US20200309129A1 - Displacement compressor system for r-718 - Google Patents

Displacement compressor system for r-718 Download PDF

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Publication number
US20200309129A1
US20200309129A1 US16/617,908 US201816617908A US2020309129A1 US 20200309129 A1 US20200309129 A1 US 20200309129A1 US 201816617908 A US201816617908 A US 201816617908A US 2020309129 A1 US2020309129 A1 US 2020309129A1
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rotor
spindle
compressor
displacement
evaporator
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Ralf Steffens
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    • 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
    • F04C18/48—Rotary-piston pumps with non-parallel axes of movement of co-operating members
    • F04C18/54—Rotary-piston pumps with non-parallel axes of movement of co-operating members the axes being arranged otherwise than at an angle of 90 degrees
    • F04C18/56—Rotary-piston pumps with non-parallel axes of movement of co-operating members the axes being arranged otherwise than at an angle of 90 degrees of intermeshing engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C18/565—Rotary-piston pumps with non-parallel axes of movement of co-operating members the axes being arranged otherwise than at an angle of 90 degrees of intermeshing engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing the axes of cooperating members being on the same plane
    • 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
    • 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
    • F04C18/082—Details specially related to intermeshing engagement type pumps
    • F04C18/084—Toothed wheels
    • 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
    • F04C18/48—Rotary-piston pumps with non-parallel axes of movement of co-operating members
    • F04C18/54—Rotary-piston pumps with non-parallel axes of movement of co-operating members the axes being arranged otherwise than at an angle of 90 degrees
    • 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
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/04—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type
    • F25B1/047—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type of screw type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B31/00—Compressor arrangements
    • F25B31/02—Compressor arrangements of motor-compressor units
    • F25B31/026—Compressor arrangements of motor-compressor units with compressor of rotary 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
    • F04C2210/00—Fluid
    • F04C2210/10—Fluid working
    • F04C2210/1094—Water
    • 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
    • F04C2240/40—Electric motor
    • F04C2240/402—Plurality of electronically synchronised motors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/60—Shafts
    • F04C2240/603—Shafts with internal channels for fluid distribution, e.g. hollow shaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/07—Details of compressors or related parts
    • F25B2400/071—Compressor mounted in a housing in which a condenser is integrated

Definitions

  • Refrigeration technology can be represented via two broad areas here:
  • turbo-compressors Although these machines only generate lower pressure ratios of approximately 6 despite their two-stage configuration with intermediate cooling so that the necessary heat transfer at the condenser is realized merely to an unsatisfactory degree in the cooling circuit.
  • turbomachine the serious disadvantage of its soft working characteristic (i.e. pressure values above volume flow) in order to be able to ensure stable operating points for various operating points.
  • the R718 displacement compressor system provides the following advantages:
  • the compressor machine ( 41 ) is configured here in accordance with the disclosure as an open machine that separates the evaporator ( 7 ) and the condenser ( 8 ) by means of the compressor housing ( 1 ).
  • the compressor machine thus no longer has face-side compressor-limiting lateral parts (so-called “covers”) and can no longer be operated in an autarkic manner as a vacuum machine but rather only in conjunction with a connected evaporator ( 7 ) and a connected condenser ( 8 ) with respective housing vessels ( 28 and 29 ).
  • the drive motors ( 2 . 3 and 3 . 3 ) for each spindle-rotor rotation unit ( 40 and 39 ) are located on the compressor inlet side ( 11 ) and suspended directly in the evaporator chamber ( 7 ) for optimal cooling of the electric drive motors ( 2 . 3 and 3 . 3 ) for the “unlimited” operation in accordance with the disclosure by purging the heat losses of these drive motors ( 2 . 3 and 3 . 3 ) via the respective refrigerant fluid flows K 5 in the event of increased (i.e. above the nominal load) performance demands during operation.
  • the monitoring of the drive motors ( 2 . 3 and 3 . 3 ) preferably occurs via temperature sensors in the area of the motor windings in order to be able to adapt the respective refrigerant fluid flows K 5 accordingly so that the drive motors are not damaged and can provide the performance demanded.
  • an intermediate water jacket ( 5 ), preferably with its own cooling tube coil ( 6 ), is part of this thermal balance management system according to the disclosure for the R718 displacement compressor system in order to operate the selective thermostatic control for the compressor housing ( 1 ) via the refrigerant fluid flow K 1 .
  • the selective interior cooling of the rotors ( 2 . 2 and 3 . 2 ) by means of a refrigerant fluid flow K 2 and K 3 (as 9 . 2 and 9 . 3 ) remains simultaneously possible, the situation with respect to the play between the working-space structural components (i.e.
  • compressor housing and spindle-rotor pair is regulated, and via the inner gap leakage thus the volumetric efficiency for the different operating/working points as a result of the respective thermal expansion behaviours of the structural components (which is saved in the control unit ( 15 ) for the regulation of the refrigerant fluid flows ( 9 )), while crashes are simultaneously reliably avoided (crash as a disruptive consumption of play).
  • the thermal balance management according to the disclosure for the R718 displacement compressor system in the “maximum” version* ⁇ * comprises the following refrigerant fluid flows ( 9 ) regulated in a selective manner via control unit ( 15 ):
  • This thermal balance management system is crucially necessary in particular for the working-space structural components during so-called k 0 operation, when the compressor is operated at a speed that, although creating the difference in pressure between the inlet and the outlet, does not yet convey or only conveys a minimum volume flow, as a result of which the compressor thus only contends with its own (interior) leakage, but would become accordingly hot on account of the power injection, which is reliably avoided by the thermal balance management system managed by the control unit ( 15 ) in accordance with the disclosure.
  • a centrifugal disk ( 22 ) is preferably arranged on every spindle rotor on the gas inlet side ( 11 ) in accordance with the disclosure for the speed-optimized introduction of the injection refrigerant quantity K 4 , wherein the refrigerant-fluid-flow-K 4 feed according to ( 23 . 1 ) or ( 23 . 2 ) on the preferably rough surface of the centrifugal disk ensures a speed-optimized refrigerant-fluid-flow-K 4 mist, which is mixed with the gas flow in a sufficiently even manner.
  • Speed-optimized is understood to mean here that the velocity vectors of the liquid refrigerant-fluid-flow-K 4 mist droplets move similarly to the spindle-rotor surfaces, which is ensured by each centrifugal disk ( 22 ). A hard impact on the spindle-rotor surfaces as a result of large differences in velocity, and consequently at the least an unpleasant patter noise up to the damage of the spindle-rotor surfaces, is consequently reliably avoided.
  • both the be. 2 K.em(z) distribution as well as the ⁇ .be. 2 K(z) distribution are at a minimum.
  • both the be. 2 K.em(z) distribution as well as the ⁇ n.be. 2 K(z) distribution decrease, whereas, in the event of a sharply decreasing m(z) in the inlet area, both the be. 2 K.em(z) distribution as well as the ⁇ .be. 2 K(z) distribution increase sharply.
  • This feature according to the disclosure is valid with a precision of preferably ⁇ 15% and ensures on the inlet side ( 11 ), i.e. for the area of larger z values in the form of representation chosen here, higher volumes of the working chambers on the inlet side in order to consequently be able to suction larger displacement volume flows.
  • control balls ( 10 ) are provided for the selective adaptation of the inner compression ratios in accordance with the specific application, i.e. in particular in the event of different pressure values in the condenser as different working points during the operation of the R718 displacement compressor system.
  • the inner volume ratio is, initially without taking thermodynamic effects into account, dependent on the geometry of the configured spindle-rotor pair as the simple ratio of the inlet working-chamber volume to the outlet working-chamber volume, which is determined at the time of manufacture of the spindle-rotor pairing.
  • the control balls ( 10 ) ensure that efficiency-reducing overcompression is avoided in that the control ball is raised as a result of the pressure difference when the current outlet pressure p 2 is reached in the particular working chamber during compression, so that a partial gas flow leaves the working chamber in the direction of the outlet space ( 12 ) and thus to the condenser ( 8 ).
  • This preferably occurs both in the longitudinal direction of the rotor axis as well as on the face side at the outlet end ( 12 ) in accordance with the illustrative representation represented in FIG. 2 .
  • control balls ( 10 ) which are preferably weight-loaded, are raised by the difference in pressure between the current pressure in the particular working chamber and the outlet pressure p 2 and move back by the force of gravity, which is shown by means of the angles in accordance with the illustrative representation in FIG. 8 , wherein g indicates the direction of gravity.
  • g indicates the direction of gravity.
  • control balls ( 10 ) in FIG. 1 and in FIG. 4 can be seen on the outlet side in the outlet control disk ( 12 ) as well as in FIG. 2 in the longitudinal direction of the rotor axis for the ⁇ iV adjustment for avoiding efficiency-damaging over- and undercompression as well as in an axial top view in the outlet control disk ( 12 ) and adapt the so-called inner volume ratio ⁇ iV in accordance with the specific application to the particular pressure ratio actually present.
  • an intermediate support ( 17 ) on the two-toothed spindle rotor ( 2 ) is proposed for weight reduction, in particular also as a lower mass moment of inertia during initial acceleration (as well as deceleration) with simultaneous high flexural rigidity, for example made of a vacuum-compatible fibre-composite material, e.g. as a CFRP material.
  • the inner volume ratio (i.e. the simple quotient of the working-chamber volume at the inlet divided by the working-chamber volume at the outlet) of the spindle-rotor pair is limited to an iV range preferably between 2 up to a maximum of 20, wherein the adaptation to the particular working/operating point with its current actual pressure ratios occurs via the aforementioned control balls ( 10 ) in accordance with the specific application. If still greater temperature lifts ⁇ T h in accordance with
  • the play values in the compressor outlet area are selectively increased by approximately 20 to at least 50% greater average gap clearances, preferably realized simply in that the outer rotor diameters are manufactured to be correspondingly smaller over an area in the longitudinal direction of the rotor axis corresponding to 0.3 to 2 times the extension of the working-chamber length on the outlet side in the longitudinal direction of the rotor axis, wherein, in the event of a face-side outlet plate with a bearing support ( 25 ) on the control edge ( 27 .S), this is also realized by bevelling (in the sense of rendering oblique) said control edge ( 27 .S).
  • the outer rotor diameter/gap adaptation on the rotor pair preferably occurs here so that this diametric adaptation, which progresses in the direction of the outlet initially slowly, increases to progressively larger values so that the averaged gap clearances reach the above-mentioned increase as an average.
  • This outlet-gap-iV adaptation helps in particular to reduce noise as the pressure pulsations on the outlet side are dampened.
  • PIRSA pressure/Inner Ratio/Speed Adaptation
  • the control unit ( 15 ) has its own preinstalled databank here and can adapt these operating parameters in a regulating manner, wherein this process occurs through self-learning by means of trial and error in accordance with the specific application, by modifying individual values slightly and determining by the reaction of the system whether the overall efficiency improved or suffered. This way, the databank is constantly broadened in every operating point through self-learning and the system becomes increasingly more intelligent in terms of efficiency improvement.
  • m s ⁇ ( ⁇ ) 2 ⁇ ⁇ ⁇ dz s ⁇ ( ⁇ ) d ⁇ ⁇ ⁇ ⁇ 2 ⁇ ⁇ ⁇ ⁇ ⁇ ⁇ z s ⁇ ( ⁇ ) ⁇ ⁇ ⁇ ⁇ ⁇
  • the tooth flank offset according to the disclosure is illustrated via the head arc angle be. 2 K(z) in accordance with FIG. 9 in a simplified manner in the plane, although this type of problem is three-dimensional due to the non-parallel rotational axes of the spindle rotors.
  • ⁇ . 2 ( z ) and ⁇ . 3 ( z ) are preferably chosen so that the requirements of the specific application are fulfilled to the highest possible degree, for example with respect to working-chamber volume as well as the so-called “volume curve” (i.e. the distribution of the working-chamber volumes in the longitudinal direction of the rotor axis, wherein in particular the variation of these working-chamber volumes is of importance).
  • volume curve i.e. the distribution of the working-chamber volumes in the longitudinal direction of the rotor axis, wherein in particular the variation of these working-chamber volumes is of importance.
  • the thermal balances of the working-space structural components, i.e. the housing ( 1 ) and the spindle-rotor pair ( 2 and 3 ), in the R718 displacement compressor system ( 42 ) are managed and regulated so that the following advantages are simultaneously met at all times and in all conditions and intelligently by the system:
  • control unit ( 15 ) The necessary capability for accomplishing these advantages in accordance with the disclosure in the sense of intelligence lies in the control unit ( 15 ). Both its design as well as its operation must be configured in accordance with the disclosure so that the advantages mentioned in the introduction are reliably achieved at all times.
  • the speed adaptation occurs via FUs ( 2 . 4 and 3 . 4 ) via the electronic synchronization of the motor pair/spindle rotors by means of the FU-CU ( 16 ) in conjunction with the control unit ( 15 ).
  • the injection cooling K 4 performs the main share of cooling during compression, whereas the cooling of the working-space structural components is added by the control unit ( 15 ) in particular to compensate for various thermal expansions of each working-space structural component and/or to protect the sensitive structural components (in particular the rotor mount as well as the drive motors) by saving this in the algorithm of the control unit ( 15 ).
  • the cooling water “kra” generally purges the heat Q ab from the condenser ( 8 ), while the heat Q ent is withdrawn from the chilled water “Ka” in the evaporator ( 7 ) by the displacement compressor system.
  • K Designated as the refrigerant (abbreviated as “K”) here is the water that is diverted from the evaporator ( 7 ) as a refrigerant fluid flow in a manner regulated by the control unit ( 15 ) in the refrigerant separator ( 26 ) for separation into a main flow HS and the individual refrigerant fluid flows K 1 , K 2 , K 3 , K 4 and K 5 for the achievement of the aforementioned advantages.
  • the heat balance for the compressor housing ( 1 ) is selectively set in accordance with the disclosure as the so-called “housing thermal-balance management” via the intermediate water jacket ( 5 ) by the control unit ( 15 ) in accordance with the specific application as set out below:
  • the distance between the spindle-rotor axes at the inlet ( 11 ) preferably at least 10% greater than at the outlet ( 12 )
  • cylindrical inner cooling of spindle rotor can be limited to the last area, i.e. not over the entire rotor length (with corresponding increase in the bottom wall thickness at the inlet)
  • the maximum version is represented (so to speak the “Mercedes”), as all cooling mechanisms are realized—there will also be a slimmed-down version (so to speak the “VW”), by preferably/for example omitting the structural-component cooling and adjusting the temperatures during compression only via the injection cooling, i.e.: the above advantages can only be achieved in a limited manner, as this is sufficient for several applications.
  • K 0 speed measurement (as self-diagnosis for the determination of changes, e.g. formation of deposits, etc.)
  • FIG. 1 illustratively shows a representation of a longitudinal section through the R718 displacement compressor system ( 42 ) in accordance with the disclosure with a standing configuration.
  • the customary vacuum pump for ensuring negative pressure is not shown in the represented R718 displacement compressor system ( 42 ), but is sufficiently known and implemented in accordance with FIG. 4 when purging preferably via the shielding-gas discharge ( 31 ) shown in FIG. 4 .
  • FIG. 3 shows an enlargement of the inlet area with the evaporator ( 7 ) of this representation and FIG. 4 shows an enlargement of the outlet area with the condenser ( 8 ).
  • the important gap values between the rotor head and the housing are adjusted by means of peeling disks ( 18 ) on the inlet side via the positions of the spindle-rotor units ( 39 and 40 in accordance with FIG. 13 ) in the longitudinal rotor-axis direction.
  • the face-side gap values of the spindle rotor to the outlet control disk ( 12 ) are adjusted via peeling disks ( 18 ).
  • FIG. 2 As an illustrative sectional representation relating to FIG. 1 perpendicular to the axis of the housing vessel ( 28 ) approximately halfway down the longitudinal rotor axis in a perspective looking toward the outlet ( 12 ) as a cylindrical cooling-system cross section for the R718-displacement compressor system with control balls ( 10 ) both in the longitudinal rotor-axis direction (the control balls are accordingly shown as sectioned and shaded) and as a top view of the outlet control disk ( 12 ) simply as circular control-ball openings, which are shown in turn in FIG. 1 as sectioned and shaded at the outlet ( 12 ). Furthermore, the end outlet openings ( 27 ) with the control edges ( 27 .S) can be seen clearly on the outlet control disk ( 12 ).
  • FIG. 3 As an illustrative representation for the suction area shown in FIG. 1 with a representation of the respective refrigerant fluid flows K 1 and K 2 and K 3 and K 4 and K 5 with HS as the circuit-medium-R718 main flow for the achievement of the core objective for the transfer of heat.
  • various configurations are shown simultaneously (in practice they are realized separately) for the heat transfer in the evaporator ( 7 ), by having the refrigerant R-718 flow, for example, via the overflow groove ( 37 ) over a large enough surface to the drain ( 37 .
  • FIG. 5 As illustrative 3D representation toward the compressor housing ( 1 ) with separation between evaporator space and condenser space via the preferably cylindrical dividing plate ( 1 .P), moreover with the preferably three attached bearing-support support arms ( 24 ) for each bearing support ( 25 ).
  • the principle of the “open” compressor becomes clear, as merely the two spindle-rotor rotation units ( 39 and 40 ) are mounted in the housing, and the compressor machine ( 41 ) is practically complete without specific face-side closing parts (thus “open” compressor)
  • FIG. 6 Illustratively represented is an enlargement of the feed ( 23 . 1 ) of injection refrigerant K 4 to the centrifugal disk ( 22 ) via a bearing-support support arm ( 24 ) in the compressor inlet area ( 11 ) shown in FIG. 1 , by having the refrigerant fluid flow K 4 reach, for example via a small tube, the upper side of the centrifugal disk ( 22 ), where K 4 , which is distributed evenly by means of centrifugal forces, then enters the gas flow at the inlet ( 11 ) with the optimum speed profile vis-à-vis the spindle rotor.
  • FIG. 7 As an illustrative representation of the centrifugal disk ( 22 ) preferably with rough, course surface for the reduction of slippage and better distribution of the refrigerant fluid flow K 4 , wherein the diameter ⁇ a.s as well as the height h and the angle ⁇ s substantially influence the spray of the refrigerant fluid flow K 4 from the centrifugal disk and are to be configured in accordance with the specific application.
  • FIG. 8 As an illustrative representation of the control ball ( 10 ) for the adaptation of the inner volume ratios to various temperature lifts with corresponding pressure differences, rolling away on the ramp ( 10 .R) via the angles ⁇ A and ⁇ R with respect to the direction of gravity g while preferably subject to the force of gravity by means of the difference in pressure ⁇ p at the control ball between the particular working-chamber pressure and the outlet pressure, a special material not necessarily being necessary here, and automatically rolling back by force of gravity when the difference in pressure decreases.
  • FIG. 9 Illustrative representation of the spindle-rotor profile pairing, wherein the problem, which is actually three-dimensional on account of non-parallel rotational axes, is shown in a simplified manner in a plane.
  • K(z) which yields the tooth flank offset ⁇ k vs (z) as a different z( ⁇ ) distribution for the right and left profile flank for each tooth, as well as with the particular ⁇ value for each spindle rotor via the rotor head circles with a(z) distribution for the distance between the rotor axles.
  • FIG. 10 . 1 [Values Only Illustrative]
  • FIG. 10 . 2 [Values Only Illustrative]
  • the ⁇ values shown in FIG. 10.2 lead here to the cylindrical rotor mount shown in FIG. 1 in order to make possible the evaporator cooling at each spindle rotor in particular during k 0 operation.
  • FIG. 10 . 3 [Values Only Illustrative]
  • FIG. 10 . 4 [Values Only Illustrative]
  • FIG. 10 . 5 [Values Only Illustrative]
  • FIG. 11 As an illustrative representation, three different spindle-rotor pairs for the rotor construction kit are represented as FIG. 11.1 and FIG. 11.2 and FIG. 11.3 , which fit with respect to their outer/connecting geometry to the same compressor housing ( 1 ), at the least to the same housing sleeve, wherein the following description applies:
  • FIG. 11.1 shows illustratively a spindle-rotor pair with a high suction capacity with a moderate number of tiers for applications in which it is less the compression capacity that is of importance, but a high volume flow.
  • FIG. 11.2 shows illustratively a spindle-rotor pair with a moderate suction capacity with an intermediate number of tiers for applications without a pronounced prioritization, i.e. more of a general orientation.
  • FIG. 11.3 shows illustratively the spindle-rotor pair with a low suction capacity with a very high number of tiers for applications in which a high compression capacity is more important than volume flow.
  • FIG. 12.1 Illustrative representation of an alternative design for the outlet control disk ( 12 ), in which control balls ( 10 ) can be omitted, by configuring the outlet control disk to be rotatable ( 12 .S) together with the pivot bearings ( 12 . g ) as well as the discharge slot ( 12 . s ) at the end of the two-toothed spindle rotor.
  • FIG. 12.2 Illustrative representation of the configuration of the rotatable outlet control disk ( 12 . d ) with the discharge slot ( 12 . s ) as well as, in addition, lateral outlet notches ( 12 . k ), so that the last working chamber pushing outward does not close again when the minimum inner compression ratio is adjusted. These notches are necessary because the discharge slot ( 12 . s ) cannot take up too much of the circle as otherwise the factor by which the inner compression can be increased sinks. When the maximum inner compression ratio is set, the outlet notches ( 12 . k ) are above the chamber that would open without the outlet control disk ( 12 . d ). The outlet notches ( 12 .
  • FIG. 13 Represented illustratively are the finished and completely balanced spindle-rotor rotation units ( 39 and 40 ), which, without further intervention via the peeling disks ( 18 ), can be inserted without any changes in the compressor housing ( 1 ) for the exact gap adjustment and thus form the open compressor machine ( 41 ).
  • FIG. 14 Represented illustratively are 3 operating modes for operating the R718 displacement compressor system for different cooling-water (“ü”) and chilled-water (“a”) temperature levels, which are optimally set in accordance with the specific application by the control unit ( 15 ) by means of PIRSA as “Pressure/Inner Ratio/Speed Adaptation”, as described.
  • the open compressor machine ( 41 ) is configured as a spindle-rotor compressor in the form of a twin-shaft rotary displacement machine for conveying and compressing gaseous media. It has a spindle-rotor pair ( 2 and 3 ), which is arranged in a compressor housing ( 1 ) and configured with an electronic synchronization of the motor pair/spindle rotors.
  • the compressor machine ( 41 ) is arranged between the evaporator ( 35 ) and the condenser ( 36 ).

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
US16/617,908 2017-06-30 2018-06-27 Displacement compressor system for r-718 Abandoned US20200309129A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102017006206.4A DE102017006206A1 (de) 2017-06-30 2017-06-30 Verdrängerverdichtersystem für R-718
DE102017006206.4 2017-06-30
PCT/EP2018/067239 WO2019002363A1 (fr) 2017-06-30 2018-06-27 Compresseur volumétrique pour r-718

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US (1) US20200309129A1 (fr)
EP (1) EP3645891A1 (fr)
JP (1) JP2020525697A (fr)
CN (1) CN110869615A (fr)
DE (1) DE102017006206A1 (fr)
WO (1) WO2019002363A1 (fr)

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DE102020000350A1 (de) * 2020-01-21 2021-07-22 Ralf Steffens Volumenverhältnis bei einem R718*-Verdichter

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DE102004001927A1 (de) * 2004-01-14 2005-08-04 York Deutschland Gmbh Verfahren zur Wärmerückgewinnung
DE102008063133A1 (de) * 2008-12-24 2010-07-01 Oerlikon Leybold Vacuum Gmbh Vakuumpumpe
DE102010021015A1 (de) * 2010-05-19 2011-11-24 O3-innovation Ursula Bürger e.Kfr. Wärmepumpe mit gewendelten Kolben gleichen Profilquerschnitts für die Erzeugung von Kälte und Wärme
DE102013009040B4 (de) * 2013-05-28 2024-04-11 Ralf Steffens Spindelkompressor mit hoher innerer Verdichtung
DE102014008288A1 (de) * 2014-06-03 2015-12-03 Ralf Steffens Spindelverdichter für Kompressionskältemaschinen
CN104235988B (zh) * 2014-10-16 2017-02-01 珠海格力电器股份有限公司 采用水作为制冷剂的离心式空调机组及运行方法
US10746177B2 (en) * 2014-12-31 2020-08-18 Ingersoll-Rand Industrial U.S., Inc. Compressor with a closed loop water cooling system
CN106679213B (zh) * 2017-02-09 2019-03-12 浙江理工大学 压缩驱动的双温超重力制冷热泵系统及方法

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DE102017006206A1 (de) 2019-01-03
CN110869615A (zh) 2020-03-06
JP2020525697A (ja) 2020-08-27
WO2019002363A1 (fr) 2019-01-03

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