since in a preferred embodiment it has a smaller pitch than the suction-side displacement element and preferably also as the displacement elements arranged between the suction-side and the pressure-side displacement element.
  • a particularly suitable symmetrical profile is the so-called "cycloid profile".
  • the provision of at least two such displacement elements means that the corresponding screw compressor can generate high outlet pressures at low power consumption.
  • the thermal load is also low.
  • Arranging at least two displacement elements having a constant pitch and a constant contour in a compressor designed according to the invention leads to substantially the same results as in a compressor having a displacement element with a changing pitch. At high built volume ratios can be provided per rotor three or four displacement elements.
  • a pressure-side displacement element that is, in particular in the pumping direction last displacement element, has a large number of windings. Due to the high number of turns, a larger gap between the screw rotor and the housing can be accepted with consistent performance.
  • the gap can have a cold gap width of 0.05-0.3 mm.
  • a large number of outlet turns or number of turns in the pressure-side displacement element is inexpensive to produce, since according to the invention this displacement element can have a constant pitch and preferably also a symmetrical contour. On the outlet side, an asymmetric profile can also be used.
  • This pressure-side or last displacement element preferably has more than 6, in particular more than 8, and particularly preferably more than 10 turns.
  • the use of symmetrical profiles in a particularly preferred embodiment has the advantage that both flanks of the profile can be cut simultaneously with a milling cutter. In this case, the milling cutter is additionally supported by the respectively opposite flank, so that deformation or bending of the milling cutter during the milling process and thus caused inaccuracies are avoided.
  • the pitch change between adjacent displacement elements is discontinuous or erratic.
  • the two displacement elements are arranged in the longitudinal direction at a distance from each other, so that between two displacement elements a circumferential cylindrical chamber is formed, which serves as a tool outlet. This is particularly advantageous for the production of integrally formed rotors, since the helix producing tool can be brought out in this area in a simple manner. If the displacement elements are produced independently of each other and then mounted on a shaft, it is not necessary to provide a tool outlet, in particular such a ring-cylindrical area.
  • no tool outlet is provided between two adjacent displacement elements on the change of pitch.
  • both flanks have a defect or recess in order to be able to lead out the tool.
  • Such a defect has no appreciable influence on the compression capacity of the compressor, since it is a locally highly limited defect or recess.
  • the compressor screw rotor according to the invention has in particular a plurality of displacement elements. These can each have the same or different diameters. In this case, it is preferred that the pressure-side displacement element has a smaller diameter than the suction-side displacement element.
  • displacement elements which are produced independently of the rotor shaft, they are mounted on the shaft, for example by press fits. In this case, it is preferable to provide elements such as dowel pins for fixing the angular position of the displacement elements to one another.
  • the screw rotor is made in one piece, in particular one made of steel or an iron alloy.
  • the screw rotor can also have a rotor shaft that carries the at least one displacement element. This has the advantage, in particular when providing a plurality of displacement elements, that they can be produced independently of one another and are then connected to the rotor shaft in particular by being pressed on or shrink-fitted. In this case, it is possible to provide feathering keys or the like for defining the angular position of the individual displacement elements.
  • the screw rotors have no rotor inner cooling.
  • the screw rotors do not have any channels through which liquid coolant flows in particular.
  • the screw rotors can have bores or channels, for example for weight reduction, for balancing or the like. It is preferred in particular that the screw rotors are solid.
  • the housing has an average heat flow density in the region of the displacement elements which is less than 80,000 W / m 2 , preferably less than 60,000 W / m 2 and in particular less than 40,000 W / m 2 .
  • the mean heat flux density is the ratio of compaction power to the wall area of the compression area.
  • a gas aftercooler and / or a condensate separator for separating off the condensate and / or a silencer resulting from the compression may optionally additionally be provided on the compressor outlet. It is also possible to provide an intake air filter or an intake silencer at the compressor inlet.
  • a delivery level of at least 70 percent, preferably at least 85 percent, can be achieved for at least one operating point of the compressor.
  • the decisive factor is the ratio of theoretically possible and practically achieved volume flow.
  • the achievable by the compressor according to the invention high degree of delivery is a measure of the good tightness of the compressor.
  • the compressor according to the invention preferably has a high isothermal grade of at least 45 percent, preferably at least 60 percent.
  • the isothermal grade is the ratio of ideal isothermal compaction performance and real compaction performance.
  • the isothermal grade in turn represents a measure of good tightness and good cooling of the compressor.
  • the dry-compressing compressor according to the invention is preferable for the dry-compressing compressor according to the invention to be operated with a medium-speed motor.
  • the speed is more than 3000 "*> and particularly preferred
  • the speed is preferably lower than
  • an intensive cooling of the housing to keep the gas and components cold. If appropriate, this can also be done without rotor internal cooling in the embodiment of the compressor according to the invention. Low gas temperatures cause a reduction in compression work and thus have a positive effect on the power consumption of the compressor.
  • the rotors or the displacement elements can be coated with inlet layers, for example based on PTFE or molybdenum sulfide, in order to reduce the gap heights without impairing operational safety.
  • 1 is a schematic plan view of a preferred embodiment of a screw rotor of the screw compressor according to the invention
  • 2 is a schematic sectional view of displacement elements with asymmetric profile
  • Fig. 3 is a schematic sectional view of displacement elements with symmetrical profile
  • Fig. 4 is a schematic sectional view of a screw compressor.
  • the screw rotors shown in FIGS. 1 to 3 can be used in a screw compressor according to the invention, as shown in FIG. 4.
  • the rotor has a compression direction, i. H. in Figure 1 from left to right, changing or variable slope.
  • a first suction-side region 10 which forms a first displacement element
  • a large pitch of approximately 50-150 mm / revolution is provided in a first suction-side region 10, which forms a first displacement element.
  • the slope changes in the range 10, d. H. in the precompression range, at 55-65% of the inlet slope, i. approx. 30 - 100 mm / revolution.
  • the pitch is significantly lower. In this range, the slope is in the range of 10 - 30 mm / revolution.
  • the at least one displacement element per screw rotor thus formed by a screw rotor with variable preferably continuously changing pitch. This corresponds to a multiplicity of displacement elements arranged one behind the other in the conveying direction.
  • a gas collection chamber 14 is provided in the illustrated preferred embodiment.
  • the integrally formed screw rotor has two bearing seats 16 and a shaft end 18. With the shaft end 18, for example, a gear is connected to the drive.
  • the continuous shaft 20 may also be made of another material different from the displacement elements 10, 12.
  • conical rotors can also be provided. These in turn have according to the invention a plurality of displacement elements. Again, it is particularly preferred that the plurality of displacement elements are realized by a variable pitch. Conical rotors are also designed to be catchy.
  • Fig. 2 is a schematic sectional view of an asymmetric profile (e.g., a Quimby profile).
  • the illustrated asymmetrical profile is a so-called "Quimby profile”.
  • the sectional view shows two screw rotors which mesh with each other and whose longitudinal direction is perpendicular to the plane of the drawing. The opposite rotation of the rotors is indicated by the two arrows 15. Relative to a plane 17 running perpendicular to the longitudinal axis of the displacement elements are the profiles of the flanks
  • Such an asymmetric profile is preferably provided in the suction-side displacement element 10.
  • the schematic sectional view in Fig. 3 again shows a cross section of two displacement elements or two screw rotors, which in turn rotate in opposite directions (arrows 15). Relative to the axis of symmetry 17, the flanks 23 are designed to be symmetrical per displacement element.
  • the preferred exemplary embodiment shown in FIG. 4, a symmetrically designed contour, is a cycloid profile.
  • a symmetrical profile, as shown in FIG. 3, is preferably provided in the pressure-side displacement elements 12.
  • displacement elements are provided. These may possibly also have different head diameters and corresponding foot diameters. In this case, it is preferred that a displacement element with a larger head diameter at the inlet, i. is arranged on the suction side in order to realize a greater pumping speed in this area and / or to increase the built-in volume ratio. Furthermore, combinations of the embodiments described above are possible. For example, one or more displacement elements may be made integral with the shaft or an additional displacement element independent of the shaft and then mounted on the shaft.
  • the compressor housing 26 has an inlet 28 through which gas is sucked in the direction of an arrow 30. Furthermore, the compressor housing 26 has a pressure-side outlet 32, through which the gas is ejected in the direction of an arrow 38.
  • the screw compressor according to the invention compresses air into a compressed air space. Between the surfaces 42 of the two displacement elements 12 and an inner surface 44 of a pump chamber 26 formed by the compressor housing 26, a gap is formed whose height preferably in the range of 0.03 mm - 0.2 mm and in particular in the range of 0.05 mm - 0.1 mm.
  • the gap between the flanks of the displacement elements preferably has a gap height of 0.1-0.3 mm.
  • the compressor housing 26 is closed in the illustrated embodiment with two housing covers 47.
  • the left in Fig. 4 housing cover 47 has two bearing receptacles, in each of which a ball bearing 48 is arranged for mounting the two rotor shafts.
  • a ball bearing 48 is arranged for mounting the two rotor shafts.
  • the pins 50 of the two screw rotor shafts protrude through the covers 47.
  • a gear wheel 52 is arranged on each of the two shaft journals 50.
  • the two toothed wheels 52 mesh with one another in order to synchronize the two screw rotors with each other.
  • two bearings 48 for supporting the screw rotors are also arranged in the right-hand cover 47 in FIG.
  • a seal is provided in addition to the bearings 48.
  • shaft is the drive shaft which is connected to a drive motor, not shown.

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

Abstract

L'invention concerne un compresseur à vis à compression à sec, qui comporte, dans un boîtier (26) formant un espace d'aspiration, deux rotors à vis. De préférence, une pression atmosphérique est appliquée sur une entrée (28) du compresseur, et de préférence une pression supérieure à 2 bar (absolue) est appliquée sur une sortie (32) du compresseur. Au moins un élément de refoulement (10, 12) comportant un évidement de forme hélicoïdale servant à former plusieurs spires est prévu par rotor à vis. L'élément ou les éléments de refoulement (10, 12) par rotor à vis comportent un profil asymétrique à un filet.
EP19700332.0A 2018-01-12 2019-01-04 Compresseur Withdrawn EP3737863A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE202018000178.3U DE202018000178U1 (de) 2018-01-12 2018-01-12 Kompressor
PCT/EP2019/050145 WO2019137852A1 (fr) 2018-01-12 2019-01-04 Compresseur

Publications (1)

Publication Number Publication Date
EP3737863A1 true EP3737863A1 (fr) 2020-11-18

Family

ID=65013675

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19700332.0A Withdrawn EP3737863A1 (fr) 2018-01-12 2019-01-04 Compresseur

Country Status (7)

Country Link
US (1) US20200362861A1 (fr)
EP (1) EP3737863A1 (fr)
JP (1) JP2021510404A (fr)
KR (1) KR20200105817A (fr)
CN (1) CN111448392B (fr)
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WO2019137852A1 (fr) 2019-07-18
KR20200105817A (ko) 2020-09-09
DE202018000178U1 (de) 2019-04-15
US20200362861A1 (en) 2020-11-19
CN111448392B (zh) 2022-07-26
JP2021510404A (ja) 2021-04-22
CN111448392A (zh) 2020-07-24

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