EP2732165B1 - Compresseur à vis - Google Patents

Compresseur à vis Download PDF

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Publication number
EP2732165B1
EP2732165B1 EP12728244.0A EP12728244A EP2732165B1 EP 2732165 B1 EP2732165 B1 EP 2732165B1 EP 12728244 A EP12728244 A EP 12728244A EP 2732165 B1 EP2732165 B1 EP 2732165B1
Authority
EP
European Patent Office
Prior art keywords
slider
screw
screw compressor
insertion space
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.)
Active
Application number
EP12728244.0A
Other languages
German (de)
English (en)
Other versions
EP2732165A1 (fr
Inventor
Dominic Kienzle
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.)
Bitzer Kuehlmaschinenbau GmbH and Co KG
Original Assignee
Bitzer Kuehlmaschinenbau GmbH and Co KG
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 Bitzer Kuehlmaschinenbau GmbH and Co KG filed Critical Bitzer Kuehlmaschinenbau GmbH and Co KG
Publication of EP2732165A1 publication Critical patent/EP2732165A1/fr
Application granted granted Critical
Publication of EP2732165B1 publication Critical patent/EP2732165B1/fr
Active legal-status Critical Current
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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
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/12—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C2/14—Rotary-piston machines or pumps 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
    • F04C2/16—Rotary-piston machines or pumps 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
    • 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
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C20/00—Control of, monitoring of, or safety arrangements for, machines or engines
    • F01C20/10—Control of, monitoring of, or safety arrangements for, machines or engines characterised by changing the positions of the inlet or outlet openings with respect to the working chamber
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C20/00—Control of, monitoring of, or safety arrangements for, machines or engines
    • F01C20/10—Control of, monitoring of, or safety arrangements for, machines or engines characterised by changing the positions of the inlet or outlet openings with respect to the working chamber
    • F01C20/12—Control of, monitoring of, or safety arrangements for, machines or engines characterised by changing the positions of the inlet or outlet openings with respect to the working chamber using sliding valves
    • 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
    • F04C28/10—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by changing the positions of the inlet or outlet openings with respect to the working chamber
    • F04C28/12—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by changing the positions of the inlet or outlet openings with respect to the working chamber using sliding valves
    • 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
    • F04C28/10—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by changing the positions of the inlet or outlet openings with respect to the working chamber
    • F04C28/12—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by changing the positions of the inlet or outlet openings with respect to the working chamber using sliding valves
    • F04C28/125—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by changing the positions of the inlet or outlet openings with respect to the working chamber using sliding valves with sliding valves controlled by the use of fluid other than the 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
    • F04C29/0007—Injection of a fluid in the working chamber for sealing, cooling and lubricating

Definitions

  • the invention relates to a screw compressor comprising a screw compressor housing with a screw rotor housing, with screw rotor bores arranged in the screw rotor housing, with screw rotors arranged in the screw rotor bores and rotatably mounted in the screw rotor housing about axes of rotation, with a drive for the screw rotors and with one in the screw rotor housing in a slide receptacle slidably guided and partially adjacent to the screw rotor with end faces slide for adjusting a volume ratio of the screw compressor, which extends from an entry space of the slide receptacle in an open towards the screw rotor bores guide recess of the slide receptacle in the direction of the high pressure outlet and in a first position and in a second position can be positioned, wherein in one of the positions, the volume ratio of the screw compressor grö He is in the other position.
  • Such screw compressors are for example from the GB 2 119 445 A or the WO 2004/051089 A1 known.
  • the invention is therefore an object of the invention to improve a screw compressor of the generic type such that it requires as little space for the operation of the slide with the best possible slide guide.
  • the slide is connected to an at least partially arranged in the Einfahrraum first cylinder element which cooperates with an at least partially arranged in the Einfahrraum second cylinder element, and that the cylinder elements on a side opposite the high pressure outlet side of the slide are arranged following in the direction of displacement on the slider.
  • the advantage of the solution according to the invention is the fact that with this the possibility exists to arrange the cylinder elements to save space in the screw compressor housing.
  • the entry-in space is designed to receive the first cylinder element both in the first position and in the second position.
  • the entry space is formed receiving the second cylinder element.
  • the second cylinder element may be a separate element arranged in the retraction space or an element formed by the retraction space itself.
  • an advantageous solution provides that the entry space is arranged without overlapping relative to the screw rotor bores, that is, that there is no spatial overlap between the entry space and the screw rotor bores, so that the entry space is formed separately from the screw rotor bores.
  • the entry space could be arranged at a distance from the guide trough.
  • the retraction space is arranged in a radial direction to the rotational axes of the screw rotors laterally adjacent to a low-pressure side bearing unit for the screw rotors.
  • the retraction could extend both in the screw rotor housing and reach into the motor housing.
  • a particularly simple and space-saving solution provides that the retraction space extends in the screw rotor housing and preferably does not extend into the motor housing.
  • the entry space has a cross-sectional contour which extends transversely to the direction of displacement and which is at least large enough for it to be able to receive the slide and the first cylinder element.
  • the slider and the first cylinder member can be moved together into the retraction space, so that the slider can be made compact with the first cylinder member.
  • the cross-sectional contour of the retraction is adapted to the cross-sectional contour of the first cylinder element, in which case the cross-sectional contour of the first cylinder member is greater than the cross-sectional contour of the slider, so that the slider can also easily enter the retraction space.
  • the retraction space has a wall surface area, which forms the slide in the entry space transverse to the direction leading slide guide surfaces. This makes it possible to reliably guide the slide both in the guide trough and in the entry area.
  • a particularly compact solution provides that the first cylinder element is firmly connected to the slide.
  • a particularly compact solution with regard to its construction provides that the entry area forms the second cylinder element.
  • the entry space is designed so that it in turn is located in a cylinder housing and receives a piston body.
  • first cylinder element and the second cylinder element include a cylinder volume, which is acted upon either with high-pressure compressed medium or medium present at low pressure, in particular for compression medium, so that a simple control option High pressure or low pressure is applied to the cylinder volume.
  • the low-pressure pockets can be kept in a variety of ways to low pressure.
  • a particularly favorable solution provides that the low-pressure pockets are held at low pressure via a discharge channel leading to the low-pressure inlet, which runs either through the slide or through the screw rotor housing.
  • Such a discharge channel is preferably a channel which extends transversely through the slide from the low-pressure pockets to a low-pressure side of the slide and opens into this with a mouth opening, so that low pressure can always be maintained in the low-pressure pockets via this discharge channel.
  • the mouth opening is arranged for example on a comb formed by the end surfaces of the slide.
  • the screw rotor housing for example, opening into one of the rotor bores injection port for lubricant provided with which in particular a compression chamber formed by the screw rotor, preferably a first forming compression chamber, lubricant is supplied, said supply of lubricant in particular independently the positions of the slide takes place.
  • the injected amount of lubricant can vary, for example, depending on the volume ratio and / or a pressure difference and / or the speed.
  • a further advantageous embodiment provides that the slide is provided with a lubricant inlet facing the screw rotors, so that can be supplied to the screw rotors via the slider, at least in the first position with a large volume ratio, lubricant.
  • the injection opening communicates with an injection channel provided in the slide, to which lubricant can be supplied from the side of the screw rotor housing via a feed opening.
  • the amount of lubricant that can be supplied via the slide is at least as great, preferably more than one and a half times as large, even better more than twice as large as the amount of lubricant supplied via the screw rotor housing in all positions of the slide.
  • the amount of lubricant supplied via the slide can also vary depending on the volume ratio and / or the pressure difference and / or the rotational speed.
  • the screw compressor according to the invention can be provided with a drive which operates at one or more defined predetermined speeds and drives the screw compressor.
  • variable-speed drive expediently takes place by means of an inverter.
  • An exemplary embodiment of a screw compressor designated as a whole by 10 has a screw compressor housing designated by 12, which comprises a motor housing 14, a screw rotor housing 16 and, for example, a high-pressure housing 18 ( Fig. 1 to 5 ).
  • a designated as a whole with 20 drive motor which comprises a stator 22 and a rotor 24, wherein by means of the rotor 24 via a drive shaft 26, for example by means of an inverter 28 variable speed controllable drive of one of two Screw rotors 32 and 34, which are arranged in screw rotor bores 36, 38 in the screw rotor housing 16 and stored in a low-pressure side bearing unit 37 and in a high-pressure side bearing unit 39 and mesh and thereby compress a supplied via a low pressure inlet 42 to be compressed medium, so that this from a High-pressure outlet 44 of the screw rotor housing 16 exits again and then enters from the high-pressure outlet 44 in the high-pressure housing 18, in which, for example Schmierstoffabscheidevorraum 40 is arranged, through which lubricant from the high-pressure medium to be compressed medium is deposited, before the latter leaves the high-pressure housing 18.
  • slide is provided, which is guided in a slide receiving 52 parallel to the axes of rotation 33 and 35 of the screw rotors 32 and 34 in a direction of displacement 60 and, as in Fig. 1 to 13 shown, on the screw rotors 32 and 34 adjacent and the fferenassirbohrept 36 and 38 complementary end surfaces 54 and 56, which limit in the region in which these adjoin the screw rotors 32 and 34, which limit the compression chambers formed by these.
  • the end surfaces 54 and 56 extend along the slide 50 and that of a low pressure side on all sides of the slide receiving 52 adjacent end wall 58 to outlet edges 62 and 64, by their position along the screw rotors 32 and 34, in particular by their distance from a high-pressure side end wall 66 of the screw rotor bores 36 and 38, a high-pressure side outlet window 70 is defined, which extends between the end wall 66 and the outlet edges 62 and 64, wherein a distance of the outlet edges 62, 64 of the low-pressure inlet 42 determines a volume ratio of the screw compressor.
  • the volume ratio defines the volume of the first closed compression chamber between the screw rotors 32 and 34 to the volume of the last closed compression chamber of the screw rotors 32, 34, the volume of the last closed compression chamber by the position of the outlet edges 62 and 64, at which always the last closed compression chamber opens to the high pressure outlet 44, and thus also determined by the size of the outlet window 70.
  • the slider 50 is in a first ( Fig. 1 and 3 ) and a second ( Fig. 4 and 5 ) Position movable, wherein the first position corresponds to a large volume ratio, that is, the volume of the first closed compression chamber based on the volume of the last closed compression chamber results in a ratio greater than a small compression ratio, which is present when the Slider 50, as in Fig. 4 and 5 shown, in the second position is, in which the outlet edges 62 and 64 have a greater distance from the end wall 66 and thus the medium to be compressed is compressed in the last still closed compression chamber to a larger volume than in the first position, so that the Volume of the first inlet-side closed compression chamber relative to the last closed compression chamber results in a smaller ratio.
  • the slider receptacle 52 comprises a guide recess 72 extending in the direction of displacement 60 parallel to the screw rotors 32, 34 between an inlet-side end 46 of the screw rotors 32, 34 and an outlet-side end 48 of the screw rotors 32, 34 and one adjoining the guide recess 72 the inlet-side ends of the screw rotors 32, 34 extend beyond the guide recess 72 into the screw rotor housing 16 and beyond the inlet-side end 46, the screw rotor bores 36, 38 extending retraction space 74 in which the slider 50 in the second position to a greater extent means with a larger section immersed than in the first position.
  • the retraction space 74 is formed as part of the slide receptacle 52 so that it is at least capable of the guided by the guide trough 72 slide 50 with its cross-sectional shape and with its extension in the Displacement direction 60, in particular in the second position to record, so that a cross-sectional shape of the retraction 74 corresponds to at least one cross-sectional shape of the slider 50 and example, guide surfaces 76 of the guide trough 72 steplessly pass into the retraction 74.
  • the slider 50 To move the slider 50 between the in Fig. 1 illustrated first position, which corresponds to a large compression ratio, and the in Fig. 4 shown second position corresponding to a small compression ratio, the slider 50 is on its the outlet edges 62, 64 opposite and adjoining the end wall 58 side provided with a first cylinder member performing piston body 80, which dips into a second cylinder member performing cylinder housing 82 and in this back and forth is movable.
  • the cylinder housing 82 then extends into the guide recess 72 into the screw rotor housing 16, wherein the cylinder housing 82 in the first exemplary embodiment is formed directly into the screw rotor housing 16 and formed by the retraction space 74.
  • the cylinder housing 82 is formed so that this connects steplessly to the guide trough 72, that is, an inner cylinder surface 84 which corresponds to the guide trough 72 at least partially forming inner cylindrical surface 86 with respect to its central axis and its radius, at which the piston body 80 with a Piston seal 90 sealingly abuts ( Fig. 1 . 4 . 11 )
  • the cylinder housing 82 has in the direction of displacement 60 of the slider 50 has an extent which is so large that the piston body 80 in the first position corresponding to a larger volume ratio is still within the cylinder housing 82, but at maximum distance from an end wall 88 of the cylinder housing 82nd ,
  • the piston body 80 may be displaced so far in the direction of the high-pressure outlet 44, that the end wall 58 of the slider 50 is at a small distance from an inlet-side end 46 of the screw rotors 32, 34.
  • the slider 50 is shifted so far that the piston body 80 is close to the end wall 88, preferably rests against this.
  • the slider 50 can now be positioned in the solution according to the invention in the first and second position by a control 100 (FIG. Fig. 1 ), which is arranged on the one hand via a low pressure inlet 42 associated sensor 102, preferably upstream of the low pressure inlet 42, in particular between this and a suction-side shut-off valve 104 or even in a leading to the suction-side shut-off valve 104 suction line 105, and one the high-pressure outlet 44 associated sensor 106, in particular downstream of the high pressure outlet 44, in particular still in the high pressure housing 18, is arranged, determines the pressure ratio of the screw compressor and then according to the present pressure ratio, the slider 50 in the first position according to Fig. 1 or the second position according to Fig. 4 emotional.
  • the relief channel 130 opens into a in the region of a ridge 132, which is formed by the adjacent end surfaces 54 and 56 on the slider 50, the mouth opening 134, both in the first and in the second position with the low pressure in the region of the inlet ends 46 communicates.
  • an injection passage 138 is provided for injecting lubricant into the first compression chamber formed between the screw rotors 32 and 34 to cool and lubricate the screw rotors 32, 34 and seal the forming compression chambers.
  • an injection channel 140 is still provided in the slide 50, which extends from an injection port 142 on the comb 132 into an interior of the slider 50 and connected via connecting channels 144 running in the slide 50 to a supply opening 146 which is provided on a guide casing 150 of the slide 50 outside the end surfaces 54 and 56 and at least in the first position is aligned with a supply channel 148 provided in the screw rotor housing 16 (FIG. Fig. 3 ), but in the second position ( Fig. 5 ) is no longer aligned, since in this position no increased injection of lubricant is required.
  • the amount of lubricant that can be supplied per unit time via the injection opening 142 is at least twice the amount that can be supplied via the injection channel 138 per unit time of lubricant.
  • the slider 50 is still provided with a guide tongue 160, which is arranged on the underside 122 of the slider 50, preferably on a side opposite the outlet edges 62 and 64 side, and a slide receiving 52 facing guide 162, in which a held on the screw rotor housing 16 nut 164 engages, which secures the slider 50 against rotation in the slider receptacle 52 and thus precisely aligned.
  • a guide tongue 160 which is arranged on the underside 122 of the slider 50, preferably on a side opposite the outlet edges 62 and 64 side, and a slide receiving 52 facing guide 162, in which a held on the screw rotor housing 16 nut 164 engages, which secures the slider 50 against rotation in the slider receptacle 52 and thus precisely aligned.
  • the low-pressure line 116 'between the cylinder volume ZV and the suction side is provided with a throttle 117 so that it is not controlled.
  • connection between the supply line 112 to the cylinder space 82 and the high-pressure line 114 is only controlled via the valve block 108 'by means of the controller 100', wherein more refrigerant under high pressure flows into the cylinder space 82 when the valve block is opened via the supply line 112, as can flow off via the low pressure line 116 'and the throttle 117 to the low pressure inlet 42, so that in the end also high pressure in the cylinder chamber 82 builds up.
  • the second embodiment is according to Fig. 15 constructed in the same way as the first embodiment, so that with respect to all other features in full reference is made to the description of the first embodiment.
  • FIG Fig. 16 and Fig. 17 is in the cylinder chamber 82 nor a compression spring 170 is provided, which is supported on the end wall 88 and the slider 50 is acted upon in the direction of the second position, for example, the slider 50 is still provided with a receptacle 172 for the spring 170, which serves to guide the spring 170.
  • the receptacle 172 extends, for example, into the slider 50 and comprises a terminating surface 174, via which the spring 170 is supported on the slider 50.
  • the spring 170 provides an additional force in the direction of the first position of the slider 50, which can also be exploited, for example, in an unpressurized state of the screw compressor during the start of the screw compressor or a start-up phase of the same to push the slider 50 in the first position and at least during the start-up phase to hold in this first position.
  • FIG. 18 and 19 shown in FIG Fig. 18 and 19 is the cross-section of the second cylinder member 82 and thus the pressure in the cylinder volume ZV acted upon surface of the slider 50 is reduced in that on the end wall 88 ', a sleeve 180 is formed on the outer circumferential surface 182, a seal between the first cylinder member 80' and the sleeve 180 takes place.

Claims (15)

  1. Compresseur à vis comprenant un carter de compresseur à vis (12) avec un boîtier de rotors (16), des alésages destinés aux rotors (36, 38) disposés dans le boîtier de rotors (16), des rotors (32, 34) disposés dans les alésages destinés aux rotors (36, 38) et pouvant tourner autour d'axes de rotation (33, 35) dans le boîtier de rotors (16), un organe d'entraînement (20) pour les rotors (32, 34) et un coulisseau (50) qui est guidé de manière déplaçable dans un logement de coulisseau (52) dans le boîtier de rotors (16) et partiellement contigu aux rotors (32, 34) par le biais de surfaces d'extrémité (54, 56), permettant de régler un rapport volumique du compresseur à vis, qui s'étend en partant d'un espace d'entrée (74) du logement de coulisseau (52) dans une cuvette de guidage (72) du logement de coulisseau (52) ouverte vers les alésages destinés aux rotors (36, 38) en direction d'une sortie haute pression (44), et qui peut être positionné dans une première position et dans une deuxième position, le rapport volumique du compresseur à vis étant plus élevé dans l'une des positions que dans l'autre, caractérisé en ce que des poches basse pression (124, 126) sont prévues sur un côté (122) du coulisseau (50), opposé aux surfaces d'extrémités (54, 56) et se trouvant dans la cuvette de guidage (72), en ce que les poches basse pression (124, 126) sont maintenues en basse pression au moyen d'un canal de délestage (130) menant à l'admission basse pression (42).
  2. Compresseur à vis selon la revendication 1, caractérisé en ce que le coulisseau (50) est relié à un premier élément cylindrique (80) disposé au moins en partie dans l'espace d'entrée (74), lequel premier élément coopère avec un deuxième élément cylindrique (82) disposé au moins en partie dans l'espace d'entrée (74), et en ce que les éléments cylindriques (80, 82) sont disposés sur un côté du coulisseau (50), opposé à la sortie haute pression (44) dans le sens de déplacement (60) suivant le coulisseau (50).
  3. Compresseur à vis selon la revendication (2), caractérisé en ce que l'espace d'entrée (74) est conçu pour loger le premier élément cylindrique (80) aussi bien dans la première position que dans la deuxième, et en ce que l'espace d'entrée (74) est conçu pour loger le deuxième élément cylindrique (82).
  4. Compresseur à vis selon l'une quelconque des revendications précédentes, caractérisé en ce que l'espace d'entrée (74) est directement adjacent à la cuvette de guidage (72).
  5. Compresseur à vis selon l'une quelconque des revendications précédentes, caractérisé en ce que l'espace d'entrée (74) s'étend dans le boîtier de rotors (16).
  6. Compresseur à vis selon l'une quelconque des revendications précédentes, caractérisé en ce que l'espace d'entrée (74) présente un contour de section transversal au sens de déplacement (60) et est au moins suffisamment grand pour pouvoir loger le coulisseau (50) et le premier élément cylindrique (80).
  7. Compresseur à vis selon l'une quelconque des revendications précédentes, caractérisé en ce que le contour de section de l'espace d'entrée (74) est adapté au contour de section du premier élément cylindrique (80).
  8. Compresseur à vis selon l'une quelconque des revendications précédentes, caractérisé en ce que l'espace d'entrée (74) présente une zone de paroi (84) qui forme des faces de guidage du coulisseau guidant le coulisseau (50) dans l'espace d'entrée (74) transversalement au sens de déplacement (60).
  9. Compresseur à vis selon l'une quelconque des revendications précédentes, caractérisé en ce que le premier élément cylindrique (80) est solidement relié au coulisseau (50).
  10. Compresseur à vis selon la revendication 9, caractérisé en ce que le premier élément cylindrique (80) est aménagé de façon monolithique contre le coulisseau (50).
  11. Compresseur à vis selon l'une quelconque des revendications précédentes, caractérisé en ce que l'espace d'entrée (74) forme le deuxième élément cylindrique (82).
  12. Compresseur à vis selon l'une quelconque des revendications précédentes, caractérisé en ce que le premier élément cylindrique (80) et le deuxième élément cylindrique (82) incluent un volume de cylindre (ZV) pouvant être exposé soit à un fluide compressé à haute pression soit à un fluide existant à basse pression, en particulier à un fluide à compresser.
  13. Compresseur à vis selon l'une quelconque des revendications précédentes, caractérisé en ce que le coulisseau (50) est doté d'un orifice de pulvérisation (142) dirigé vers les rotors (32, 34) et destiné à des lubrifiants.
  14. Compresseur à vis selon la revendication 13, caractérisé en ce que l'orifice de pulvérisation (142) est relié à un canal de pulvérisation (140) prévu dans le coulisseau (50), canal vers lequel du lubrifiant peut être acheminé du côté du boîtier de rotors (16) par le biais de l'orifice d'alimentation (146).
  15. Compresseur à vis selon la revendication 13 ou la revendication 14, caractérisé en ce que la quantité de lubrifiant pulvérisée par le biais de l'orifice de pulvérisation (142) dans le coulisseau (50) est au moins égale à la quantité de lubrifiant pulvérisée par le biais du canal de pulvérisation (138).
EP12728244.0A 2011-07-11 2012-06-14 Compresseur à vis Active EP2732165B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102011051730A DE102011051730A1 (de) 2011-07-11 2011-07-11 Schraubenverdichter
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DE102011051730A1 (de) 2013-01-17
US10030653B2 (en) 2018-07-24
EP2732165A1 (fr) 2014-05-21
CN103649544B (zh) 2016-11-16
US20140127067A1 (en) 2014-05-08
WO2013007470A1 (fr) 2013-01-17
CN103649544A (zh) 2014-03-19

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