EP3440358B9 - Compresseur à vis - Google Patents

Compresseur à vis Download PDF

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Publication number
EP3440358B9
EP3440358B9 EP16714450.0A EP16714450A EP3440358B9 EP 3440358 B9 EP3440358 B9 EP 3440358B9 EP 16714450 A EP16714450 A EP 16714450A EP 3440358 B9 EP3440358 B9 EP 3440358B9
Authority
EP
European Patent Office
Prior art keywords
control
slider
screw compressor
compressor according
gap
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
EP16714450.0A
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German (de)
English (en)
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EP3440358A1 (fr
EP3440358B1 (fr
Inventor
Tihomir Mikulic
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
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Publication date
Application filed by Bitzer Kuehlmaschinenbau GmbH and Co KG filed Critical Bitzer Kuehlmaschinenbau GmbH and Co KG
Priority to EP21163537.0A priority Critical patent/EP3859159B1/fr
Publication of EP3440358A1 publication Critical patent/EP3440358A1/fr
Application granted granted Critical
Publication of EP3440358B1 publication Critical patent/EP3440358B1/fr
Publication of EP3440358B9 publication Critical patent/EP3440358B9/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/18—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by varying the volume of the working chamber
    • F04C28/185—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by varying the volume of the working chamber by varying the useful pumping length of the cooperating members in the axial direction
    • 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
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F04C18/023—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where both members are moving
    • 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

Definitions

  • the invention relates to a screw compressor comprising a compressor housing with a screw rotor space arranged in this housing, two screw rotors which are arranged in the screw rotor space and are each mounted on the compressor housing such that they can rotate about a screw rotor axis, which engage in one another with their screw contours and each interact with compression wall surfaces which adjoin and partially enclose them , in order to take up gaseous medium supplied via a low-pressure space arranged in the compressor housing and release it in the region of a high-pressure space arranged in the compressor housing, the gaseous medium being enclosed at low pressure with an intake volume in compression chambers formed between the screw contours and compression wall surfaces adjoining them and compressed to an end volume at high pressure is, as well as two running in a slide channel of the compressor housing in a parallel to the screw rotor axes Control slides arranged one behind the other in the displacement direction and adjoining both screw rotors with slide compression wall surfaces, which are movable in the displacement direction, a first control slide being arranged
  • control slides form an inflow space at least in a transitional position between the connected position and the disconnected position, into which the medium to be compressed flows from one of the compression chambers by being between the facing end faces of the control slides and that one of the control slides is provided with at least one discharge outlet adjacent to the inflow space, through which the medium from the inflow space enters an outflow opening on the slide channel that overlaps with the outflow outlet in this transitional position.
  • the advantage of the solution according to the invention can be seen in particular in the fact that it creates the possibility of obtaining defined flow conditions for the medium flowing out of the inflow chamber in the transitional position, which on the other hand in turn lead to defined pressure conditions in the region of the end regions of the control slides facing one another and thus allow a reliable transition from the composite position of the spool in their disconnected position.
  • the central recess could be provided in the first or in the second control slide.
  • the second spool Since the second spool is generally moved relative to the first spool during the transition from the connected position to the disconnected position, it is advantageous if the central recess is provided in the second spool so that its mass can be reduced.
  • the at least one outflow outlet is arranged in the second spool valve and thus the outflow opening provided in the transitional position with the outflow outlet can be arranged in the slide channel as close as possible to the low-pressure side.
  • the outflow outlet opens into the central recess of the second control slide.
  • the inflow space also extends into an intermediate space delimited by the mutually facing end regions of the control slides and the slide channel.
  • the slide channel is provided with at least one lateral outflow opening, ie the outflow opening is not on the front side of the slide channel but in longitudinal sides of the slide channel extending parallel to the direction of displacement.
  • the outflow outlet is arranged in a side wall area of the control slide that has it.
  • the outflow opening of the slide channel at least partially overlaps the intermediate space formed between the end regions of the control slides, so that in the disconnected position the medium essentially does not enter the outflow opening via the outflow outlet, but rather directly from the intermediate space between the control slides can enter the outflow outlet.
  • control slides are designed at their end regions facing one another in such a way that during a transition from the connected position to the disconnected position, they enter a first transitional position following the connected position first throttle gap forms with a transverse to the displacement direction gap width.
  • Such a first throttle gap makes it possible for the medium emerging from the compression chamber to enter the intermediate space between the control slides and thus in particular also in the inflow space in a throttled manner.
  • the first throttle gap is arranged offset in the displacement direction relative to the end faces of the control slides facing one another. This creates the possibility of forming the throttle gap independently of the gap formed between the end faces.
  • the first throttle gap has a smaller gap width in the first transitional position than the gap formed between the end faces of the control slides, so that the outflow of the medium can be defined exclusively through the throttle gap and thus the possibility is created in which first transitional position to provide defined flow conditions for the outflowing medium.
  • the first throttle gap with its gap width is present over a distance in the displacement direction that is greater than the gap width of the throttle gap, so that the first transitional position can be realized over a significant defined distance in the displacement direction.
  • the first throttling gap can be designed in a wide variety of ways.
  • the first throttle gap is delimited by two wall surfaces, one of which is arranged on the end area of the first control slide and the other on the end area of the second control slide.
  • the wall surfaces are preferably located in such a way that the wall surface formed by the end region of the first control slide runs adjacent to the end face of the first control slide.
  • the wall surface arranged on the end region of the second control slide runs adjacent to the end face of the second control slide.
  • An advantageous solution provides that at least one of the wall surfaces runs essentially parallel to the direction of displacement.
  • both wall surfaces run essentially parallel to the direction of displacement, so that the gap width does not vary during a movement in the direction of displacement in the first transitional position.
  • control slides are designed at their mutually facing end regions such that in a second transitional position lying between the first transitional position and the disconnected position, a second throttle gap is formed with a gap width running transversely to the direction of displacement that is greater than the Gap width of the first throttle gap.
  • the second throttle gap is arranged in such a way that it is delimited by at least one wall surface, which is arranged on a side of the wall surface delimiting the first throttle gap, facing away from the end face.
  • This wall surface is preferably set back in relation to the wall surface of this control body which delimits the first throttle gap, in order to achieve a larger gap width.
  • the second throttle gap is delimited by a wall surface which also delimits the first throttle gap.
  • a further advantageous embodiment provides that at least one of the end faces of the control slides has a sealing edge surface adjoining the slide compression wall surfaces and on a side of the sealing edge surface opposite the slide compression wall surfaces adjoining the latter and opposite the sealing edge surface in a direction parallel to the Has displacement direction recessed or lowered inner surface.
  • This solution has the advantage that, firstly, the sealing edge surface of one end face can form a seal with the other end face in the connected position and, on the other hand, the recessed or lowered inner surface is available to build up a force that contributes to moving the control slides apart.
  • the sealing edge surface extends so far in the direction of the slide channel that it is still adjacent to a partial surface of the circumferential guide surface of the respective control slide, so that a reliable seal is created by the sealing edge surface with the opposite end face of the other control slide is guaranteed.
  • the inner surface which is set back from the sealing edge surface, forms a gap space with the opposite end face in the combined position of the control slides, which gap is connected to an inflow space delimited by the control slides in the connected position and is at the same pressure level as the inflow space, so that as a result a force that is already effective in the composite position can be generated, which supports the spool valves moving apart.
  • the inflow chamber is at low pressure in the composite position of the control slides.
  • the inflow chamber is connected to the low-pressure chamber of the compressor housing when the control slides are in the composite position, in that in the composite position an outflow outlet in one of the control slides is arranged so that it overlaps with the outflow opening on the slide channel.
  • the illustrated exemplary embodiment of a screw compressor 10 comprises a compressor housing, designated as a whole with 12, which has a suction connection 14, via which a gaseous medium to be sucked in, in particular refrigerant, is sucked in and a pressure connection 16, via which the gaseous medium compressed to high pressure, in particular the refrigerant, is delivered, has.
  • a helical rotor space 18 of the compressor housing 12 are provided two helical rotors 26, 28, each rotatable about a helical rotor axis 22, 24, which engage in one another with their helical contours 32 and 34 and interact with compression wall surfaces 36 and 38 of the helical rotor chamber 18 adjoining them on the circumferential side, in order to receive a gaseous medium fed to the screw contours 32, 34 adjoining the suction side of the low-pressure chamber 42, to compress it and to release it at high pressure into a high-pressure chamber 44 in the compressor housing 12.
  • the gaseous medium in particular refrigerant, is enclosed in compression chambers formed between the screw contours 32, 34 and the compression wall surfaces 36, 38 adjoining them at low pressure in an intake volume and is compressed to a final volume at high pressure.
  • the operating state of the screw compressor 10 is adjusted on the one hand with regard to the volume ratio, which indicates the relation between the maximum enclosed suction volume and the discharged end volume, and on the other hand with regard to the compressor performance, which indicates the proportion of the volume flow actually compressed by the screw compressor in relation to the maximum volume flow that can be compressed by the screw compressor 10 .
  • a first control slide 52 and a second control slide 54 arranged one behind the other in a slide channel 56 provided in the compressor housing 12, the slide channel 56 running parallel to the screw rotor axes 22, 24 and the first Control slide 52 and the second control slide 54 in the region of their non-adjacent to the screw rotor 26, 28 peripheral guide surface 58 in a defined by the slide channel 56 displacement direction 72.
  • the first spool valve 52 faces the high-pressure chamber 44 and is therefore arranged on the high-pressure side, and the second spool valve 54 is arranged on the low-pressure side relative to the first spool valve 52 .
  • Each of the two control slides 52 and 54 also has a slide compression wall surface 62 adjoining screw rotor 26 and a slide compression wall surface 64 adjoining screw rotor 28, which represent partial areas of compression wall surfaces 36 and 38, and housing compression wall surfaces 66 and 68 formed by compressor housing 12, which also Represent partial surfaces of the compression wall surfaces 36 and 38, supplement to the compression wall surfaces 36 and 38, which together with the screw contours 32 and 34 contribute to the formation of the compression chambers.
  • the first spool valve 52 and the second spool valve 54 are, as in Figures 2 to 15 shown, designed in such a way that they are identical insofar as they form the slide compression wall surfaces 62 and 64 as well as the peripheral guide surface 58 and thus they can be guided displaceably in the slide channel 56 of the compressor housing 12 in a single displacement direction 72 running parallel to the screw rotor axes 22, 24 .
  • the first control slide 52 forms an outlet edge 82 facing the high-pressure chamber 44 and defining the end volume of the compression chambers Compression chambers and thus the volume ratio co-determined.
  • the first control slide 52 and the second control slide 54 have end faces 86 and 88, respectively, adjoining the slide compression wall surfaces 62, 64, running transversely thereto and facing one another, with which these, as for example in 4 shown, are abuttable such that the spool compression wall surfaces 62 and 64 of the first spool 52 and the second spool 54 merge into one another.
  • a compression spring 104 is preferably also provided, which serves to act on the first control slide 52 relative to the second control slide 54 in such a way that the end faces 86 and 88 can be moved away from one another.
  • a cylinder arrangement 112 which comprises a cylinder chamber 114 and a piston 116, the piston 116 being connected to a piston rod 118 which establishes a connection to the first control slide 52, for example with an in 2 and 4 shown extension 122 of the first control slide 52, which is arranged for example on a side opposite the end face 86 of the same.
  • the cylinder arrangement 112 is located in particular on a side of the first control slide 52 opposite the second control slide 54, preferably in a high-pressure-side housing section 124 of the compressor housing 12, which is connected to the slide channel 56 and to the high-pressure chamber 44 and thus on the low-pressure chamber 42 opposite side of the compressor housing 12 is arranged.
  • the second control slide 54 can be displaced by a cylinder arrangement 132, which comprises a piston 136 that can be moved in a cylinder chamber 134, with the cylinder chamber 134 extending in particular as a continuation of the slide channel 56 in a low-pressure-side housing section 142, in which, for example, drive-side bearing units for the screw rotors 26 and 28 are arranged, which can be driven via a drive shaft 143, for example.
  • a cylinder arrangement 132 which comprises a piston 136 that can be moved in a cylinder chamber 134, with the cylinder chamber 134 extending in particular as a continuation of the slide channel 56 in a low-pressure-side housing section 142, in which, for example, drive-side bearing units for the screw rotors 26 and 28 are arranged, which can be driven via a drive shaft 143, for example.
  • the piston 136 is integrally formed on the second spool valve 54 and has a piston area that corresponds at least to the cross-sectional area of the second spool valve 54 .
  • the low-pressure side housing section 142 which accommodates the cylinder chamber 134 for the cylinder arrangement 132 for moving the second control slide 54, is located in an area of the compressor housing 12 which is arranged opposite the high-pressure side housing section 124 for accommodating the cylinder chamber 114 for the cylinder arrangement 112.
  • the first spool valve 52 and the second spool valve 54 can be pushed together by the cylinder assemblies 112 and 132 to such an extent that the end faces 86 and 88 abut one another in a composite position, and the two spool valves 52, 54 can also be operated together in the composite position like a single spool valve move, which extends from the suction-side closing surface 126 in the direction of the pressure-side closing surface 84 and whose outlet edge 82 contributes to determining the volume ratio, wherein, as in FIG 4 and 6 shown, the screw compressor 10 always promotes the maximum volume flow in this compound position.
  • the volume ratio can be adjusted, which is based on the position according to FIG 4 present minimum value as the distance decreases of the outlet edge 82 rises from the end surface 84 and reaches its maximum value when the outlet edge 82 is at the minimum distance from the end surface 84 required to minimize the final volume, such as in FIG 6 shown.
  • the compressor output i.e. the volume flow actually delivered
  • this is done, as for example in Figures 7 to 15 shown, separating the end faces 86 and 88 by moving the control slides 52 and 54 apart into a disconnected position, in particular by moving the second control slide 54 in the direction of the low-pressure-side housing section 142.
  • the second control slide 54 has no effect, since the medium to be compressed flows out of the compression chamber located above the end faces 86 and 88 between the control slides 52, 54 in the direction of the slide channel 56, which is connected to the low-pressure chamber 42 via the side of the slide channel 56 in the compressor housing 12 arranged outflow openings 144 ( 2 ) and is connected to these adjoining channels in the compressor housing 12.
  • Discharge openings 144 lying opposite one another are preferably arranged on opposite longitudinal sides of the slide channel 56 .
  • the outflow openings 144 extend in particular over a region of the slide channel 12 which extends from the suction-side closing surface 126 in the direction of the pressure-side closing surface 84 .
  • the position of the end face 86 of the first control slide 52 defines the initial volume.
  • the outlet edge 82 is not in a position in which it specifies the minimum possible end volume, the relation of the initial volume, specified by the end face 86, to the end volume, specified by the outlet edge 82, is not variable.
  • the second spool valve 54 In order to eliminate the effect of the second spool valve 54 in the disconnected position, it is moved into the housing section 142 in particular by means of the cylinder arrangement 132, with the cylinder chamber 134 being dimensioned such that it also includes an insertion space 148 for the second spool valve 54 and thus the possibility manages to move the second spool 54 far enough away from the first spool 52 that the face 88 no longer affects the initial volume.
  • the second spool valve 54 thus makes it possible to influence the initial volume in that it either rests with its end face 88 against the end face 86 of the first spool valve 52 to form the combined position of the control slide valves 52, 54 and thus maximizes the initial volume, or with its own end face 88 in such a way can be moved far away from the end face 86 of the first spool valve 52 so that the initial volume is no longer influenced by the second spool valve 54 .
  • control slides 52, 54 are stepped at their mutually facing end regions 152, 154, the second control slide 54 having a slide compression wall surfaces 62, 64 and the end face 88 and thus adjoining the screw contours 32, 34 extension 164, while the first control slide 52 has an extension 162 which protrudes beyond the end face 86 in the direction of the second control slide 54 and which in particular lies essentially in the slide channel 56 .
  • the extensions 164 and 162 are preferably formed in such a way that in 4 and 6 In the composite position shown, the extension 164 overlaps the extension 162 in such a way that the end faces 88 and 86 of the control slides 54 and 52 rest against one another in a sealing manner and the slide compression wall surfaces 62, 64 merge into one another.
  • the extension 164 in particular is designed in such a way that it also includes partial surfaces 172 of the peripheral guide surface 58 of the second control slide 54 adjoining the slide compression wall surfaces 62, 64 and the end face 68, so that the extension 164 in turn is also guided in the slide channel 56 ( 9 ).
  • extension 162 in turn forms a partial surface 174 that supplements the partial surfaces 172 in the circumferential direction to form the circumferential surface 58.
  • the extension 162 further includes a cylindrical extension 176 which, as for example in 4 and 6 shown, forms a receptacle 178 for the compression spring 104, which, starting from this receptacle 178, extends to a support flange 182 of a central recess 184 provided in the second control slide 54 and with a force which moves the control slides 52, 54 away from one another and acts on the control slides 52 , 54 acts.
  • a cylindrical extension 176 which, as for example in 4 and 6 shown, forms a receptacle 178 for the compression spring 104, which, starting from this receptacle 178, extends to a support flange 182 of a central recess 184 provided in the second control slide 54 and with a force which moves the control slides 52, 54 away from one another and acts on the control slides 52 , 54 acts.
  • first throttle gap 196 in a first transitional position occurring during the transition from the connected position to the disconnected position a first gap width SB1 running transversely to the displacement direction 72, which, as in 7 and particularly 8 shown, throttles an inflow of the medium to be compressed into an inflow space 198, which forms the central recess 184 in the second spool valve 54 and a transverse position between the spool valves 52, 54 as a result of the movement from the connected position in the direction of the disconnected position and transversely to the displacement direction of the slide channel 56 limited space 202 includes.
  • the second control slide 54 is provided in the area of its side walls 214 forming the peripheral guide surfaces 58 with outflow outlets 212, in particular outflow windows 212, which in the central recess 184 delimiting side walls 214 of the second control slide 54 are arranged ( 7 , 9 to 11 ), wherein the outflow outlets 212 are positioned so that they are arranged overlapping with the side outflow openings 144 in the first transition position.
  • the extent of the intermediate space 202 in the displacement direction 72 is so small that it does not overlap with the outflow openings 144 or does so to a significant extent.
  • the first throttle gap 196 is decisive for the throttling of the outflowing medium due to the flow paths designed in this way.
  • the first throttle gap 196 formed between the first wall surfaces 192 and 194 of the extensions 162, 164 is ineffective, and a second throttle gap 222 is formed with a second gap width SB2 running transversely to the displacement direction 72 and with a larger cross section than the first throttle gap 196 between the wall surface 194 of the extension 164 and a wall surface 224 of the first extension 162 that is set back from the wall surface 192.
  • the outflow outlets 212 are arranged so that they overlap with the outflow openings 144, so that the second throttle gap 222 is decisive for throttling the outflowing medium.
  • the end face 88 is provided with a sealing edge surface 232 adjoining the slide compression wall surfaces 62, 64 and the partial surface 172 of the guide peripheral surface 58, relative to which an inner surface 234 runs set back or lowered, so that between this inner surface 234 and end face 86 creates a gap space 236 in which there is medium under low pressure even when the control slides 52, 54 are in the connected position, so that the inner surface 234 acted upon by the low pressure and the partial area of the end face 86 facing it counteract the cylinder arrangements 112 and 132 forces that promote the transition from the connected position to the disconnected position and thus make it more reliable ( Figures 9 to 11 ).
  • a position detection device designated as a whole by 252 which comprises a detector element 254 that extends parallel to the displacement direction 72 of the control slides 52, 54 and thus parallel to the helical rotor axes 22, 24. which is able to detect the positions of position indicators 256 and 258.
  • Position indicator element 256 is rigidly coupled to first spool valve 52, specifically to extension 162 of first spool valve 52, and position indicator element 258 is coupled to second spool valve 54, specifically to that in spool channel 56 and to first spool valve 52 facing end region 154 of the same, as in particular in 15 shown.
  • each of these position indicator elements 256 and 258 comprises a fork body, designated as a whole with 274, which with its two fork legs 276 and 278 delimits an intermediate space 282 lying between them, through which the elongate detector element 254 runs.
  • Each of these fork bodies 274 is coupled to the corresponding control slide 52, 54 via a connecting body 272 connected to the extension 162 or the end region 154 ( 15 ).
  • the connecting bodies 272 which are held on the respective control slides 52, 54, pass through an elongate, slot-shaped passage 294, which is molded into a housing wall 296 forming the slide channel 56 and has a length which, in the disconnected position, allows the second control slide 54 to be fully retracted into the drive-in space 148 and a position of the first control slide 52 with a minimum initial volume and a position of the first control slide 52 with a minimum volume ratio, i.e. maximum distance of the outlet edge 82 from the pressure-side closing surface 84, and also a position of the second control slide 54 in the compound position with the first spool 52 at maximum volume ratio and minimum volume ratio.
  • Each connecting body 272 connected to the respective control slide 52 or 54 forms, together with the slot-shaped passage 294, an anti-twist device for the respective control slide 52, 54, similar to a guide using a sliding block and a groove, so that there is no need to 54 grooves are to be provided which interact with sliding blocks protruding into the slide channel 56 ( 12 and 15 ).
  • the passage 294 is always maintained at the pressure in the low-pressure chamber 42 and thus also serves to keep the control slides 52, 54 with their peripheral guide surface 58 in contact with the slide channel 56, so that the control slides 52, 54 do not push through between the slide channel 56 and high pressure forming guide peripheral surface 58 with vane compression wall surfaces 62,64 against helical rotors 26,28.
  • the passage 294 is sealed against higher pressures, in particular also high pressure, by the narrowly tolerable gap between the slide channel 56 and the peripheral guide surface 58 of the control slides 52, 54.
  • a controller 318 is provided which, through the connection to the position detection device 252, is able to determine the actual positions of the control slides 52, 54.
  • the cylinder assemblies 112 and 132 can be controlled in order to position the control slides 52, 54.

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

Claims (15)

  1. Compresseur à vis (10) comprenant un boîtier de compresseur (12) avec un espace de rotor à vis (18) agencé dans celui-ci, deux rotors à vis (26, 28), qui sont agencés dans l'espace de rotor à vis (18) et logés de manière à pouvoir tourner au niveau du boîtier de compresseur (12) respectivement autour d'un axe de rotor à vis (22, 24), qui viennent en prise l'un dans l'autre avec leurs contours hélicoïdaux (32, 34) et coopèrent respectivement avec des surfaces de paroi de compression (36, 38) contiguës à ceux-ci et entourant partiellement ceux-ci, afin de recevoir du milieu gazeux amené par le biais d'un espace à basse pression (42) agencé dans le boîtier de compresseur (12) et de le sortir dans la zone d'un espace à haute pression (44) agencé dans le boîtier de compresseur (12), le milieu gazeux étant englobé dans des chambres de compression formées entre les contours hélicoïdaux (32, 34) et des surfaces de paroi de compression (36, 38) contiguës à ceux-ci en cas de basse pression avec un volume d'aspiration et étant comprimé à un volume terminal en cas de haute pression, ainsi que deux tiroirs de commande (52, 54) agencés l'un derrière l'autre dans un canal de tiroir (56) du boîtier de compresseur (12) dans une direction de déplacement s'étendant parallèlement aux axes de rotor à vis (22, 24) et contigus aux deux rotors à vis (26, 28) avec des surfaces de paroi de compression de tiroir (62, 64), qui sont mobiles dans la direction de déplacement (72), un premier tiroir de commande (52) étant agencé en influençant le volume terminal et un deuxième tiroir de commande (54) étant agencé en influençant le volume initial, le premier tiroir de commande (52) et le deuxième tiroir de commande (54) étant mobiles dans une position combinée avec des côtés avant (86, 88) tournés l'un vers l'autre se terminant de manière étanche l'un avec l'autre et ensemble dans la direction de déplacement (72) et étant positionnables dans une position de séparation à distance l'un de l'autre en formant un espace intermédiaire (202),
    caractérisé en ce que les tiroirs de commande (52, 54) forment au moins dans une position de transition se trouvant entre la position combinée et la position de séparation un espace d'admission (198), dans lequel le milieu à compresser afflue à partir d'une des chambres de compression en ce qu'il passe entre les côtés avant (86, 88) tournés l'un vers l'autre des tiroirs de commande (52, 54), et qu'un des tiroirs de commande est pourvu d'au moins une sortie d'évacuation (212) contiguë à l'espace d'admission (198), par laquelle le milieu entre de l'espace d'admission (198) dans une ouverture d'évacuation (144) recouvrant dans cette position de transition la sortie d'évacuation (212) au niveau du canal de tiroir (56).
  2. Compresseur à vis selon la revendication 1, caractérisé en ce que l'espace d'admission (198) s'étend dans un évidement central (184) d'un des tiroirs de commande (54).
  3. Compresseur à vis selon la revendication 2, caractérisé en ce que l'évidement central (184) est prévu dans le deuxième tiroir de commande (54).
  4. Compresseur à vis selon l'une des revendications précédentes, caractérisé en ce que l'au moins une sortie d'évacuation (212) est agencée dans le deuxième tiroir de commande (54).
  5. Compresseur à vis selon la revendication 4, caractérisé en ce que la sortie d'évacuation (212) débouche dans l'évidement central (184) du deuxième tiroir de commande (54).
  6. Compresseur à vis selon l'une des revendications précédentes, caractérisé en ce que l'espace d'admission (198) s'étend aussi dans un espace intermédiaire (202) délimité par les zones terminales (152, 154) tournées l'une vers l'autre des tiroirs de commande (52, 54) et le canal de tiroir (56).
  7. Compresseur à vis selon l'une des revendications précédentes, caractérisé en ce que le canal à tiroir (56) est pourvu d'au moins une ouverture d'évacuation (144) latérale.
  8. Compresseur à vis selon l'une des revendications précédentes, caractérisé en ce que la sortie d'évacuation (212) est agencée dans une zone de paroi latérale du tiroir de commande (54) la présentant.
  9. Compresseur à vis selon l'une des revendications précédentes, caractérisé en ce que dans la position de séparation l'ouverture d'évacuation (144) du canal à tiroir (56) recouvre au moins partiellement l'espace intermédiaire (202) se formant entre les zones d'extrémité (152, 154) des tiroirs de commande (52, 54).
  10. Compresseur à vis selon l'une des revendications précédentes, caractérisé en ce que les tiroirs de commande (52, 54) sont réalisés au niveau de leurs zones d'extrémité (152, 154) tournées l'une vers l'autre de sorte que lors d'une transition de la position combinée dans la position de séparation une première fente d'étranglement (196) se réalise avec une largeur de fente s'étendant transversalement à la direction de déplacement (72) dans une première position de transition suivant la position combinée, notamment que la première fente d'étranglement (196) est agencée en déport par rapport aux côtés avant (86, 88) tournés l'un vers l'autre des tiroirs de commande (52, 54) dans la direction de déplacement (72).
  11. Compresseur à vis selon la revendication 10, caractérisé en ce que la première fente d'étranglement (196) présente dans la première position de transition une largeur de fente plus faible que la fente se formant entre les côtés avant (86, 88) des tiroirs de commande (52, 54).
  12. Compresseur à vis selon la revendication 10 ou 11, caractérisé en ce que la première fente d'étranglement (196) se présente avec sa largeur de fente sur une course dans la direction de déplacement (72) qui est supérieure à la largeur de fente de la première fente d'étranglement (196).
  13. Compresseur à vis selon l'une des revendications 10 à 12, caractérisé en ce que la première fente d'étranglement (196) est délimitée par deux surfaces de paroi (192, 194), dont une (192) est agencée au niveau de la zone d'extrémité (152) du premier tiroir de commande (54) et une autre (194) est agencée au niveau de la zone d'extrémité (154) du deuxième tiroir de commande (54), notamment que
    la surface de paroi (192) formée par la zone d'extrémité (152) du premier tiroir de commande (52) s'étend de manière contiguë au côté avant (86) du premier tiroir de commande (52), notamment que la surface de paroi (194) agencée au niveau de la zone d'extrémité (152) du deuxième tiroir de commande (54) s'étend de manière contiguë au côté avant (88) du deuxième tiroir de commande (54).
  14. Compresseur à vis selon l'une des revendications 10 à 13, caractérisé en ce qu'au moins une des surfaces de paroi (192, 194) s'étend sensiblement parallèlement à la direction de déplacement (72).
  15. Compresseur à vis selon l'une des revendications précédentes, caractérisé en ce que les tiroirs de commande (52, 54) sont réalisés au niveau de leurs zones d'extrémité (152, 154) tournées l'une vers l'autre de sorte que dans une deuxième position de transition se trouvant entre la première position de transition et la position de séparation une deuxième fente d'étranglement (222) se réalise avec une largeur de fente s'étendant transversalement à la direction de déplacement (72) qui est supérieure à la largeur de fente de la première fente d'étranglement (196), notamment que la deuxième fente d'étranglement (222) est délimitée par au moins une surface de paroi qui est agencée sur un côté éloigné du côté avant (86) de la surface de paroi (192) délimitant la première fente d'étranglement (196), et/ou notamment que la deuxième fente d'étranglement (222) est délimitée par une surface de paroi (194) qui délimite aussi la première fente d'étranglement (196).
EP16714450.0A 2016-04-06 2016-04-06 Compresseur à vis Active EP3440358B9 (fr)

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JP6500964B1 (ja) * 2017-10-30 2019-04-17 ダイキン工業株式会社 スクリュー圧縮機
CN110410329A (zh) * 2019-08-26 2019-11-05 珠海格力电器股份有限公司 压缩机及空调

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US4516914A (en) * 1982-09-10 1985-05-14 Frick Company Micro-processor control of moveable slide stop and a moveable slide valve in a helical screw rotary compressor
JPS59188076A (ja) * 1984-03-23 1984-10-25 Kobe Steel Ltd スライド弁式スクリユ圧縮機
US5183395A (en) * 1992-03-13 1993-02-02 Vilter Manufacturing Corporation Compressor slide valve control
JPH09317676A (ja) * 1996-05-23 1997-12-09 Hitachi Ltd スクリュー圧縮機の容量制御装置
ATE516440T1 (de) * 2005-12-12 2011-07-15 Johnson Controls Denmark Aps Schraubenkompressor
US7891955B2 (en) * 2007-02-22 2011-02-22 Vilter Manufacturing Llc Compressor having a dual slide valve assembly
US8813492B2 (en) * 2009-10-14 2014-08-26 Hansen Engine Corporation Internal combustion engine and supercharger
RU2418193C1 (ru) * 2009-10-27 2011-05-10 Закрытое акционерное общество "Научно-исследовательский и конструкторский институт центробежных и роторных компрессоров им. В.Б. Шнеппа" Винтовой компрессор с регулятором производительности
CN203257685U (zh) * 2012-12-26 2013-10-30 福建雪人压缩机科技有限公司 机械式高精度螺杆压缩机能量及内容积比滑阀调节机构
DE102015116324A1 (de) * 2014-10-08 2016-04-14 Bitzer Kühlmaschinenbau Gmbh Schraubenverdichter
EP4245997A3 (fr) * 2016-04-06 2023-12-27 BITZER Kühlmaschinenbau GmbH Unité de compresseur et procédé de fonctionnement d'une unité de compresseur

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Publication number Publication date
US20190032661A1 (en) 2019-01-31
EP3859159A1 (fr) 2021-08-04
EP3859159B1 (fr) 2024-03-27
RU2713784C1 (ru) 2020-02-07
US11286935B2 (en) 2022-03-29
EP3440358A1 (fr) 2019-02-13
CN109072919A (zh) 2018-12-21
WO2017174130A1 (fr) 2017-10-12
CN109072919B (zh) 2020-05-12
EP3440358B1 (fr) 2021-03-24

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